Heat pump system and method

Abstract

This specification provides methods and systems for generating water vapor. [Solution] This method may include circulating a first working fluid through a first heat pump cycle, circulating a second working fluid through a second heat pump cycle, and transferring heat from the first working fluid to the second working fluid in a heat exchanger connected to the first and second heat pump cycles. In some embodiments, the first heat pump cycle receives heat from the ambient airflow.

Description

[Background technology]

[0001] Cross-reference of related applications This application claims the interests of U.S. Provisional Application No. 63 / 453,047, filed on 17 March 2023, which is incorporated herein by reference in its entirety.

[0002] In the United States, the industrial sector accounts for 22% of greenhouse gas emissions, which is equivalent to approximately 1.5 billion tons of carbon dioxide equivalent (GtCO2e / year) per year. Within this industrial sector, steam generation for process heat is one of the largest sources of energy consumption, accounting for approximately 4 quads of primary energy consumption in the United States and emitting more than 200 million tons of carbon dioxide (CO2) annually. The majority of these emissions are caused by conventional boilers, cogeneration (combined heat and power), and fuel combustion for process heating. Furthermore, the electrification of steam generation relies on inefficient electric boilers and waste heat-driven heat pumps. This reliance on waste heat is a barrier to adoption due to high installation costs and a lack of consistency in waste heat across various industries and facilities. [Overview of the Initiative] [Problems that the invention aims to solve]

[0003] This disclosure relates to an air-source heat pump system for industrial steam generation and a method of using the same, which can at least meet the above-mentioned needs. [Means for solving the problem]

[0004] In one aspect, the present disclosure provides a method for generating steam, the method comprising: circulating a first heat transfer fluid through an intermediate loop comprising (i) a first heat exchanger that receives a first heat transfer fluid and an ambient airflow and transfers heat from the ambient airflow to the first heat transfer fluid; and (ii) a second heat exchanger that receives a heat transfer fluid and a first working fluid and transfers heat from the first heat transfer fluid to the first working fluid; circulating a first working fluid through a first heat pump cycle comprising (i) a second heat exchanger and (ii) a third heat exchanger that receives a first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid; and circulating a second working fluid through a second heat pump cycle comprising (i) a third heat exchanger and (ii) a steam generator, and supplying a water-containing supply stream to a steam generator, the steam generator transferring heat from the second working fluid to the supply stream to generate steam.

[0005] In some embodiments, the method further includes transferring heat from a heat source subunit to an intermediate loop via a heat exchanger, wherein the heat source subunit is coupled to the intermediate loop.

[0006] In some embodiments, the heat source subunit is (i) a refrigeration system, (ii) a geothermal source, (iii) waste heat flow from a process, wastewater or waste heat flow from a heat system, power system or combined heat and power system, (iv) a carbon capture process, (v) a body of water, (vi) a regional energy system, (vii) a solar thermal source, or (viii) a nuclear reactor.

[0007] In some embodiments, the body of water is a lake or a river.

[0008] In some embodiments, the carbon capture process is a direct air capture system.

[0009] In some embodiments, the intermediate loop subunit heat exchanger receives the subunit fluid and the first heat transfer fluid and transfers heat from the subunit fluid to the first heat transfer fluid.

[0010] In some embodiments, the subunit heat exchanger condenses at least a portion of the subunit fluid.

[0011] In some embodiments, the method further includes transferring heat from the subunit fluid of the heat source subunit to a second heat transfer fluid, and transferring heat from the second heat transfer fluid to an intermediate loop.

[0012] In some embodiments, the first heat transfer fluid supplies cooling directly to the heat source subunit.

[0013] In some embodiments, the first heat transfer fluid directly cools a water flow or a reservoir.

[0014] In some embodiments, the method further includes directing a fluid airflow to an additional heat exchanger in an intermediate loop, thereby transferring heat from the ambient air to the first heat transfer fluid via the additional heat exchanger, the additional heat exchanger being arranged in parallel with the first heat exchanger.

[0015] In some embodiments, the method further includes directing a fluid airflow to an additional heat exchanger in an intermediate loop, thereby transferring heat from the ambient air to the first heat transfer fluid via the additional heat exchanger, the additional heat exchanger being arranged in series with the first heat exchanger.

[0016] In some embodiments, the method further includes transferring heat from a vapor compression system to a heat transfer fluid, with the intermediate loop being coupled to the vapor compression system.

[0017] In some embodiments, the first heat exchanger is located within the cycle of the vapor compression system.

[0018] In some embodiments, the vapor-compressed fluid in the vapor compression system is ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H2O). 12 ), butane (C4H 10) It contains one or more of isobutane (HC(CH3)3), propane (C3H8), or propene (C3H6).

[0019] In some embodiments, the intermediate loop is coupled to a vapor compression system using a condenser and an evaporator.

[0020] In some embodiments, the intermediate loop further includes a heat recovery heat exchanger, which enables at least one of (i) operation at a very low ambient temperature or (ii) sizing the vapor compression cycle to a lower capacity.

[0021] In some embodiments, the intermediate loop further includes a fourth heat exchanger that receives a first heat transfer fluid and a third working fluid and transfers heat from the first heat transfer fluid to the third working fluid.

[0022] In some embodiments, the method further includes circulating the third working fluid through a third heat pump cycle that includes (i) the fourth heat exchanger and (ii) a fifth heat exchanger that receives the third working fluid and a fourth working fluid and transfers heat from the third working fluid to the fourth working fluid, circulating the fourth working fluid through a fourth heat pump cycle that includes (i) the fifth heat exchanger and (ii) a second steam generator, and supplying a second supply stream containing water to the second steam generator that transfers heat from the fourth working fluid to the supply stream to generate steam.

[0023] In some embodiments, the second heat exchanger and the fourth heat exchanger are configured in parallel.

[0024] In some embodiments, the second heat exchanger and the fourth heat exchanger are configured in series.

[0025] In some embodiments, the vapor compression system is an air source.

[0026] In some embodiments, the vapor compression fluid of the vapor compression system includes one or more hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants.

[0027] In some embodiments, the first heat exchanger (i) transfers heat to the first heat transfer fluid when the refrigeration load is low or zero or the steam load is high, or (ii) transfers heat from the first heat transfer fluid when the refrigeration load is high or the heat pump load is low or zero.

[0028] In some embodiments, the method further includes compressing water vapor using a water vapor compressor.

[0029] In some embodiments, the method further includes superheating and removing the steam after it has been compressed.

[0030] In some embodiments, superheating of the steam is removed by injecting water into the steam at one or more locations to cool the steam to a saturated state. Here, one or more locations are downstream of the steam compressor, upstream of the steam compressor, or at the steam compressor itself.

[0031] In some embodiments, the steam is deheated by cooling it to saturation using a heat transfer fluid from one or more cycles of the heat pump at one or more locations, where one or more locations are downstream of the steam compressor, upstream of the steam compressor, or at the steam compressor itself.

[0032] In some embodiments, the method further includes filling a storage tank with fluid from a steam generator and discharging the fluid from the storage tank, the fluid being discharged as steam.

[0033] In some embodiments, the method further includes closing one or more valves to isolate the storage tank, thereby preventing filling and discharging.

[0034] In another embodiment, the Disclosure relates to an intermediate loop comprising a first heat exchanger and a second heat exchanger, the intermediate loop configured to circulate a first heat transfer fluid, the first heat exchanger configured to receive ambient airflow and the first heat transfer fluid and transfer heat from the ambient airflow to the first heat transfer fluid, and a first heat pump cycle configured to circulate a first working fluid between the second heat exchanger and a third heat exchanger, the second heat exchanger configured to receive the first heat transfer fluid and the first working fluid and transfer heat from the first heat transfer fluid to the first working fluid, and the third heat The present invention provides a steam generation system comprising: a first heat pump cycle configured to receive a first working fluid and a second working fluid and transfer heat from the first working fluid to the second working fluid; and a second heat pump cycle configured to circulate the second working fluid between a third heat exchanger and a fourth heat exchanger, the fourth heat exchanger configured to receive the second working fluid and a supply stream, the supply stream containing water, and the first heat exchanger being isolated from the first and second heat pump cycles.

[0035] In some embodiments, the system further comprises a heat source subunit, the heat source subunit having at least one component coupled to an intermediate loop.

[0036] In some embodiments, the heat source subunit is a refrigeration system, a geothermal source, a waste heat flow from a process, or wastewater or waste heat flow from a heat system, power system, or combined heat and power system.

[0037] In some embodiments, the heat source subunit includes a subunit fluid, and the intermediate loop includes a subunit heat exchanger configured to receive the subunit fluid and a first heat transfer fluid and transfer heat from the subunit fluid to the first heat transfer fluid.

[0038] In some embodiments, at least a portion of the subunit fluid is condensed by the subunit heat exchanger.

[0039] In some embodiments, the system further includes a heat source subunit, which includes a condenser and is disconnected from the intermediate loop.

[0040] In some embodiments, the condenser is configured to transfer heat from the subunit fluid of a subunit to a second heat transfer fluid, which supplies heat to an intermediate loop.

[0041] In some embodiments, the first heat transfer fluid supplies cooling directly to the heat source subunit.

[0042] In some embodiments, the first heat transfer fluid directly cools a water flow or a reservoir.

[0043] In some embodiments, the intermediate loop includes an additional heat exchanger positioned in parallel with the first heat exchanger, which receives ambient air and transfers heat from the ambient air to the first heat transfer fluid.

[0044] In some embodiments, the intermediate loop comprises an additional heat exchanger positioned in series with the first heat exchanger, which receives ambient air and transfers heat from the ambient air to the first heat transfer fluid.

[0045] In some embodiments, the intermediate loop is coupled to a vapor compression system, which supplies heat to the heat transfer fluid.

[0046] In some embodiments, the first heat exchanger is located within the cycle of the vapor compression system.

[0047] In some embodiments, the vapor-compressed fluid in the vapor compression system is ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H2O). 12 ), butane (C4H 10It contains one or more of the following: ), isobutane (HC(CH3)3), propane (C3H8), or propene (C3H6).

[0048] In some embodiments, the intermediate loop includes an integrated vapor compression system.

[0049] In some embodiments, the integrated steam compression system includes a compressor, which is a positive displacement compressor.

[0050] In some embodiments, the positive displacement compressor is a screw compressor, a scroll compressor, or a reciprocating compressor.

[0051] In some embodiments, the positive displacement compressor is a screw compressor.

[0052] In some embodiments, the system further comprises one or more centrifugal compressors(s).

[0053] In some embodiments, one or more centrifugal compressors(groups) are one or more oil-free centrifugal compressors(groups).

[0054] In some embodiments, the supply stream contains water, and the fourth heat exchanger is configured to heat the supply stream without altering the phase of the water in the supply stream.

[0055] In some embodiments, the system further comprises a flash tank downstream of the fourth heat exchanger, configured to receive at least water from the supply stream from the fourth heat exchanger.

[0056] In some embodiments, the flash tank is configured to reduce the pressure of at least the water in the supply stream to generate steam.

[0057] In some embodiments, the outlet of the fourth heat exchanger is water vapor, and the ambient airflow temperature is -20°C or lower.

[0058] In some embodiments, the system is configured to generate steam as the outlet of the fourth heat exchanger when the ambient airflow temperature is below -40°C.

[0059] In some embodiments, the system further comprises at least two flash tanks downstream of the fourth heat exchanger, the at least two flash tanks configured to receive at least water from the supply stream from the fourth heat exchanger.

[0060] In some embodiments, the intermediate loop further comprises a fifth heat exchanger, and the system further comprises a third heat pump cycle configured to circulate a third working fluid between the fifth heat exchanger and a sixth heat exchanger, wherein the fifth heat exchanger is configured to receive a first heat transfer fluid and a third working fluid and to transfer heat from the first heat transfer fluid to the third working fluid, and the sixth heat exchanger is configured to receive a third working fluid and a fourth working fluid and to transfer heat from the fourth working fluid to the fifth working fluid; and a fourth heat pump cycle configured to circulate a fourth working fluid between the sixth heat exchanger and a seventh heat exchanger, wherein the seventh heat exchanger receives a fourth working fluid and a second supply stream, the second supply stream containing water, and the first heat exchanger is disconnected from the third and fourth heat pump cycles.

[0061] In some embodiments, the second heat exchanger and the fifth heat exchanger are configured to be arranged in parallel.

[0062] In some embodiments, the second heat exchanger and the fifth heat exchanger are configured to be arranged in series.

[0063] In some embodiments, the system further includes a subcooler, which is located downstream of the third or fourth heat exchanger.

[0064] In some embodiments, the subcooler is positioned at the same height as or lower than the third or fourth heat exchanger.

[0065] In some embodiments, saturated or supercooled liquid from the top cycle is drawn from the bottom of a third or fourth heat exchanger and coupled to the supercooler.

[0066] In some embodiments, a saturated or supercooled liquid absorbs heat from the bottom cycle, evaporates and moves upward, and is either (i) coupled at the expansion valve outlet or (ii) directly injected into a third or fourth heat exchanger.

[0067] In some embodiments, the top-cycle fluid flow entering the subcooler is controlled by a valve located upstream of the subcooler.

[0068] In some embodiments, the top-cycle fluid flow entering the subcooler is controlled by a flow limiter, which is located on a bypass stream upstream of the subcooler.

[0069] In some embodiments, the subcooler uses glycol to cool the bottom cycle fluid, and the glycol is used to defrost the heat exchanger.

[0070] In some embodiments, the system further includes a heat storage system.

[0071] In some embodiments, the heat storage system includes a phase change material, which is configured to (i) be incorporated into a heat exchanger or (ii) be located outside the heat exchanger, and the phase change material is further configured to store and release stored energy using the latent heat of the phase change.

[0072] In another embodiment, the Disclosure provides a steam generation method comprising: circulating a first working fluid through a refrigeration cycle that receives a first working fluid and a cooled fluid and transfers heat from the cooled fluid to the first working fluid; and circulating a second working fluid through a heat pump cycle comprising (i) a second heat exchanger that receives a first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid; and (ii) a steam generator that receives a second working fluid and a supply stream and transfers heat from the second working fluid to the supply stream to generate a saturated steam flow, wherein the supply stream contains water.

[0073] In some embodiments, the first working fluid of the refrigeration cycle is ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H2O). 12 ), butane (C4H 10 ), contains one or more of the following: isobutane (HC(CH3)3), propane (C3H8), or propene (C3H6).

[0074] In some embodiments, the refrigeration cycle includes a positive displacement compressor or a centrifugal compressor.

[0075] In some embodiments, the positive displacement compressor is a screw compressor, a scroll compressor, or a reciprocating compressor.

[0076] In some embodiments, the positive displacement compressor or centrifugal compressor is an oil-free compressor.

[0077] In some embodiments, the refrigeration cycle includes a third heat exchanger that transfers heat from the first working fluid to the ambient airflow.

[0078] In some embodiments, the maximum temperature of the first working fluid during operation is 100°C or less.

[0079] In some embodiments, the first working fluid of the refrigeration cycle includes one or more hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants.

[0080] In another embodiment, the Disclosure provides a steam generating system comprising: a refrigeration cycle configured to circulate a first working fluid, comprising a first heat exchanger configured to receive the first working fluid and a cooled fluid and to transfer heat from the cooled fluid to the first working fluid; and a heat pump cycle configured to circulate a second working fluid, comprising (i) a second heat exchanger, and (ii) a steam generator configured to receive the second working fluid and a supply stream and to transfer heat from the second working fluid to the supply stream to generate a saturated steam flow, wherein the supply stream contains water.

[0081] In some embodiments, the first working fluid of the refrigeration cycle or the second working fluid of the heat pump cycle is ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H2O2), etc. 12 ), butane (C4H 10 ), isobutane (HC(CH3)3), propane (C3H8), propene (C3H6), hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, and one or more hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants.

[0082] In some embodiments, the refrigeration cycle includes a positive displacement compressor or a centrifugal compressor.

[0083] In some embodiments, the positive displacement compressor of the refrigeration cycle is a screw compressor.

[0084] In some embodiments, the refrigeration cycle further includes at least one of a cryogenic evaporator, an air-cooled condenser, or a heat exchanger, coupled to a water loop that includes a condenser.

[0085] In some embodiments, the heat pump cycle further comprises at least one of an economizer, a compressor, an intercooler, or a suction line heat exchanger.

[0086] In some embodiments, the maximum temperature of the first working fluid of the refrigeration cycle is 100 °C or less.

[0087] In another aspect, the present disclosure provides a method for generating steam, comprising circulating a first working fluid that is in a subcritical state in at least a part of a first heat pump cycle through the first heat pump cycle, and circulating a second working fluid through a second heat pump cycle, wherein the second heat pump cycle includes a first steam generator, the second working fluid is in a subcritical state in at least a part of the second heat pump cycle, the first working fluid is in a supercritical state in at least a part of the first heat pump cycle, the second working fluid is in a supercritical state in at least a part of the second heat pump system, or the first working fluid and the second working fluid are in a supercritical state in at least a part of the first heat pump cycle and the second heat pump cycle, and supplying a heat exchanger for receiving the first working fluid and the second working fluid and transferring heat from the first working fluid to the second working fluid.

[0088] In some embodiments, the first working fluid comprises one or more of ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H 12 ), butane (C4H 10 ), isobutane (HC(CH3)3), propane (C3H8), or propene (C3H6).

[0089] In some embodiments, the second working fluid comprises one or more of ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H 12 ), butane (C4H 10It contains one or more of the following: ), isobutane (HC(CH3)3), propane (C3H8), or propene (C3H6).

[0090] In some embodiments, the first or second working fluid comprises one or more of the following: hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants.

[0091] In some embodiments, the first heat pump cycle moves air from the ambient airflow to the first working fluid.

[0092] In some embodiments, at least one of the first or second heat pump cycles includes an oil-free compressor.

[0093] In some embodiments, the oil-free compressor is a positive displacement compressor or a centrifugal compressor.

[0094] In some embodiments, the second heat pump cycle includes a second steam generator.

[0095] In some embodiments, either the first heat pump cycle or the second heat pump cycle further comprises an economizer, an intercooler, an intake tube heat exchanger, or at least two condensers thereof.

[0096] In another embodiment, the Disclosure provides a first heat pump cycle configured to circulate a first working fluid, the first working fluid being subcritical in at least a portion of the first heat pump cycle, and a second heat pump cycle comprising a first steam generator, the second heat pump cycle configured to circulate a second working fluid, the second working fluid being subcritical in at least a portion of the second heat pump cycle, the first working fluid being supercritical in at least a portion of the first heat pump, and the second working fluid being subcritical in at least a portion of the second heat pump system. A system for generating steam or hot water is provided, comprising: a second heat pump cycle in which the first working fluid and the second working fluid are in a supercritical state in at least part of the first and second heat pump cycles, and a first steam generator configured to (i) receive a supply stream containing the second working fluid and water from a first compressor, and (ii) transfer heat from the second working fluid to the supply stream to generate steam or hot water; and a first heat exchanger configured to receive the first and second working fluids and transfer heat from the first working fluid to the second working fluid.

[0097] In some embodiments, the system further comprises a second steam generator positioned in parallel with the first steam generator, the second steam generator (i) receiving a second supercritical fluid flow and water flow from the first compressor, and (ii) producing saturated steam.

[0098] In some embodiments, the system further comprises a first compressor and a second compressor arranged in series with a first steam generator, the first steam generator supplying a first supercritical fluid to the second compressor, and the second compressor supplying a second supercritical fluid flow to either the first or second steam generator.

[0099] In some embodiments, the first steam generator and the second steam generator produce steam at different temperatures.

[0100] In some embodiments, the portion of the second heat pump cycle in which the second working fluid is supercritical includes at least a portion of the second working fluid in a steam generator.

[0101] In another embodiment, the present disclosure provides a steam generation method comprising: circulating a first working fluid through a first heat pump cycle; circulating a second working fluid through a second heat pump cycle; providing a first heat exchanger that receives the first and second working fluids and transfers heat from the first working fluid to the second working fluid; supplying an ambient airflow to a first evaporator that receives an ambient airflow and either the first or second working fluid and transfers heat from the ambient airflow to either the first or second working fluid; and providing an external heat source to a second evaporator that receives either the first or second working fluid and transfers heat from a heat source to either the first or second working fluid.

[0102] In some embodiments, the external heat source includes (i) a refrigeration cycle, (ii) a geothermal source, (iii) waste heat from a process, a heat system, a power system, or wastewater or waste heat flow from a combined heat and power system, (iv) a carbon capture process, (v) a body of water, (vi) a regional energy system, (vii) a solar thermal source, or (viii) a nuclear reactor.

[0103] In some embodiments, the body of water is a lake or a river.

[0104] In some embodiments, the carbon capture process is a direct air capture system.

[0105] In some embodiments, the inlet temperature of the first evaporator is lower than the inlet temperature of the second evaporator.

[0106] In some embodiments, at least 500 kg / hour of steam is generated.

[0107] In another embodiment, the Disclosure provides a steam generating system comprising: a first heat pump cycle configured to circulate a first working fluid; a second heat pump cycle configured to circulate a second working fluid, including at least one compressor, at least one expansion valve, and a first steam generator; a first heat exchanger configured to receive the first and second working fluids and transfer heat from the first working fluid to the second working fluid; a first evaporator configured to receive an ambient airflow and the first or second working fluid and transfer heat from the ambient airflow to the first or second working fluid; and a second evaporator configured to transfer heat from a heat source to the first or second working fluid.

[0108] In some embodiments, the second evaporator is coupled to (i) a connected or disconnected refrigeration cycle, (ii) a geothermal source, or (iii) a waste heat source from a process, (iv) a carbon capture process, (v) a body of water, (vi) a regional energy system, (vii) a solar heat source, or (viii) a nuclear reactor.

[0109] In some embodiments, the body of water is a lake or a river.

[0110] In some embodiments, the carbon capture process is a direct air capture system.

[0111] In some embodiments, the second evaporator is arranged in parallel with the first evaporator.

[0112] In some embodiments, at least one of the first evaporator or the second evaporator is intermittently bypassed.

[0113] In some embodiments, the first evaporator and the second evaporator are located within the first heat pump cycle.

[0114] In some embodiments, the first evaporator and the second evaporator are located within a second heat pump cycle.

[0115] In some embodiments, one of the first and second evaporators is located in a first heat pump cycle, and the other of the first and second evaporators is located in a second heat pump cycle.

[0116] In some embodiments, the first heat pump cycle comprises at least a first compressor and a second compressor, and the second evaporator is arranged in series with the second compressor and in parallel with the first compressor.

[0117] In some embodiments, the second heat pump cycle comprises at least a first compressor and a second compressor, wherein the second evaporator is arranged in series with the second compressor and in parallel with the first compressor.

[0118] In another embodiment, the Disclosure provides a method for generating steam, comprising: circulating a first working fluid through a first heat pump cycle; circulating a second working fluid through a second heat pump cycle comprising a first steam generator; providing a first heat exchanger that receives the first working fluid and an ambient airflow and transfers heat from the ambient airflow to the first working fluid; providing a second heat exchanger that receives the first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid; supplying a first supply stream containing water to a first steam generator to generate steam by transferring heat from the second working fluid to the first supply stream; and supplying a second supply stream containing water to a third heat exchanger to transfer heat from the second working fluid to the second supply stream.

[0119] In another embodiment, the Disclosure provides a steam generating system comprising: a first heat pump cycle configured to circulate a first working fluid; a second heat pump cycle including a first steam generator, the second heat pump cycle configured to circulate a second working fluid, and the first steam generator configured to receive a first water flow and a second working fluid and transfer heat from the second working fluid to the first water flow to generate steam; a first heat exchanger configured to receive a first working fluid and a second working fluid and transfer heat from the first working fluid to the second working fluid; a second heat exchanger configured to (i) receive a first working fluid and an ambient airflow and (ii) transfer heat from the ambient airflow to the first working fluid; and a third heat exchanger configured to receive a second water flow and at least one of the first working fluid and the second working fluid and transfer heat from either the first working fluid or the second working fluid to the second water flow.

[0120] In some embodiments, the third heat exchanger and the first heat exchanger are arranged in parallel in the first heat pump cycle.

[0121] In some embodiments, the third heat exchanger is located within the second heat pump cycle.

[0122] In another embodiment, the disclosure provides a method for generating steam, which includes circulating a working fluid through a heat pump cycle including a compressor, and transferring heat from the working fluid to a supply stream containing water to generate an outlet stream containing steam.

[0123] In some embodiments, the heat pump cycle includes one or more oil-free compressors.

[0124] In some embodiments, the temperature of the water vapor in the outlet stream is at least 120°C.

[0125] In some embodiments, the method further includes supplying a thermally coupled ambient airflow to a heat pump cycle to transfer heat from the ambient airflow to the working fluid.

[0126] In some embodiments, the compressor includes bearings lubricated with a liquid refrigerant.

[0127] In some embodiments, the compressor includes at least one jet for supplying liquid refrigerant to the bearings.

[0128] In some embodiments, the compressor includes at least two jets for supplying liquid refrigerant to the bearings.

[0129] In some embodiments, the compressor is of the double-ended type.

[0130] In some embodiments, the compressor includes a preload spring between the mount housing the bearing and the compressor chassis.

[0131] In some embodiments, the bearings include nitrogen-treated stainless steel.

[0132] In some embodiments, the method further includes a. transferring heat from ambient air to a heat pump cycle using one or more heat exchangers(groups), and b. defrosting at least one of the one or more heat exchangers(groups).

[0133] In some embodiments, one or more heat exchangers(s) are defrosted by electric resistance heaters embedded in or on one or more coils of the heat exchangers.

[0134] In some embodiments, one or more heat exchangers are defrosted by heating the surrounding air with an electric resistance heater before heat transfer by the heat transfer fluid.

[0135] In some embodiments, one or more heat exchangers(s) are defrosted by thermal coupling with a high-temperature gas bypass from the compressor discharge pipe.

[0136] In some embodiments, one or more heat exchangers(s) are defrosted by heating an intermediate fluid and circulating the intermediate fluid, which has been in thermal contact with one or more heat exchangers.

[0137] In some embodiments, one or more heat exchangers(s) are defrosted by introducing a fluid flow containing water or steam onto the surface of one or more heat exchangers.

[0138] In some embodiments, one or more heat exchangers(s) are defrosted sequentially or simultaneously.

[0139] In some embodiments, the heat pump cycle further includes an oil loop for lubricating one or more ball bearings in the compressor.

[0140] In some embodiments, the compressor includes one or more magnetic coils at the end of the shaft to balance the thrust.

[0141] In some embodiments, the compressor is cooled by a motor coolant flow, which contains a refrigerant.

[0142] In some embodiments, the motor coolant flow is cooled by (i) a glycol cooler, (ii) an air cooler, or (iii) a vapor compression cycle.

[0143] In some embodiments, the compressor is cooled by a water flow.

[0144] In some embodiments, the compressor is cooled by injecting a portion of the working fluid between the compressor stages, and a portion of the working fluid is cooled in an economizer before injection.

[0145] In some embodiments, the compressor includes one or more shaft seals.

[0146] In some embodiments, the compressor includes one or more guide vanes.

[0147] In some embodiments, the compressor includes one or more collectors.

[0148] In some embodiments, the compressor includes a diffuser.

[0149] In some embodiments, the compressor is equipped with a shroud.

[0150] In some embodiments, the method further includes cooling a space with air from a heat pump system, the heat pump system comprising a heat pump cycle.

[0151] In some embodiments, the method further includes transferring heat from the air to a heat pump system after cooling the space.

[0152] In another embodiment, the disclosure provides a method for generating steam, comprising: a first system provided in an outdoor space, comprising a heat transfer fluid cycle for transferring heat from an ambient airflow to a heat transfer fluid; and a second system provided in an indoor space, comprising at least one heat pump cycle for receiving the heat transfer fluid and transferring heat to a water-containing supply stream to generate steam.

[0153] In some embodiments, the heat transfer fluid is a refrigerant fluid.

[0154] In some embodiments, the refrigerant fluid includes one or more of water or glycol.

[0155] In some embodiments, the second system comprises at least two heat pump cycles coupled together.

[0156] In some embodiments, steam is generated as an outlet stream from a heat exchanger coupled to at least one heat pump cycle, and the heat exchanger is configured to accept a supply stream containing water.

[0157] In some embodiments, the method further includes depressurizing a pressurized flow containing water in a flash tank to generate steam, the flash tank being located in or coupled to a second heat pump system and receiving a fluid flow containing water from a heat exchanger of the second heat pump system.

[0158] In some embodiments, the heat exchanger of a first heat pump system, which is configured to accept ambient air, is defrosted.

[0159] In some embodiments, the heat exchanger is defrosted by an electric resistance heater embedded in or on one or more coils of the heat exchanger.

[0160] In some embodiments, the heat exchanger is defrosted by heating the surrounding air using an electric resistance heater before heat transfer with the heat transfer fluid.

[0161] In some embodiments, the heat exchanger is defrosted by thermal coupling with a high-temperature gas bypass from the compressor's discharge pipe.

[0162] In some embodiments, the heat exchanger is defrosted by heating an intermediate fluid and circulating the intermediate fluid in thermal contact with the heat exchanger.

[0163] In some embodiments, the heat exchanger is defrosted by introducing a fluid flow containing water or steam onto the surface of the heat exchanger.

[0164] In some embodiments, the method further includes transferring heat from a heat transfer fluid to a working fluid, and the heat transfer loop includes the heat transfer fluid.

[0165] In some embodiments, the heat transfer loop is an intermediate heat transfer loop located between the heat pump and the second heat pump.

[0166] In some embodiments, the method further includes delivering a heat transfer fluid to an end user, wherein the heat transfer fluid is hot water.

[0167] In another embodiment, the disclosure provides a method for cooling at least one of the shaft or rotor of an oil-free compressor, comprising supplying a coolant fluid to a cavity that is in thermal contact with at least one of the shaft or rotor, the coolant fluid at least partially evaporating within the cavity, thereby cooling the at least one of the shaft or rotor of the oil-free compressor, and maintaining the temperature of the rotor below a temperature threshold for demagnetization of permanent magnets in the rotor.

[0168] In some embodiments, the demagnetization temperature threshold is 150°C or less.

[0169] In some embodiments, the compressor compresses a fluid stream containing water or steam to produce an outlet stream containing steam with a temperature of 120°C or higher.

[0170] In some embodiments, the compressor compresses a fluid to produce an outlet stream containing gas with a temperature of 80°C or higher.

[0171] In another embodiment, the Disclosure provides a carbon recovery system comprising a regeneration step, a method for generating steam comprising: directing a saturated steam fluid stream, at least partially condensed, to the regeneration step; and directing a fluid stream discharged from the regeneration step to a heat pump cycle, wherein the fluid stream from the regeneration step supplies heat to the heat pump cycle, and the heat pump cycle generates steam.

[0172] In some embodiments, the fluid flow exiting the regeneration step contains CO2.

[0173] In some embodiments, the fluid stream exiting the regeneration step further includes nitrogen (N2) and / or oxygen (O2).

[0174] In some embodiments, at least a portion of the steam generated by the heat pump cycle is sent to the regeneration step of the carbon capture system.

[0175] In some embodiments, the method further includes (i) cooling the space with air from a heat pump system including a heat pump cycle, and (ii) sending the air to an adsorbent layer of a carbon recovery system.

[0176] In another embodiment, the disclosure provides a method for cooling a high-temperature compressor, comprising: using one or more pumps to transport liquid as motor coolant from one or more locations in the main cycle to one or more motors during a startup condition in which the pressure ratio between multiple compressors of the system is below a threshold; and, when the system gains pressure and the startup condition ends, transitioning to a pressure-driven flow of motor coolant by using the liquid from one or more locations in the main cycle and turning off one or more pumps.

[0177] In some embodiments, one or more positions in (a) are different from one or more positions in (b).

[0178] In some embodiments, one or more locations in (a) are (i) between the system's expansion valve and evaporator, (ii) between the system's condenser and economizer, (iii) from the condenser, (iv) the condenser outlet, (v) the outlet of the suction tube heat exchanger, (vi) the coldest liquid in the system, (vii) any location between the system's condenser and expansion valve, or (viii) any location on the high-pressure side of the main cycle having a liquid reservoir.

[0179] In some embodiments, another location of (b) is (i) between the system's expansion valve and evaporator, (ii) between the system's condenser and economizer, (iii) from the condenser, (iv) the condenser outlet, (v) the outlet of the suction tube heat exchanger, (vi) the coldest liquid in the system, (vii) any location between the system's condenser and expansion valve, or (viii) any location on the high-pressure side of the main cycle having a liquid reservoir.

[0180] In another embodiment, the disclosure provides a method for cooling a high-temperature compressor, comprising: (a) dividing the motor coolant among a plurality of compressor stages in the system; (b) pooling the motor coolant divided among the plurality of compressors together; and (b) sending the pooled motor coolant to the suction side of the compressor with the lowest pressure.

[0181] In some embodiments, supplying the motor coolant in (c) includes (i) piping the motor coolant to the outlet of the system's evaporator, (ii) piping the motor coolant to the inlet of the evaporator, or between the expansion valve and the evaporator, or (iii) combining the motor coolant with a high-temperature gas bypass flow.

[0182] In another aspect, the disclosure provides a method for cooling a high-temperature compressor, comprising: (a) dividing motor coolant among a plurality of compressor stages in a system; pooling the motor coolant divided among the plurality of compressors together; and (b) sending the pooled motor coolant to one or more locations in the system, at least in part, based on one or more operating conditions of the system.

[0183] In some embodiments, one or more operating conditions of the system include the operating temperature of the system.

[0184] In some embodiments, if the operating temperature exceeds a threshold temperature, the motor coolant is sent to the suction side of the compressor where the pressure is lowest.

[0185] In some embodiments, if the operating temperature falls below a threshold temperature, the motor coolant is supplied between two or more compressor stages, or downstream of a subsequent compressor stage.

[0186] In another embodiment, the Disclosure provides a method for integrating carbon recovery with the operation of a heat pump, comprising: obtaining a fluid mixture through a direct air recovery (DAC) regeneration step; using the fluid mixture as a heat source for a heat pump system to condense and supercool the fluid mixture; and using the supercooled water separated from the fluid mixture as feedwater for the heat pump to generate steam for repeating the DAC regeneration step.

[0187] In another embodiment, the Disclosure provides a defrosting method comprising: providing a glycol heater at one or more locations in the system; diverting a certain amount of glycol to the glycol heater to heat a certain amount of glycol using at least a portion of the heat from the working fluid of the heat pump cycle; sending a certain amount of glycol to one or more heat exchangers(group) of the heat pump; and defrosting one or more heat exchangers(group) using a certain amount of glycol.

[0188] In some embodiments, one or more positions include the discharge position of the bottom cycle compressor, the discharge position of the top cycle compressor, or any position on the top cycle.

[0189] In some embodiments, the downstream of the cyclic refrigerant is used in parallel with the main flow of the cyclic refrigerant to heat a certain amount of glycol.

[0190] In some embodiments, the glycol heater is operated in parallel with the heat exchanger by (i) using the glycol heater to condense the refrigerant and (ii) sending the refrigerant to the outlet of the two-phase heat exchanger.

[0191] In some embodiments, one or more positions include positions prior to the expansion valve on the top cycle of the system, in which case the performance of the top cycle is improved by the subcooling of the refrigerant.

[0192] In some embodiments, supercooling degrades the quality of the steam at the evaporator inlet.

[0193] In some embodiments, one or more heat exchangers are defrosted in parallel using a single glycol loop, and the glycol in the single glycol loop is used to defrost each individual heat exchanger of one or more heat exchangers(s) sequentially or simultaneously.

[0194] In another embodiment, the disclosure provides a method for heating glycol used in a defrosting cycle, wherein the defrosting cycle includes single defrosting or parallel defrosting, utilizing the heat storage or heat release of a thermal storage device.

[0195] In another embodiment, the disclosure provides a system comprising an intake tube heat exchanger and an economizer, wherein the positions of the intake tube heat exchanger and the economizer are switchable in any cycle configuration.

[0196] In some embodiments, the positions of the suction tube heat exchanger and the economizer can be switched so that the liquid at the outlet of the system's steam generator is cooled by the suction tube heat exchanger before entering the economizer.

[0197] In another embodiment, the disclosure provides a system comprising a suction tube heat exchanger and an economizer, wherein the fluid flowing into the expansion valve of the economizer is drawn from the downstream of the suction tube heat exchanger, thereby cooling the fluid by at least 10 to 50°C.

[0198] In another embodiment, the disclosure provides a system comprising a plurality of compressor stages, wherein an economizer or intercooler is configured to be injected into one or more of the plurality of compressor stages, at least in part based on the operating mode of the system.

[0199] In some embodiments, the operating mode is based at least partially on whether one or more compressors are operating or bypassed during a given cycle.

[0200] In some embodiments, the operating mode is based at least partially on the total pressure ratio across one or more compressors.

[0201] In some embodiments, the operating mode is based at least partially on the ambient air temperature.

[0202] In another aspect, the disclosure provides a system comprising a plurality of compressor stages and a plurality of economizers located in intermediate coolers or injection positions, wherein the plurality of economizers are configured to operate in parallel or in series.

[0203] In another aspect, the disclosure provides a method of using ejectors in one or more cycles to recover energy in a throttling process of a refrigerant flow by at least partially increasing the heat absorption capacity and reducing the work performed by one or more compressors.

[0204] In another embodiment, the Disclosure provides a method using a flash tank economizer that includes restricting the fluid flowing out of a condenser to a low pressure to form a two-phase fluid, supplying the two-phase fluid to a flash tank, supplying cooling and flow rate increase to subsequent compressor stages by sending steam from the top of the flash tank to an intercooler between two or more compressor stages, and restricting the liquid at the bottom of the flash tank to evaporator pressure and heating the liquid by a heat source or bottom cycle.

[0205] In another embodiment, the Disclosure provides a method for using a flash tank between compressor stages, comprising: cooling a refrigerant and throttling it to an intermediate pressure to form a two-phase fluid after the fluid exits a first heat exchanger; mixing the two-phase fluid with the flow from the outlet of a first compressor to form a two-phase mixture; supplying the two-phase mixture to a flash tank; sending the saturated liquid at the bottom of the flash tank to a second heat exchanger to evaporate the refrigerant and introduce it into the inlet of a first compressor; and sending the saturated vapor at the top of the flash tank to the inlet of a second compressor.

[0206] In some embodiments, the method further includes closing a valve on the outlet stream located at the top of the flash tank, thereby directing all fluid discharged from the flash tank to a second heat exchanger.

[0207] In some embodiments, the method further includes closing a valve in the stream between the economizer and the second compressor, the valve being closed while the ambient temperature is high.

[0208] In another embodiment, the disclosure provides a system comprising a plurality of heat pumps and a centralized air coil group, the centralized air coil group comprising glycol loops configured to collect heat from the surrounding air.

[0209] In some embodiments, multiple heat pumps are installed in separate locations or in a centralized location.

[0210] In some embodiments, multiple heat pumps are arranged in series or in parallel.

[0211] In another embodiment, the disclosure provides a steam-generating air source heat pump comprising an integrated device having multiple heat exchanger functions, the integrated device comprising at least two inlet ports or at least two outlet ports.

[0212] In some embodiments, the integrated device is a combination of a steam generator, an economizer, and an intake tube heat exchanger.

[0213] In some embodiments, the integrated device is a combination of a two-phase heat exchanger, an economizer, and an evaporator.

[0214] In another embodiment, the present disclosure provides a steam generation method comprising: heating the working fluid of a topping cycle by transferring heat from the working fluid of a heat pump cycle to the working fluid of a topping cycle; compressing the working fluid of the topping cycle; and generating steam by transferring heat from the working fluid of the topping cycle to a supply water flow.

[0215] Another aspect of the present disclosure provides a non-temporary computer-readable medium containing machine-executable code that, when executed by one or more computer processors, performs any of the methods described above or elsewhere in this specification.

[0216] Another aspect of this disclosure provides a system comprising one or more computer processors and computer memory coupled thereto. The computer memory contains machine-executable code that, when executed by one or more computer processors, performs any of the methods described above or elsewhere in this specification.

[0217] Further aspects and advantages of this disclosure will be readily apparent to those skilled in the art from the following detailed description, which shows and describes only exemplary embodiments of this disclosure. As will be apparent from the following description, other different embodiments of this disclosure are possible, and some of their details can be modified in various obvious ways without departing from this disclosure. Accordingly, the drawings and description are illustrative in nature and not limiting. Reference

[0218] All publications, patents, and patent applications described herein are incorporated by reference to the same extent as any individual publication, patent, or patent application is specifically and individually indicated as being incorporated by reference. If any publication, patent, or patent application incorporated by reference conflicts with any disclosure herein, this specification shall supersede and / or take precedence over such conflicting material. [Brief explanation of the drawing]

[0219] Novel features of this disclosure are described in detail in the appended claims. The features and advantages of this disclosure will be better understood by referring to the following detailed description illustrating exemplary embodiments utilizing the principles of this disclosure, and to the appended drawings (hereinafter also referred to as "Figure" and "FIG").

[0220] [Figure 1] Figure 1 shows a heat pump system according to some embodiments described herein.

[0221] [Figure 2] Figure 2 shows a diagram of a cascade heat pump system according to some embodiments described herein.

[0222] [Figure 3] Figure 3 shows a schematic diagram of a steam generation system according to some embodiments described herein.

[0223] [Figure 4] Figure 4 shows an example of a heat pump cycle according to some embodiments described herein.

[0224] [Figure 5] Figure 5 shows an example of a heat pump cycle according to some embodiments described herein.

[0225] [Figure 6] Figure 6 shows examples of compressors incorporated into some embodiments described herein.

[0226] [Figure 7] Figure 7 shows an example of a heat pump cycle with an oil loop according to some embodiments described herein.

[0227] [Figure 8A]Figure 8A shows a schematic diagram of an example of a compressor according to some embodiments described herein.

[0228] [Figure 8B] Figure 8B shows a schematic diagram of an example of a compressor according to some embodiments described herein.

[0229] [Figure 9] Figure 9 shows an example of a glycol loop according to some embodiments described herein.

[0230] [Figure 10] Figure 10 shows an example of a heat pump cycle according to some embodiments described herein.

[0231] [Figure 11] Figure 11 shows an example of a heat pump cycle according to some embodiments described herein.

[0232] [Figure 12] Figure 12 shows some examples of steam generation systems according to some embodiments described herein.

[0233] [Figure 13] Figure 13 shows an example of a heat pump cycle including a motor coolant loop according to some embodiments described herein.

[0234] [Figure 14] Figure 14 shows an example of a heat pump cycle according to some embodiments described herein. [Figure 15] Figure 15 shows an example of a heat pump cycle according to some embodiments described herein.

[0235] [Figure 16A] Figure 16A shows an example of a steam generation system including a heat transfer fluid cycle according to some embodiments described herein.

[0236] [Figure 16B] Figure 16B shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16C] Figure 16C shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16D] Figure 16D shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16E] Figure 16E shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16F] Figure 16F shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16G] Figure 16G shows an example of the operation of the steam generation system shown in Figure 16A. [Figure 16H] Figure 16H shows an example of the operation of the steam generation system shown in Figure 16A.

[0237] [Figure 17] Figure 17 shows an example of a steam generation system with a heat transfer fluid cycle according to some embodiments described herein. [Figure 18] Figure 18 shows an example of a steam generation system with a heat transfer fluid cycle according to some embodiments described herein. [Figure 19] Figure 19 shows an example of a steam generation system with a heat transfer fluid cycle according to some embodiments described herein.

[0238] [Figure 20] Figure 20 shows an example of a steam generation system with a refrigeration system according to some embodiments described herein.

[0239] [Figure 21] Figure 21 shows an example of a steam generation system according to some embodiments described herein.

[0240] [Figure 22]Figure 22 shows an example of a steam generation system including a refrigeration system according to some embodiments described herein. [Figure 23] Figure 23 shows an example of a steam generation system including a refrigeration system according to some embodiments described herein. [Figure 24] Figure 24 shows an example of a steam generation system including a refrigeration system according to some embodiments described herein.

[0241] [Figure 25] Figure 25 shows an example of a steam generation system including a refrigeration system according to some embodiments described herein. [Figure 26] Figure 26 shows an example of a steam generation system including a refrigeration system according to some embodiments described herein.

[0242] [Figure 27] Figure 27 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein.

[0243] [Figure 28] Figure 28 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 29] Figure 29 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 30] Figure 30 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 31] Figure 31 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 32] Figure 32 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 33]Figure 33 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein.

[0244] [Figure 34] Figure 34 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein. [Figure 35] Figure 35 shows an example of a steam generation system capable of generating steam and / or hot water according to some embodiments described herein.

[0245] [Figure 36] Figure 36 shows an example of a heat pump cycle with an air heating element according to some embodiments described herein.

[0246] [Figure 37] Figure 37 shows an example of a heat pump cycle with an air heating element according to some embodiments described herein.

[0247] [Figure 38] Figure 38 shows an example of a heat pump cycle according to some embodiments described herein.

[0248] [Figure 39] Figure 39 shows an example of a heat pump cycle according to some embodiments described herein.

[0249] [Figure 40A] Figure 40A shows an example of a heat pump cycle with an additional compressor according to some embodiments described herein.

[0250] [Figure 40B] Figure 40B shows an example of the operation of the steam generation system in Figure 16, with an additional compressor added as shown in Figure 40A. [Figure 40C]Figure 40C shows an operation example of the steam generation system of FIG. 16 with an additional compressor added as shown in FIG. 40A. [Figure 40D] Figure 40D shows an operation example of the steam generation system of FIG. 16 with an additional compressor added as shown in FIG. 40A. [Figure 40E] Figure 40E shows an operation example of the steam generation system of FIG. 16 with an additional compressor added as shown in FIG. 40A. [Figure 40F] Figure 40F shows an operation example of the steam generation system of FIG. 16 with an additional compressor added as shown in FIG. 40A.

[0251] [Figure 41] Figure 41 shows an example of a steam generation system according to some embodiments described herein.

[0252] [Figure 42] Figure 42 shows an example of a steam generation system configured to generate a supercritical fluid according to some embodiments described herein.

[0253] [Figure 43] Figure 43 shows an example of a heat pump cycle including a steam compressor according to some embodiments described herein.

[0254] [Figure 44] Figure 44 shows an example of a steam generation system including an additional topping cycle according to some embodiments described herein. [Figure 45] Figure 45 shows an example of a steam generation system including an additional topping cycle according to some embodiments described herein.

[0255] [Figure 46] Figure 46 shows an example of a steam generation system including a bypass line according to some embodiments described herein. ]> [Figure 47]Figure 47 shows an example of a steam generation system including a bypass line according to some embodiments described herein.

[0256] [Figure 48] Figure 48 shows an example of a steam generation system according to some embodiments described herein.

[0257] [Figure 49] Figure 49 shows an example of a heat pump cycle with an air heater according to some embodiments described herein. [Figure 50] Figure 50 shows an example of a heat pump cycle with an air heater according to some embodiments described herein.

[0258] [Figure 51] Figure 51 shows an example of a steam generation system with a defrosting spray line according to some embodiments described herein. [Figure 52] Figure 52 shows an example of a steam generation system with a defrosting spray line according to some embodiments described herein. [Figure 53] Figure 53 shows an example of a steam generation system with a defrosting spray line according to some embodiments described herein.

[0259] [Figure 54] Figure 54 shows an example of a steam generation system according to some embodiments described herein. [Figure 55] Figure 55 shows an example of a steam generation system according to some embodiments described herein. [Figure 56] Figure 56 shows an example of a steam generation system according to some embodiments described herein.

[0260] [Figure 57] Figure 57 shows an example of a heat pump cycle with a waste heat function according to some embodiments described herein. [Figure 58] Figure 58 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 59] Figure 59 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 60] Figure 60 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 61] Figure 61 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 62] Figure 62 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 63] Figure 63 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 64] Figure 64 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 65] Figure 65 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification. [Figure 66] Figure 66 shows an example of a heat pump cycle with a waste heat function according to some embodiments described in this specification.

[0261] [Figure 67] Figure 67 shows an example of a steam generation system with a waste heat function according to some embodiments described in this specification.

[0262] [Figure 68] Figure 68 shows a computer system programmed or configured to execute the method described in this specification.

[0263] [Figure 69A]Figure 69A shows an example of a steam generation system with a glycol heater according to some embodiments described herein. [Figure 69B] Figure 69B shows an example of a steam generation system with a glycol heater according to some embodiments described herein. [Figure 70] Figure 70 shows an example of a steam generation system with a glycol heater according to some embodiments described herein. [Figure 71] Figure 71 shows an example of a steam generation system with a glycol heater according to some embodiments described herein. [Figure 72] Figure 72 shows an example of a steam generation system with a glycol heater according to some embodiments described herein.

[0264] [Figure 73] Figure 73 shows an example of a steam generation system with a heat storage function, according to some embodiments described herein.

[0265] [Figure 74] Figure 74 shows an example of a steam generation system with an economizer according to some embodiments described herein. [Figure 75] Figure 75 shows an example of a steam generation system with an economizer, according to some embodiments described herein.

[0266] [Figure 76] Figure 76 shows an example of a steam generation system with an intercooler according to some embodiments described herein. [Figure 77] Figure 77 shows an example of a steam generation system with an intercooler according to some embodiments described herein. [Figure 78] Figure 78 shows an example of a steam generation system with an intercooler according to some embodiments described herein. [Figure 79]Figure 79 shows an example of a steam generation system with an intercooler according to some embodiments described herein.

[0267] [Figure 80] Figure 80 shows an example of a steam generation system with an ejector, according to some embodiments described herein.

[0268] [Figure 81] Figure 81 shows an example of a steam generation system configured to produce a supercritical fluid, according to some embodiments described herein.

[0269] [Figure 82] Figure 82 shows an example of a steam generation system with a supercooler according to some embodiments described herein. [Figure 83] Figure 83 shows an example of a steam generation system with a supercooler according to some embodiments described herein. [Figure 84] Figure 84 shows an example of a steam generation system with a supercooler according to some embodiments described herein. [Figure 85] Figure 85 shows an example of a steam generation system with a supercooler according to some embodiments described herein.

[0270] [Figure 86] Figure 86 shows an example of a steam generation system in which multiple heat pumps are connected in series, according to some embodiments described herein.

[0271] [Figure 87] Figure 87 shows an example of a steam generation system in which multiple heat pumps are connected in parallel, according to some embodiments described herein.

[0272] [Figure 88]Figure 88 shows an example of a steam generation system integrated in series with a carbon recovery unit, according to some embodiments described herein.

[0273] [Figure 89] Figure 89 shows an example of a heat pump cycle using motor coolant flow according to some embodiments described herein. [Figure 90] Figure 90 shows an example of a heat pump cycle using motor coolant flow according to some embodiments described herein.

[0274] [Figure 91] Figure 91 shows an example of a steam generation system equipped with a steam compressor, according to some embodiments described herein. [Figure 92] Figure 92 shows an example of a steam generation system equipped with a steam compressor, according to some embodiments described herein.

[0275] [Figure 93] Figure 93 shows an example of a steam generation system using a motor cooling flow according to some embodiments described herein.

[0276] [Figure 94] Figure 94 shows an example of a bottoming cycle with a heat recovery heat exchanger according to some embodiments described herein.

[0277] [Figure 95] Figure 95 shows an example of a steam generation system with a flash tank, according to some embodiments described herein.

[0278] [Figure 96A] Figure 96A shows an example of a steam generation system with a heat storage tank according to some embodiments described herein. [Figure 96B]Figure 96B shows an example of a steam generation system with a heat storage tank according to some embodiments described herein. [Figure 96C] Figure 96C shows an example of a steam generation system with a heat storage tank according to some embodiments described herein.

[0279] [Figure 97] Figure 97 shows an example of a steam generation system with a heat storage tank according to some embodiments described herein.

[0280] [Figure 98] Figure 98 shows an example of a steam generation system with a heat transfer fluid cycle according to some embodiments described herein. [Modes for carrying out the invention]

[0281] While various embodiments are shown and described herein, it will be apparent to those skilled in the art that such embodiments are provided only as examples. Those skilled in the art can conceive of various modifications, alterations, and alternatives without departing from this disclosure. It should be understood that various alternative forms are possible for the embodiments described herein.

[0282] If the terms “at least,” “greater than,” or “greater than or equal to” precede the first number in a series of two or more numbers, then the terms “at least” or “greater than” apply to each number in that series.

[0283] If the first number in a series of two or more numbers is preceded by the terms "not more," "less than," or "less than or equal to," then the terms "less than or equal to" or "less than" apply to each number in that series.

[0284] As used herein, the terms “about” or “near” typically refer to within 15%, 10%, 9%, 8%, 7%, 6%, 5%, 4%, 3%, 2%, or 1% (plus or minus) of the specified value.

[0285] As used herein, the singular forms "a," "an," and "the" also include the plural form unless the context clearly indicates otherwise. definition

[0286] As used herein, the term “heat exchanger” generally refers to a mechanism configured to transfer heat from one or more first fluids to one or more second fluids. In some cases, a heat exchanger may be a single heat exchanger and / or a configuration of multiple heat exchangers. A configuration of multiple heat exchangers may consist of two or more heat exchangers. A configuration of multiple heat exchangers may include two or more heat exchangers in parallel, in series, or in combination thereof. A heat exchanger may refer to a steam generator, a hot water generator, an evaporator, a condenser, a two-phase heat exchanger, a three-fluid heat exchanger, a heat recovery heat exchanger, a waste heat exchanger, a suction tube heat exchanger, a subcooler, a superheat remover, and / or a combination thereof. A combination of one or more heat exchangers may enable cost reduction, improved package efficiency, or improved system operation. A heat exchanger may be an air heat exchanger. A heat exchanger can change the temperature, pressure, composition, phase, or combination thereof of one or more fluids passing through it. The heat exchangers referred to herein are one or more of the heat exchangers described above, and any type of heat exchanger can be changed or replaced with any type of heat exchanger based on the desired function and / or operation. The heat exchangers referred to herein refer to or are shell-and-tube heat exchangers, brazed plates, welded plates, gasket plates, plate fins, or microtubes. In some cases, a heat exchanger refers to a unit having one or more of the above elements. A heat exchanger may have fin tubes on the side that is thermally in contact with the ambient airflow, may be composed of microtubes, may be additively manufactured, and / or may be composed of tube-in-tube heat exchangers. A heat exchanger may have multiple inlet or outlet ports to perform multiple functions of a heat pump. To increase the efficiency of the heat exchangers described herein, additional elements and configurations may be selected, such as one or more heat transfer enhancers selected from the group consisting of expanded surfaces, fins, turbulence generators that increase turbulence of the fluid passing through the heat exchanger (e.g., twisted tape), and / or surface treatments (e.g., porous media).

[0287] As used herein, the term “working fluid” generally refers to a substance (e.g., liquid, vapor, gas, or combination thereof) that interacts with at least one element of a system. A working fluid refers to the heat transfer fluid of a system. A working fluid may also refer to a supply fluid (e.g., a supply stream). A working fluid may also refer to a fluid at a stage in a system and / or cycle. A working fluid may dissipate heat. A working fluid may absorb heat. A working fluid may change composition and / or phase while circulating through a cycle. A working fluid may be a coolant, refrigerant, and / or lubricant. Examples of working fluids include water, water vapor, glycol, air, fluorocarbons, hydrofluoroolefins, hydrofluoroethers, hydrochlorofluoroolefins, hydrocarbons, ammonia (NH3), water (H2O), carbon dioxide (CO2), and pentane (C5H2). 12 ), butane (C4H 10 This may include isobutane (HC(CH3)3), propane (C3H8), propene (C3H6), or combinations thereof. In this specification, the working fluid may refer to one or more of the working fluids described above, and any type of working fluid may be changed or substituted for any type of working fluid based on the desired function and / or operation.

[0288] As used herein, the term “compressor” generally refers to a mechanism for increasing the pressure of a substance. In one example, the compressor may be a single compressor or a multistage compressor configuration. A multistage compressor configuration may consist of two or more compressors. A multistage compressor configuration may comprise two or more compressors in parallel, in series, or a combination thereof. In one example, the compressor may consist of a multistage compressor, a double-ended compressor, a centrifugal compressor, a lubricated compressor, an oil-free compressor, an axial-flow compressor, a steam compressor, a single-shaft compressor, a magnetically coupled compressor, a multi-shaft compressor, and / or positive displacement compressors (e.g., screw compressors, scroll compressors, reciprocating compressors, etc.). A double-ended compressor may be a double-ended centrifugal compressor. In some embodiments, the centrifugal compressor may be an oil-free centrifugal compressor. An oil-free centrifugal compressor may be configured to supply a refrigerant to the compressor shaft and / or rotor. The refrigerant evaporates at least partially within the motor cavity of the compressor. The compressors described herein can be connected to one or more of the heat exchangers described above, and any type of compressor can be changed to another type of compressor based on the desired function and / or operation.

[0289] The terms "hot water" or "high-temperature water" may refer to a stream of water having a temperature of approximately 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, 60°C, 65°C, 70°C, 75°C, 80°C, 85°C, 90°C, 95°C, or higher. The temperature of hot water may be approximately 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, 70°C, 65°C, 60°C, 55°C, 50°C, 45°C, 40°C, 35°C, 30°C, 25°C, 20°C, 15°C, 10°C, 5°C, or lower. The temperature of hot water may be between any two of the above values, for example, between approximately 40°C and approximately 80°C.

[0290] The terms “hot water” or “cold water” may refer to a stream of water having a temperature of approximately 1°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, 60°C, 65°C, 70°C, 75°C, 80°C, 85°C, 90°C, 95°C, or higher. The temperature of hot water may be approximately 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, 70°C, 65°C, 60°C, 55°C, 50°C, 45°C, 40°C, 35°C, 30°C, 25°C, 20°C, 15°C, 10°C, 5°C, or lower. The temperature of hot water may be between any two of the above values, for example, between approximately 15°C and approximately 40°C. Water vapor generation system

[0291] In one embodiment, the present disclosure provides a system for generating steam. In some embodiments, the system includes a heat pump system (e.g., a heat pump cycle). In some embodiments, the system may be configured as a cascade steam heat pump system. In some embodiments, the system may include a transfer fluid pump cycle (e.g., a heat transfer fluid cycle) and a heat pump system including at least a first heat pump cycle and a second heat pump cycle, as shown in the non-limiting examples of Figures 16-19. As used herein, the term “transfer fluid pump cycle” means and may be used interchangeably with “heat transfer fluid cycle.” In some embodiments, the first heat pump cycle may be configured as a bottom cycle and the second heat pump cycle may be configured as a top cycle. In some embodiments, the transfer fluid pump cycle (e.g., a heat transfer fluid cycle) may be configured to circulate a transfer fluid (e.g., a working fluid). In some embodiments, the transfer fluid pump cycle (e.g., a heat transfer fluid cycle) may include an initial heat exchanger, a first heat exchanger, and a circulation pump. In some embodiments, the initial heat exchanger and / or heat exchanger of the described system may be an air source heat exchanger. In this specification, the term “air-source heat exchanger” may be used interchangeably with the term “air-source heat exchanger.” In some embodiments, the initial heat exchanger (e.g., air-source heat exchanger) is isolated from the first and second heat pump cycles (e.g., via a heat transfer fluid cycle). The air-source heat exchanger may be configured to be located separately from the first and second heat pump cycles (e.g., via a heat transfer fluid cycle).Advantages of a fluid-transmitting pump cycle include improved efficiency, the ability to decouple the air-source heat exchanger from the main components of the heat pump system (such as placing the air-source heat exchanger outdoors and the heat pump inside or near the steam end-user), avoidance of long piping routes for pressurized refrigerant, simplified control (such as a simple method of defrosting in cold weather by heating the glycol loop), and / or ease of integration with other processes (such as integration with a waste heat source or refrigeration system). Advantages of placing the heat pump near the steam end-user include generating lower-pressure steam and / or improving the efficiency of the heat pump. Advantages of shorter piping routes include a reduced risk of leakage and / or improved heat pump efficiency due to lower pressure drops.

[0292] In one embodiment, the present disclosure provides a steam generation system. In some embodiments, the system may be a cascade steam heat pump system. The system may further comprise a transfer fluid pump cycle (e.g., a heat transfer fluid cycle) and one or more heat pump cycles (e.g., a first heat pump cycle and a second heat pump cycle). The transfer fluid pump cycle (e.g., a heat transfer fluid cycle) may be configured to circulate a transfer fluid (e.g., a working fluid). The transfer fluid pump cycle (e.g., a heat transfer fluid cycle) may comprise a transfer fluid exchanger, a first heat exchanger, and a circulation pump. In some embodiments, the transfer fluid exchanger may be in fluid communication with the circulation pump and configured to receive the first transfer fluid from the circulation pump. In some embodiments, the transfer fluid absorbs heat in the transfer fluid exchanger. In some embodiments, the transfer fluid exchanger is in fluid communication with the first heat exchanger. In some embodiments, the first heat exchanger may be configured to discharge heat from the transfer fluid to the first working fluid of the first heat pump cycle. In some embodiments, the first working fluid absorbs heat from the transfer fluid working fluid in the first heat exchanger. In some embodiments, a circulation pump may be in fluid communication with the first heat exchanger and configured to receive the transfer fluid working fluid from the first heat exchanger.

[0293] In some embodiments, the first heat pump cycle may be configured to circulate a first working fluid. The first heat pump cycle may comprise a first heat exchanger, a first compressor, a second heat exchanger, and a first expansion valve. In some embodiments, the first heat exchanger may be configured to fluidly communicate with a first expansion valve and receive the first working fluid from the first expansion valve. In some embodiments, the first working fluid absorbs heat from a different working fluid (e.g., a transfer fluid) in the first heat exchanger. The first compressor may fluidly communicate with the first heat exchanger and receive the first working fluid from the first heat exchanger. The first compressor may increase the pressure and temperature of the first working fluid. The compressor may increase the pressure by a coefficient of about 1.1, 1.2, 1.5, 2, 5, 10, 20, or 30 or more. The compressor may increase the pressure by a coefficient between any two of the values ​​described herein. The compressor can raise the temperature by approximately 5°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 80°C, 100°C, 120°C, or 150°C. The temperature rise by the compressor may be between any two of the values ​​described herein. A second heat exchanger may be in fluid communication with the compressor (e.g., the first compressor) and configured to receive a first working fluid from the first compressor. The second heat exchanger may discharge heat from the first working fluid to a different working fluid (e.g., a second working fluid). In some embodiments, a first expansion valve may be in fluid communication with the second heat exchanger and configured to receive the first working fluid from the second heat exchanger. The first expansion valve can expand the working fluid (e.g., the first working fluid) to a low pressure. In some embodiments, the first heat pump cycle may include a heat exchanger. In this specification, the term “heat exchanger” may refer to a unit configured to operate as one or more types of heat transfer units, or a unit comprising one or more types of heat transfer units. For example, a heat exchanger may be configured to operate as one or more of a two-phase heat exchanger, an economizer, and / or an evaporator. Such a heat exchanger may be configured to have two or more inlet ports and / or two or more outlet ports.These multiple inlet and / or outlet ports may allow multiple fluid flows to enter the heat exchanger without mixing. Such a heat exchanger may provide one type of heat exchange with respect to a first fluid flow, while simultaneously providing the same or a different type of heat exchange with respect to a second fluid flow. For example, the heat exchanger described herein may be configured to transfer heat between a fluid flow of a first phase and a second fluid flow of a second phase. The second phase may be the same as or different from the first phase. Alternatively, or in addition, the heat exchanger may operate as an economizer. The heat exchanger may operate as a two-phase heat exchanger and economizer. The heat exchanger can operate as a two-phase heat exchanger, economizer, and evaporator. In some embodiments, the first heat pump cycle may include a two-phase ejector. The two-phase ejector can recover energy in the throttling process of the refrigerant flow.

[0294] In some embodiments, the second heat pump cycle may be configured to circulate a second working fluid. In some embodiments, the second heat pump cycle may include a second heat exchanger, a second compressor, a third heat exchanger, and a second expansion valve. The second heat exchanger is in fluid communication with the second expansion valve and can receive the second working fluid from the second expansion valve. In some embodiments, the second working fluid absorbs heat from a different working fluid (e.g., a first working fluid) in the second heat exchanger. The second compressor is in fluid communication with the second heat exchanger and can receive the second working fluid from the second heat exchanger. In some embodiments, the second compressor can increase the pressure and temperature of the working fluid (e.g., the second working fluid). The compressor can increase the pressure by a coefficient of about 1.1, 1.2, 1.5, 2, 5, 10, 20, or 30 or more. The compressor can increase the pressure by a coefficient between any two values ​​specified herein. The compressor can increase the temperature by about 5°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 80°C, 100°C, 120°C, or 150°C. The temperature increase by the compressor may be between any two values ​​specified herein. In some embodiments, a third heat exchanger is in fluid communication with the second compressor and can receive a second working fluid from the second compressor. The third heat exchanger may be in fluid communication with a steam generating system. The third heat exchanger can discharge heat from the second working fluid into a third working fluid in the steam generating system. The third working fluid may contain water. A second expansion valve is in fluid communication with the third heat exchanger and can receive a second working fluid from the third heat exchanger. A second expansion valve may be configured to expand the working fluid (e.g., a second working fluid) to a lower pressure. In some embodiments, the second heat pump cycle may include a heat exchanger that functions as a combination of a steam generator, an economizer, and an intake tube heat exchanger. In some embodiments, the second heat pump cycle may include a two-phase ejector.

[0295] In some embodiments, the system may further include a first suction tube heat exchanger. The first suction tube heat exchanger may be located in a first heat pump cycle or a second heat pump cycle. The first suction tube heat exchanger may be located between a heat exchanger (e.g., a first heat exchanger) and a compressor (e.g., a first compressor). Alternatively, the first suction tube heat exchanger may be located between a heat exchanger (e.g., a second heat exchanger) and a valve (e.g., a first expansion valve). The first suction tube heat exchanger may pre-cool the working fluid (e.g., a first working fluid) before it receives heat in the heat exchanger (e.g., a first heat exchanger). In some embodiments, the system may further include a second suction tube heat exchanger. The second suction tube heat exchanger may be located between a heat exchanger (e.g., a second heat exchanger) and a compressor (e.g., a second compressor). Alternatively, the second suction tube heat exchanger may be positioned between the heat exchanger (e.g., the third heat exchanger) and the valve (e.g., the second expansion valve). The second suction tube heat exchanger may pre-cool the working fluid (e.g., the second working fluid) before it receives heat from the heat exchanger (e.g., the third heat exchanger). The third heat exchanger may be a steam generator.

[0296] Advantages of suction tube heat exchangers include pre-cooling of the working fluid before it enters the heat exchanger, pre-heating of the working fluid before it enters the compressor, and / or reduction of the fluid density before it enters the compressor. The advantage of pre-heating the working fluid before it enters the compressor is that it prevents droplet formation and reduces the risk of compressor damage. The advantage of reducing the fluid density before it enters the compressor is an increase in volumetric flow rate, which can help balance the speed between compressor stages in higher head situations.

[0297] In some embodiments, the heat transfer fluid cycle may circulate a working fluid (e.g., a heat transfer working fluid). The working fluid may include glycol. The heat transfer fluid cycle may include one or more heaters. One or more heaters may be coupled to the heat transfer cycle downstream of a heat exchanger (e.g., an evaporator). One or more heaters may include electric resistance heaters. In some embodiments, the working fluid (e.g., a heat transfer fluid) may be heated by heating and / or defrosting mechanisms and / or methods described herein. In some embodiments, the heat transfer fluid cycle may include a glycol loop, as shown in the non-limiting examples of Figures 55-56. The glycol loop may include one or more heaters. One or more heaters may heat the working fluid of the glycol loop. One or more heaters may include electric resistance heaters. One or more heaters may include glycol heaters configured to discharge heat from the working fluid of a first heat pump cycle or a second heat pump cycle. The glycol heaters may be located at various positions within the first heat pump cycle or the second heat pump cycle. For example, the glycol heater may be located downstream of the first or second compressor. The glycol heater may be located at any position in the first heat pump cycle. The glycol heater may be located at any position in the second heat pump cycle. The glycol heater may be located upstream of the evaporator and / or upstream of the expansion valve. An advantage of placing the glycol heater upstream of the expansion valve is improved system efficiency. The glycol heater may be configured to receive a portion of the working fluid in either the first or second heat pump cycle, with the remainder of the working fluid bypassing the glycol heater. An advantage of diverting the fluid to the glycol heater is reduced pressure loss in the heat pump cycle with the glycol heater (e.g., reduced pressure loss on the first heat pump cycle side of the heat exchanger). One or more heaters may be the thermal accumulators described herein. One or more heaters may be a combination selected from the electric resistance heater, the glycol heater, and the thermal accumulators.The working fluid in the glycol loop may be heated by heating and / or defrosting mechanisms and / or methods described herein. In some embodiments, the glycol loop may circulate at least a portion of the working fluid from the cycle (e.g., a heat transfer fluid cycle). The glycol loop may receive the working fluid downstream of one or more heat exchangers in the cycle. The glycol loop may raise the temperature of the working fluid and deliver it upstream of one or more heat exchangers. The glycol loop may raise the temperature of the working fluid to about 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, or 100°C. The temperature rise of the working fluid may be between any two values ​​described herein. The glycol loop may raise the temperature of the working fluid from below 0°C to about 40°C. One or more heat exchangers may include one or more air source heat exchangers. The air source heat exchangers may be arranged in parallel as shown in the non-limiting example in Figure 56. The glycol loop may include one or more glycol loops. A system with multiple glycol loops may operate continuously without downtime for defrosting. One or more glycol loops may be coupled one-to-one with one or more heat exchangers. Each of the one or more glycol loops may circulate at least a portion of the working fluid from a cycle (e.g., a heat transfer fluid cycle). One or more glycol loops may receive at least a portion of the working fluid downstream of the corresponding heat exchangers in the cycle. One or more glycol loops may raise the temperature of a portion of the working fluid, send a portion of the working fluid upstream of the corresponding heat exchanger, and return a first portion of the working fluid upstream of the corresponding air source heat exchanger. The heat exchangers may include air source heat exchangers. In some embodiments, the working fluid may contain glycol. In some embodiments, each of the one or more glycol loops is configured to function independently of one another. In some embodiments, one or more glycol loops may include one or more valves configured to shut off the fluid when not in use.

[0298] In one embodiment, the present disclosure provides a system including a heat pump system (e.g., one or more heat pump cycles). In some embodiments, the heat pump system can generate cool air. In some embodiments, the cool air can be used to cool the space of a facility. In some embodiments, after the space has been cooled, the cool air can be discharged from the space as warm air. In some embodiments, after the space has been cooled, the cool air can be returned to the heat pump as warm or hot air.

[0299] In one embodiment, the Disclosure provides a system comprising a heat pump system (e.g., one or more heat pump cycles) and a carbon recovery system. In some embodiments, the carbon recovery system may be a point source system. In some embodiments, the carbon recovery system may be a direct air recovery system. In some embodiments, the carbon recovery system may require a regeneration step of condensing steam. In some embodiments, the steam quality of the outlet steam may be about 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.65, 0.7, 0.75, 0.8, 0.85, 0.9, or 0.95 or higher. The steam quality of the outlet steam may be between any two values ​​described herein. In some embodiments, the outlet steam may contain a fluid mixture. The fluid mixture may contain one or more of carbon dioxide (CO2), water, nitrogen, and oxygen. In some embodiments, the fluid mixture may be used as a heat source for the heat pump. In some embodiments, the heat pump may condense the fluid mixture. Alternatively, or in addition, a glycol loop or a water loop may condense the fluid mixture. In some embodiments, at least a portion of the CO2 can be separated from the fluid mixture. At least about 70, 80, or 90 percent of the CO2 in the fluid mixture may be separated. All of the CO2 in the fluid mixture may be separated. In some embodiments, at least a portion of the water (H2O) can be separated from the fluid mixture. At least about 70, 80, or 90 percent of the H2O in the fluid mixture may be separated. All of the H2O in the fluid mixture may be separated. In some embodiments, water may be used as input to the heat pump (e.g., feedwater converted to steam). In some embodiments, steam from the heat pump may be used as input to the regeneration step. In some embodiments, steam is generated by a natural gas boiler. Operating conditions

[0300] In some embodiments, the ambient airflow temperature may be approximately 50°C, 40°C, 30°C, 25°C, 20°C, 15°C, 10°C, 5°C, 0°C, -5°C, -10°C, -15°C, -20°C, -25°C, -30°C, -35°C, or -40°C or lower. The ambient airflow temperature may be approximately -40°C, -35°C, -30°C, -25°C, -20°C, -15°C, -10°C, -5°C, 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, or 40°C or higher. The ambient airflow temperature may be between the two temperatures mentioned above, for example, between approximately 0°C and approximately 25°C.

[0301] In some embodiments, the temperature of the supply steam (e.g., a supply stream containing water) to the heat exchanger (e.g., a steam generator) of the system described herein may be about 150°C, 140°C, 130°C, 120°C, 110°C, 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, 70°C, 65°C, 60°C, 55°C, 50°C, 45°C, 40°C, 35°C, 30°C, 25°C, 20°C, 15°C, 10°C, or 5°C or less. The temperature of the supply stream (e.g., a supply stream containing water) to the heat exchanger (e.g., a steam generator) of the system described herein may be about 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, 60°C, 65°C, 70°C, 75°C, 80°C, 85°C, 90°C, 95°C, 100°C, 110°C, 120°C, 130°C, 140°C, or 150°C or higher. The temperature of the supply stream (e.g., a supply stream containing water) to the heat exchanger (e.g., a steam generator) of the system described herein may be between the two temperatures above, for example, about 15°C and about 95°C.

[0302] In some cases, the first heat pump cycle (e.g., the bottom cycle) may receive an ambient airflow having an air temperature of approximately 150°C, 140°C, 130°C, 120°C, 110°C, 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, 70°C, 65°C, 60°C, 55°C, 50°C, 45°C, 40°C, 35°C, 30°C, 25°C, 20°C, 15°C, 10°C, or 5°C or lower, and output a working fluid with a temperature of approximately 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, 60°C, 65°C, 70°C, 75°C, 80°C, 85°C, 90°C, 95°C, 100°C, 110°C, 120°C, 130°C, 140°C, or 150°C or higher.

[0303] In some embodiments, a second heat pump cycle (e.g., a top cycle) may receive working fluid at temperatures of approximately 150°C, 140°C, 130°C, 120°C, 110°C, 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, 70°C, 65°C, 60°C, 55°C, 50°C, 45°C, 40°C, 35°C, 30°C, 25°C, 20°C, 15°C, 10°C, and 5°C or lower, and output working fluid at temperatures of 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, 60°C, 65°C, 70°C, 75°C, 80°C, 85°C, 90°C, 95°C, 100°C, 110°C, 120°C, 130°C, 140°C, and 150°C or higher. For example, a first heat pump (e.g., bottom cycle) may receive ambient airflow at an air temperature of 15°C and supply heat (e.g., output a working fluid) at a temperature of 65°C, and a second heat pump (e.g., top cycle) may receive a working fluid at 65°C via a heat exchanger coupled to the first and second heat pump cycles, and the second heat pump cycle may generate steam at a temperature of 150°C. Performance metrics

[0304] In some embodiments, the coefficient of performance of the system may be approximately 1, 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, 2.0, 2.1, 2.2, 2.3, 2.4, 2.5, 2.6, 2.7, 2.8, 2.9, 3.0, 3.5, 4.0, 4.5, or 5 or greater. The coefficient of performance of the system may be between any two values ​​described herein.

[0305] In some embodiments, the system may include a compressor. The isentropic efficiency of the compressor may be about 60%, 70%, 80%, 90%, or higher. The isentropic efficiency of the compressor may be between any two values ​​specified herein. The compressor may have a motor having an efficiency of about 70%, 80%, 85%, 90%, 95%, 96%, 97%, 98%, or 99% or higher. The efficiency of the motor may be between any two values ​​specified herein. The compressor may be designed to have a thrust of about 400 pounds, 300 pounds, 250 pounds, 200 pounds, 175 pounds, 150 pounds, 125 pounds, or less than 100 pounds (e.g., via double-ended type, preload spring, and / or magnetic coil). The thrust of the compressor may be between any two values ​​specified herein.

[0306] In some embodiments, the steam flow rate of the system may be approximately 0.5 t / hour, 1 t / hour, 2 t / hour, 4 t / hour, 6 t / hour, 8 t / hour, 10 t / hour, 12 t / hour, 15 t / hour, or 20 t / hour or more. In some embodiments, the steam flow rate of the system may be approximately 0.5 t / hour, 1 t / hour, 2 t / hour, 4 t / hour, 6 t / hour, 8 t / hour, 10 t / hour, 12 t / hour, 15 t / hour, or 20 t / hour or less. The steam flow rate may be between any two values ​​described herein.

[0307] In some embodiments, the system may include an air source heat exchanger. The capacity of the air source heat exchanger may be approximately 100 kW, 200 kW, 300 kW, 400 kW, 500 kW, 600 kW, 800 kW, 1 MW, 2 MW, 4 MW, 6 MW, 8 MW, or 10 MW or more. The capacity of the air source heat exchanger may be approximately 100 kW, 200 kW, 300 kW, 400 kW, 500 kW, 600 kW, 800 kW, 1 MW, 2 MW, 4 MW, 6 MW, 8 MW, or 10 MW or less. The capacity of the air source heat exchanger may be between any two values ​​described herein.

[0308] In some embodiments, the system may comprise a glycol loop and an evaporator. The pinch point between the glycol loop and the evaporator saturation temperature may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or higher. The pinch point between the glycol loop and the evaporator saturation temperature may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or lower. The pinch point between the glycol loop and the evaporator saturation temperature may be between any two values ​​described herein.

[0309] In some embodiments, the system may include a steam generator and steam. The pinch point between the top-cycle refrigerant saturation temperature and the steam in the steam generator may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or higher. The pinch point between the top-cycle refrigerant saturation temperature and the steam in the steam generator may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or lower. The pinch point between the top-cycle refrigerant saturation temperature and the steam in the steam generator may be between any two values ​​described herein.

[0310] In some embodiments, the system may comprise a condenser and pressurized hot water. The pinch point between the top-cycle refrigerant temperature in the condenser and the pressurized hot water may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, 10°C, 15°C, or 20°C or higher. The pinch point between the top-cycle refrigerant temperature in the condenser and the pressurized hot water may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, 10°C, 15°C, or 20°C or lower. The pinch point between the top-cycle refrigerant temperature in the condenser and the pressurized hot water may be between any two values ​​described herein.

[0311] In some embodiments, the system may comprise a top-cycle evaporator and a bottom-cycle condenser. The pinch point between the saturation temperature of the top-cycle evaporator and the saturation temperature of the bottom-cycle condenser may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or higher. The pinch point between the saturation temperature of the top-cycle evaporator and the saturation temperature of the bottom-cycle condenser may be about 0.1°C, 0.2°C, 0.4°C, 0.6°C, 0.8°C, 1°C, 2°C, 4°C, 6°C, 8°C, or 10°C or lower. The pinch point between the saturation temperature of the top-cycle evaporator and the saturation temperature of the bottom-cycle condenser may be between any two values ​​described herein.

[0312] In some embodiments, the system may include an economizer. The superheating temperature in the economizer may be about 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 40°C, or 50°C or higher. The superheating temperature in the economizer may be about 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 40°C, or 50°C or lower. The superheating temperature in the economizer may be between any two values ​​described herein. The flow rate of the economizer may be about 0%, 5%, 10%, 15%, 20%, 25%, 30%, 40%, or 50% or higher of the main refrigerant flow rate. The flow rate of the economizer may be about 0%, 5%, 10%, 15%, 20%, 25%, 30%, 40%, or 50% or lower of the main refrigerant flow rate. The flow rate of the economizer may be between any two values ​​specified herein.

[0313] In some embodiments, the system may include an inlet tube heat exchanger. The effectiveness of the inlet tube heat exchanger may be about 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9, or one or more. The effectiveness of the inlet tube heat exchanger may be between any two values ​​described herein.

[0314] In some embodiments, the system may include a motor coolant. The flow rate of the motor coolant may be about 0%, 1%, 2%, 3%, 4%, 5%, 6%, 8%, 10%, 12%, 15%, or 20% or more of the main refrigerant flow rate. The flow rate of the motor coolant may be about 0%, 1%, 2%, 3%, 4%, 5%, 6%, 8%, 10%, 12%, 15%, or 20% or less of the main refrigerant flow rate. The flow rate of the motor coolant may be between any two values ​​described herein.

[0315] In some embodiments, as shown in Operation Example 10, the system may require less power consumption to produce a predetermined amount of steam compared to an electric boiler. Frozen

[0316] In one embodiment, the present disclosure provides a system for generating steam. This system may comprise a heat pump system (e.g., one or more heat pump cycles) and a refrigeration system. In some embodiments, the refrigeration system may comprise one or more heat exchangers, one or more compressors, one or more expansion valves, and one or more other components. In some embodiments, the refrigeration system may be thermally connected to a transfer fluid pump cycle (e.g., a heat transfer fluid cycle). In some embodiments, the refrigeration system may be directly connected to the heat pump system. In some embodiments, the refrigeration system may be configured to be directly connected to the condenser of the refrigeration unit (e.g., the evaporator of the heat pump system). In some embodiments, the refrigeration system may be configured to be separated from the heat pump system. In some embodiments, the refrigeration system may be configured to be thermally connected to the heat pump system via a separated condenser. In some embodiments, the separated condenser circulates a working fluid between the refrigeration system and the heat pump system. In some embodiments, the refrigeration system may be configured to supply additional heat to the heat pump system. In some embodiments, the heat pump system may be configured to supply additional cooling to the refrigeration system. In some embodiments, the refrigeration system may be configured to supply heat to the heat pump system when the refrigeration load is low and / or close to zero. When the refrigeration load is zero, the heat pump system may be configured to use heat from ambient air or other heat sources. In some embodiments, the heat pump system may be configured to supply cooling to the refrigeration system when the load on the heat pump system is low and / or close to zero. When the load on the heat pump system is zero, the refrigeration system may be configured to cool the refrigeration system using an air-cooled condenser, a condenser water loop, and / or other cooling sources. In some embodiments, the refrigeration system may be configured to be thermally connected to a first heat pump cycle. In some embodiments, the refrigeration system may be configured to be thermally connected to a second heat pump cycle.In some embodiments, the refrigeration system may be configured to be thermally connected to one or more heat pump systems within the system.

[0317] In some embodiments, the refrigeration cycle is coupled to the bottom cycle and / or top cycle of the system. In some embodiments, the refrigeration cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the refrigeration cycle are in parallel with one or more heat exchangers of the top cycle. In some embodiments, the refrigeration cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the refrigeration cycle are in parallel with one or more heat exchangers of the bottom cycle. In some embodiments, the refrigeration cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the refrigeration cycle are in parallel with one or more heat exchangers of the heat transfer fluid cycle. Alternatively, or in addition, the refrigeration cycle may be coupled to the system of the Disclosure such that the refrigeration cycle is in series with one or more heat exchangers of the top cycle. In some embodiments, the refrigeration cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the refrigeration cycle are in series with one or more heat exchangers of the bottom cycle. In some embodiments, the refrigeration cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the refrigeration cycle are in series with one or more heat exchangers of the heat transfer fluid cycle. In some embodiments, the refrigeration cycle may be directly coupled to the cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle). Alternatively, as shown in the non-limiting examples in Figures 22 and 24-26, the refrigeration cycle may be coupled to the cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle) by additional fluid loops (e.g., intermediate loop, glycol loop, oil loop, etc.).

[0318] In some embodiments, the system may include a controller. The controller may be configured to control one or more operations of one or more elements of the system. The controller may be configured to control one or more operations of the refrigeration system and / or at least one operation of the system cycle (e.g., bottom cycle, top cycle, etc.). The controller may control the system to use an air-source heat exchanger as a heat source for generating steam and / or hot water. The air-source heat exchanger may be used as a heat source when the refrigeration system is not operating. The controller may control the system to use the refrigeration system and the air-source heat exchanger as heat sources for generating steam and / or hot water. In some embodiments, the controller may be configured to control the amount of heat generated by the air-source heat exchanger based on the amount of heat generated by the refrigeration system. Alternatively, the controller may be configured to control the system to use only the refrigeration system as a heat source for generating steam and / or hot water. In some embodiments, the controller may be configured to control the system to dissipate heat using a heat exchanger (e.g., an air cooler or a coolant loop). The heat exchanger may dissipate heat when one or more heat sources supply excess heat to the system. In some embodiments, the controller is configured to control the system so as not to generate heat, in which case the heat from the refrigeration system is discharged using a heat exchanger configured to discharge the heat. In some embodiments, the cooling heat is discharged into the ambient air.

[0319] In some embodiments, the amount of steam supplied by the heat pump cycle(s) is insufficient, and the system is configured to be connected to one or more other systems to supply additional steam.

[0320] In some embodiments, the system may comprise a vapor compression system cycle, as shown in the non-limiting examples of Figures 18-19. In some embodiments, the vapor compression system (VCS) cycle may be configured to circulate a working fluid. The vapor compression cycle may comprise one or more heat exchangers, one or more expansion valves, and one or more compressors. In some embodiments, the VCS cycle may be a refrigeration system. In some embodiments, the VCS cycle may be configured to operate independently of the refrigeration system. In some embodiments, the VCS cycle may comprise an air source heat exchanger. In some embodiments, the VCS cycle is coupled to the system of the disclosure such that one or more heat exchangers of the VCS cycle are in parallel with one or more heat exchangers of the top cycle. In some embodiments, the VCS cycle is coupled to the system of the disclosure such that one or more heat exchangers of the VCS cycle are in parallel with one or more heat exchangers of the bottom cycle. In some embodiments, the VCS cycle is coupled to the system of the disclosure such that one or more heat exchangers of the VCS cycle are in parallel with one or more heat exchangers of the heat transfer fluid cycle. Alternatively, or in addition, a VCS cycle may be coupled to the system of the Disclosure such that the VCS cycle is in series with one or more heat exchangers of the top cycle. In some embodiments, a VCS cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the VCS cycle are in series with one or more heat exchangers of the bottom cycle. In some embodiments, a VCS cycle is coupled to the system of the Disclosure such that one or more heat exchangers of the VCS cycle are in series with one or more heat exchangers of the heat transfer fluid cycle. In some embodiments, a VCS cycle may be directly coupled to another cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle). Alternatively, a VCS cycle may be coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle) by an additional fluid loop (e.g., an intermediate loop, a glycol loop, etc.).

[0321] In some embodiments, the VCS cycle is configured to be integrated into the transfer fluid cycle as an add-on loop, as shown in Figure 19.

[0322] In some embodiments, the VCS cycle includes a condenser configured to raise the temperature of the working fluid in the transfer fluid cycle. The VCS cycle may raise the temperature of the working fluid to about 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 25°C, 40°C, 50°C, 60°C, or higher. The temperature rise of the working fluid may be between any two values ​​described herein. In some embodiments, the condenser is located upstream of the cryogenic evaporator in the transfer fluid cycle. This improves the heat pump performance of the system and allows the compressor to operate closer to the design point. In some embodiments, the VCS cycle includes an evaporator configured to lower the temperature of the working fluid in the transfer fluid cycle before it enters the air source heat exchanger of the transfer fluid cycle. The evaporator may lower the temperature of the working fluid to about 5°C, 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, or higher. The temperature drop of the working fluid may be between any two values ​​described herein. The evaporator can lower the working fluid temperature below the ambient air temperature. In some embodiments, the evaporator is located downstream of the low-temperature evaporator in the transfer fluid cycle. In some embodiments, the working fluid of the VCS cycle may include a mixture of glycol and water. In some embodiments, the working fluid of the VCS cycle may include water, water vapor, glycol, air, fluorocarbons, hydrofluoroolefins, hydrofluoroethers, hydrocarbons, ammonia (NH3), water (H2O), carbon dioxide (CO2), pentane (C5H 12 ), butane (C4H 10 ), isobutane (HC(CH3)3), propane (C3H8), and propene (C3H6), or combinations thereof may be included. In some embodiments, one or more compressors in the VCS cycle are configured as screw compressors.

[0323] In some embodiments, the refrigeration system may include an ammonia cycle. In some embodiments, the ammonia cycle is configured to be directly coupled to the top cycle. In some embodiments, the ammonia cycle is configured to be coupled to the top cycle via an intermediate fluid loop and / or cycle. In some embodiments, the top cycle includes a steam generator. In some embodiments, the ammonia cycle is configured to supply cooling to the working fluid. In some embodiments, the working fluid includes air, water, brine, and / or other fluids. In some embodiments, the ammonia cycle may include an air-cooled condenser and / or condensate loop, along with a heat exchanger coupled to the top cycle. This allows the refrigeration system to be operated when steam generation is not required by discharging heat from the refrigeration system through the air-cooled condenser and / or condensate loop. Water vapor generation + cooling

[0324] In one embodiment, the present disclosure provides a system for generating and cooling water vapor. In some embodiments, as shown in the non-limiting examples of Figures 20-26, the system is configured to use a coolant (e.g., cooling water and / or cooling brine) as a heat source. The coolant may be cooling water having a temperature in the range of about 0°C to about 15°C. The coolant may be cooling brine having a temperature of about 0°C or lower. By using a coolant as a heat source, the need for a separate system to supply cooling (e.g., cooling to the cooling water or brine) can be eliminated.

[0325] In some embodiments, the system may include a separate powered refrigeration system (e.g., a standard refrigeration system, a direct expansion system, and / or part of a distributed cooling system). The separate powered refrigeration system may be configured to circulate a coolant. The separate powered refrigeration system may be configured to complement the cooling produced by the heat pump system. In some embodiments, the system is configured to use the refrigeration system in combination with one or more other heat sources to generate steam. In some embodiments, one or more other heat sources include an air heat source heat exchanger.

[0326] In some embodiments, a separate powered refrigeration system may comprise a cooling tower and one or more heat exchangers coupled to one or more cycles of the system and one or more heat pump cycles (e.g., a top heat pump cycle, a bottom heat pump cycle, and a heat transfer fluid cycle). The heat exchangers of the separate powered refrigeration system may be condensers.

[0327] In some embodiments, the system may be configured to transfer heat to the working fluid of the heat pump cycle using a coolant from a separate powered refrigeration system. The coolant may be condensed water. In some embodiments, the coolant is hotter than ambient temperature. In some embodiments, the coolant temperature is about 10°C, 15°C, 20°C, 25°C, 30°C, 35°C, 40°C, 45°C, 50°C, 55°C, or 60°C or higher. The coolant temperature may be between any two values ​​described herein. The use of warmer condensed water may lead to improved heat pump performance. This may eliminate the need for a cooling towner and reduce the power consumption associated with driving the cooling towner fan.

[0328] In some embodiments, the system is configured to operate the heat pump system and the refrigeration system separately. In some embodiments, the heat pump system includes both a hydrothermal recovery heat exchanger and an air heat exchanger. The hydrothermal recovery heat exchanger may be a condenser-type hydrothermal recovery heat exchanger. In some embodiments, the refrigeration system may include a cooling tower and / or an air-cooled heat exchanger. Intermediate loop

[0329] In some embodiments, the refrigeration system is configured to be connected to the heat pump system by an intermediate loop, as shown in the non-limiting examples of Figures 22 and 24-25. The intermediate loop may include a cooling tower and / or an air-cooled heat exchanger, as shown in Figure 25. In some embodiments, the refrigeration system may be coupled to the intermediate loop by a heat exchanger (e.g., a condenser). The intermediate loop may be coupled to the system cycle (e.g., bottom cycle, top cycle, heat transfer fluid cycle, etc.) by a heat exchanger (e.g., an evaporator).

[0330] In some embodiments, the evaporator and the air source heat exchanger are configured to be at different temperatures and / or pressures. The temperature of the evaporator may be approximately -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or higher. The temperature of the evaporator may be between any two values ​​listed herein. The temperature of the air source heat exchanger may be approximately -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, or 50°C or higher. The temperature of the air source heat exchanger may be between any two values ​​listed herein. The temperature difference between the evaporator and the air source heat exchanger may be approximately 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or higher. The temperature difference between the evaporator and the air source heat exchanger may be between any two values ​​listed herein. In some embodiments, the system further includes a back pressure regulator. In some embodiments, two or more evaporators are configured to be located in separate compressor stages (i.e., hotter fluids are used in higher compressor stages).

[0331] In some embodiments, the system comprises a heat pump system and a refrigeration system as described herein. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system separately. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system in conjunction. In some embodiments, the system is configured to allow independent control of the operation of the heat pump system and the refrigeration system. Direct integration

[0332] In some embodiments, the refrigeration system is directly connected to the heat pump system. In some embodiments, the heat pump system is configured as the condenser of the refrigeration system. In some embodiments, the heat generated by the condenser is used as the heat source for the bottom cycle, as shown in the non-limiting example of Figure 23, and / or as the heat source for the top cycle of the heat pump system, as shown in the non-limiting example of Figure 26. This system configuration, in which the refrigeration system is directly integrated with the heat pump system, may be more efficient than using an intermediate water / cooling tower loop. In some embodiments, the heat pump system includes both a condensate heat recovery heat exchanger and an air source heat exchanger. In some embodiments, the refrigeration system may include a cooling tower and / or an air-cooled heat exchanger.

[0333] In some embodiments, the condenser-hydrothermal recovery heat exchanger and the air-source heat exchanger are configured as evaporators. In some embodiments, the evaporators and the air-source heat exchangers are configured to be at different temperatures and / or pressures. The temperature of the evaporator may be approximately -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or higher. The temperature of the evaporator may be between any two values ​​described herein. The temperature of the air-source heat exchanger may be approximately -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, or 50°C or higher. The temperature of the air-source heat exchanger may be between any two values ​​described herein. The temperature difference between the evaporator and the air source heat exchanger may be approximately 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or higher. The temperature difference between the evaporator and the air source heat exchanger may be between any two values ​​described herein. In some embodiments, the system further includes a pack pressure regulator. In some embodiments, two or more evaporators are configured to be located in separate compressor stages (i.e., higher temperature fluids may be used in higher compressor stages).

[0334] In some embodiments, the system comprises a heat pump system and a refrigeration system as described herein. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system separately. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system in conjunction. In some embodiments, the system is configured to allow the operation of the heat pump system to be controlled independently of the operation of the refrigeration system. Compressor coolant heat

[0335] In some embodiments, the system comprises a heat pump system and a refrigeration system. The heat pump system may comprise one or more cycles (e.g., a top cycle, a bottom cycle, a heat transfer fluid cycle, etc.). One or more cycles and / or the refrigeration system may comprise a coolant loop configured to circulate a coolant (e.g., a coolant), as shown in the non-limiting example of Figure 24. The coolant may include oil. In some embodiments, the refrigeration system and / or one or more cycles may comprise one or more compressors. In some embodiments, at least one of the one or more compressors of the refrigeration system may be configured to receive the coolant. The coolant may be delivered by the coolant loop. One or more compressors of the Disclosure may receive the coolant. One or more compressors may transfer heat from another fluid (e.g., a working fluid) to the coolant and / or transfer heat from another fluid (e.g., a working fluid) to the coolant. In some embodiments, one of the one or more compressors described herein may increase the pressure of the fluid (e.g., a working fluid) passing through the compressor. The compressor may increase the fluid pressure to at least 1 kPa, 5 kPa, 10 kPa, 15 kPa, 20 kPa, 30 kPa, 50 kPa, 75 kPa, 100 kPa, 150 kPa, 200 kPa, 300 kPa, 400 kPa, 500 kPa, 700 kPa, 1000 kPa, 1500 kPa, 2000 kPa, 2500 kPa, 3000 kPa, 3500 kPa, or more. The increase in fluid pressure may be between any two values ​​described herein. In some embodiments, the compressor of the refrigeration system may supply heat to the heat pump system. The compressor may be configured to transfer heat directly from the refrigeration system to the heat pump system. The compressor may transfer heat from the refrigeration system to the heat pump system via an intermediate loop. In some embodiments, one or more compressors of the refrigeration system may be configured to transfer heat to the fluid of the heat pump system while cooling the coolant of the refrigeration system.

[0336] In some embodiments, the heat pump system comprises both a condenser hydrothermal recovery heat exchanger and an air source heat exchanger. In some embodiments, the condenser hydrothermal recovery heat exchanger and the air source heat exchanger are coupled in parallel. Alternatively, or in addition, the condenser hydrothermal recovery heat exchanger and the air source heat exchanger are coupled in series. The condenser hydrothermal recovery heat exchanger and the air source heat exchanger may be configured as an evaporator. In some embodiments, the evaporator and the air source heat exchanger are configured to be at different temperatures and / or pressures. The temperature of the evaporator may be about -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or higher. The temperature of the evaporator may be between any two values ​​described herein. The temperature of the air source heat exchanger may be about -30°C, -20°C, -10°C, 0°C, 10°C, 20°C, 30°C, 40°C, or 50°C or higher. The temperature of the air source heat exchanger may be between any two values ​​specified herein. The temperature difference between the evaporator and the air source heat exchanger may be about 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, or 90°C or more. The temperature difference between the evaporator and the air source heat exchanger may be between any two values ​​specified herein. In some embodiments, the system further includes a pack pressure regulator. In some embodiments, the hydrothermal recovery heat exchanger and the air source heat exchanger may be located in separate compressor stages (i.e., hotter fluids may be used in higher compressor stages).

[0337] In some embodiments, the system comprises a heat pump system and a refrigeration system as described herein. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system separately (for example, via one or more controllers). In some embodiments, the system is configured to operate the heat pump system and the refrigeration system in conjunction. In some embodiments, the system is configured to allow independent control of the operation of the heat pump system and the refrigeration system. Top Cycle

[0338] In some embodiments, the refrigeration cycle is configured to be thermally connected to the top cycle of the heat pump system. In some embodiments, the system is configured to supply heat from the refrigeration system directly to the heat pump system, as shown in the non-limiting example of Figure 26. In some embodiments, the system is configured to supply heat from the refrigeration system to the heat pump system via an intermediate loop, as shown in the non-limiting example of Figure 25.

[0339] In some embodiments, the top cycle comprises a two-phase heat exchanger configured to be coupled to the bottom cycle and a condensate heat recovery heat exchanger configured to be coupled to the refrigeration system. In some embodiments, the condensate heat recovery heat exchanger and the two-phase heat exchanger are configured to be at different temperatures and / or pressures. In some embodiments, the system further comprises a pack pressure regulator. In some embodiments, the condensate heat recovery heat exchanger and the two-phase heat exchanger are configured to be located in separate compressor stages (i.e., the hotter fluid may be used in a higher compressor stage).

[0340] In some embodiments, the refrigeration system and / or intermediate loop may include an air-cooled condenser and / or a condenser water loop.

[0341] In some embodiments, the system comprises a heat pump system and a refrigeration system as described herein. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system separately. In some embodiments, the system is configured to operate the heat pump system and the refrigeration system in conjunction. In some embodiments, the system is configured to allow independent control of the operation of the heat pump system and the refrigeration system.

[0342] In some embodiments, the system may include a controller. In some embodiments, the controller may be configured to control the operation of one or more cycles and / or loops of the system and / or one or more components (e.g., a compressor, expansion valve, heat exchanger, fluid flow, etc.). In a non-limiting example, one or more controllers may control the operation of the refrigeration cycle by controlling the working fluid of the refrigeration cycle (e.g., heat transfer fluid). One of the one or more controllers may control the operation of one or more components of the refrigeration cycle (e.g., a heat exchanger, a cryogenic evaporator). In some embodiments, the controller of the refrigeration system may allow the system to be coupled to and / or disconnected from one or more cycles, fluid flows, or components of the system. In a non-limiting example, the controller may control the fluid flow of the refrigeration system to shut off an air heat exchanger and / or turn on a secondary heat source (e.g., a waste heat flow, a geothermal source, or a refrigeration subunit).

[0343] An advantage of the controlled system described herein is that it can receive heat from various heat sources while shutting off unused components or systems to increase system efficiency. Another advantage of the controlled system described herein is that it can ensure sufficient cooling and / or sufficient water vapor generation for a measured or input threshold.

[0344] The controller may control the system to use air as a heat source to produce steam and / or hot water when other heat sources (e.g., waste heat flow, geothermal heat source, electric heater, and / or refrigeration system) are not operating. The controller may control the system to use the refrigeration system and air heat exchanger as heat sources. The controller may control the heat produced by the air heat exchanger based on the amount of heat produced by other heat sources (e.g., waste heat flow, geothermal heat source, electric heater, and / or refrigeration system). The controller may control the system to use only the refrigeration system as a heat source for producing steam and / or hot water. In some embodiments, the controller may control the heat exchanger to discharge heat. The heat exchanger may discharge heat when the heat source is generating excess heat (e.g., an amount of heat exceeding a predetermined threshold). The heat exchanger may be an air cooler and / or coolant loop. The controller may control the system to prevent heat generation. The controller may control the refrigeration system to discharge heat. In some embodiments, the refrigeration system is configured to dissipate heat into the ambient air. hydrothermal production

[0345] In one embodiment, the present disclosure provides a system for generating steam and / or hot water. In some embodiments, the system includes a heat pump system. In some embodiments, the system is configured as a cascade steam heat pump system. The heat pump system may include one or more heat pump cycles (e.g., a first heat pump cycle and a second heat pump cycle). In some embodiments, the one or more heat pump cycles include at least one bottom cycle and at least one top cycle.

[0346] In some embodiments, the bottom cycle may be configured to circulate the working fluid. The bottom cycle may include one or more heat exchangers, one or more expansion valves, one or more compressors, and one or more other elements. One or more other elements of the bottom cycle may include at least one economizer. The benefits of the economizer include improved efficiency (e.g., by reducing the vapor quality of the refrigerant entering the expansion valve) and / or increased mass flow rate between compressor stages while maintaining volumetric flow rate. Increased mass flow rate may help reduce the required operating speed of the downstream compressor or adjust the thrust balance between two stages of a double-ended centrifugal compressor. Medium temperature hot water generation

[0347] In some embodiments, the top cycle may be configured to circulate a working fluid. In some embodiments, the top cycle comprises one or more heat exchangers, one or more expansion valves, one or more compressors, and one or more other elements. One or more other elements of the top cycle may include at least one economizer. The bottom cycle may comprise a hot water heat exchanger. The hot water heat exchanger may be arranged in parallel with a second heat exchanger of the bottom cycle, as shown in the non-limiting example of Figure 27. The second heat exchanger may connect the top cycle to the bottom heat cycle. The second heat exchanger may be a two-phase heat exchanger. The hot water heat exchanger and the two-phase heat exchanger may be a single three-fluid heat exchanger. In some embodiments, the hot water heat exchanger may transfer heat from the working fluid to the water flow. The hot water heat exchanger may be configured to perform at least partial heat transfer from the working fluid to the water flow. In some embodiments, the hot water heat exchanger produces hot water in the temperature range of about 20°C to about 30°C, 30°C to about 40°C, 40°C to about 50°C, about 50°C to about 60°C, about 60°C to about 70°C, about 70°C to about 80°C, about 80°C to about 90°C, about 90°C to about 100°C, or about 100°C to 110°C. In some embodiments, the hot water heat exchanger produces hot water at temperatures of about 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, 100°C, or 110°C or higher. The hot water heat exchanger may produce hot water at temperatures between any two of the values ​​described herein. In some embodiments, the system further comprises at least one of a refrigeration system, a waste heat system, a thermal storage system, a backup system, an auxiliary system, and / or a combination thereof. High temperature hydrothermal production

[0348] In some embodiments, the top cycle comprises a hot water heat exchanger. In some embodiments, the hot water heat exchanger is configured in series with a second heat exchanger of the top cycle. The hot water heat exchanger may be located downstream of the low-pressure compressor, as shown in the non-limiting example of Figure 28. The second heat exchanger may connect the top heat cycle to the bottom heat cycle. The second heat exchanger may be a two-phase heat exchanger. In some embodiments, the hot water heat exchanger produces hot water at temperatures of about 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, or 100°C or higher. The hot water heat exchanger may produce hot water at temperatures between any two of the values ​​described herein. In some embodiments, the hot water heat exchanger produces hot water at a saturation point of at least about 104°C. In some embodiments, the system further comprises at least one of a refrigeration system, a waste heat system, a thermal storage system, a backup system, an auxiliary system, and / or a combination thereof.

[0349] In some embodiments, the cycle (e.g., top cycle or bottom cycle) comprises at least one economizer and / or at least one intercooler. In some embodiments, the heat pump system is configured to draw working fluid from the fluid flow of at least one economizer and / or at least one intercooler to produce hot water, as shown in the non-limiting examples of Figures 28-30. The working fluid may be a refrigerant. The cycle may include one or more valves configured to restrict the working fluid to a low pressure (e.g., intermediate pressure or evaporator pressure). The working fluid may be the working fluid for the top cycle and / or bottom cycle. In some embodiments, the system may combine the restricted fluid vapor with the main fluid flow between the compressor stages. The main fluid flow may include the working fluid for the top cycle and / or bottom cycle. The restricted fluid may include the working fluid for the top cycle and / or bottom cycle. In some embodiments, the system is configured to prevent liquid and / or two-phase mixtures from flowing into the compressor inlet and damaging the compressor. The restricted fluid may be a refrigerant. The restricted fluid may be a two-phase mixture. The throttling fluid may include a liquid and / or vapor. The main fluid flow may include superheated vapor. In some embodiments, the system is configured to superheat a mixed two-phase mixture and / or superheated vapor.

[0350] In some embodiments, the hot water heat exchanger is configured to inject the fluid directly into the intercooler fluid flow. The fluid may or may not pass through a valve between the hot water heat exchanger and the intercooler. The fluid output from the hot water heat exchanger may be a refrigerant. Condensers connected in series

[0351] In some embodiments, the hot water heat exchanger may be located in series with the steam generator. In a non-limiting example, as shown in Figure 31, the hot water heat exchanger may be located upstream of the steam generator. The hot water heat exchanger may be located between the compressor and the steam generator. The hot water heat exchanger may be located downstream of the compressor. The hot water heat exchanger receives a first working fluid (e.g., steam) discharged from the compressor and produces hot water. The hot water heat exchanger may output a working fluid (e.g., a first working fluid). In some embodiments, the working fluid output from the hot water heat exchanger may include a refrigerant. In some embodiments, the hot water heat exchanger may be a high-temperature hot water heat exchanger. In some embodiments, the working fluid output from the hot water heat exchanger may include a refrigerant that is steam or a partially condensed two-phase fluid. In some embodiments, the hot water heat exchanger may be located downstream of the steam generator. In some embodiments, the refrigerant may flow into the hot water heat exchanger as steam, a partially condensed two-phase fluid, or a liquid. Parallel-connected condensers

[0352] In some embodiments, the hot water heat exchanger may be arranged in parallel with the steam generator. In non-limiting examples, the hot water heat exchanger and steam generator may be arranged downstream of the compressor, as shown in the non-limiting example in Figure 32. The hot water heat exchanger may receive a first working fluid (e.g., hot steam). In some embodiments, the hot water heat exchanger may output a working fluid (e.g., a first working fluid). The working fluid output from the hot water heat exchanger may include a saturated liquid. Alternatively, the hot water heat exchanger may be configured to output a working fluid, and the working fluid output from the hot water heat exchanger may include a supercooled liquid. Three-fluid condenser

[0353] In some embodiments, the top-cycle heat exchanger may be a three-fluid heat exchanger. In some embodiments, the three-fluid heat exchanger may produce steam and / or hot water. In some embodiments, the three-fluid heat exchanger may be a single device, as shown in the non-limiting example in Figure 33. Parallel / Series Water Steam

[0354] In some embodiments, the hot water heat exchanger is coupled to a cycle of the system (e.g., a bottom cycle, a top cycle, etc.). In some embodiments, the hot water heat exchanger is coupled to a cycle of the disclosure, with one or more heat exchangers of the cycle coupled in parallel with the hot water heat exchanger. In some embodiments, the hot water heat exchanger is coupled to a cycle of the disclosure, with one or more heat exchangers of the cycle coupled in series. In some embodiments, the hot water heat exchanger may be directly coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle). Alternatively, the refrigeration cycle may be coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle) by an additional fluid loop (e.g., an intermediate loop, a glycol loop, etc.).

[0355] In some embodiments, as shown in the non-limiting example in Figure 34, the hot water heat exchanger is configured to be located downstream of the steam generator. The hot water heat exchanger may receive steam from the steam generator to produce hot water. The hot water heat exchanger may be located in parallel with the steam flow supplied to the facility. The hot water heat exchanger may be located in series with the steam flow supplied to the facility. In some embodiments, as shown in the non-limiting example in Figure 35, a compressor (e.g., a steam compressor) may be located between the steam generator and the hot water heat exchanger. The steam generator may output superheated steam from the heat pump cycle. In some embodiments, the hot water heat exchanger may superheat and remove the steam output by the heat pump cycle. In even more embodiments, the steam flow supplied to the facility is configured to receive the steam superheated and removed by the hot water heat exchanger. The superheated and removed steam may include saturated steam.

[0356] In some embodiments, the steam generation system described herein may include a steam generator. The steam generator may be configured to produce a pressurized hot water flow. The pressurized hot water flow is sent to a flash tank, which uses the pressurized hot water flow to generate steam. supercooling

[0357] In some embodiments, the working fluid may be supercooled. Supercooling can improve the control of the expansion valve and potentially increase the efficiency of the cycle. For example, supercooling the fluid flow before it enters the expansion valve may improve the control of the expansion valve's operation at lower material temperatures (e.g., preventing the fluid flow from becoming a two-phase mixture). Alternatively, or in addition, supercooling the fluid flow before it enters the expansion valve may improve the efficiency of the cycle including the expansion valve by allowing more energy to be transferred from the condenser side and / or by reducing the inlet vapor quality to the evaporator, thereby enabling greater heat transfer at a given flow rate. Furthermore, the motor coolant may require a supercooled liquid. In some embodiments, the working fluid of the lower cycle is supercooled by a supercooler. In some embodiments, the working fluid of the upper cycle is supercooled by a supercooler. In some embodiments, the supercooler is a thermosiphon. In some embodiments, the supercooler is positioned at the same height as or lower than the two-phase heat exchanger. In some embodiments, the supercooler is used in parallel with the evaporator. When a supercooler is used in parallel with an evaporator, it may be important to control the flow rate to the supercooler. The flow rate may be controlled by a thermosiphon system, control valves, and / or by adding flow limiting devices. Hydrothermal water generation control

[0358] In some embodiments, the system includes a controller. The controller may be configured to control the operation of one or more elements of the system. The controller may be configured to control the operation of a refrigeration system and / or at least one operation of the system, such as a bottom cycle or a top cycle. The controller may control the operation of the system to produce hot water and / or steam. In some embodiments, the controller controls the system to produce only hot water or only steam. In some embodiments, the controller is configured to control the system to produce both hot water and steam simultaneously. In some embodiments, the hot water produced is low-temperature hot water. In some embodiments, the hot water produced is high-temperature hot water. In some embodiments, the controller is configured to shut off and / or turn on any element and / or operation of the system. The controller may determine, based on an input, whether to shut off and / or turn on any part of the system. The input may include at least one of user inputs, data from the system, data from an external source, or any combination thereof. The data may include at least one of pressure data, electrical data, temperature data, operation data, safety data, output data, system data, environmental data, or other data. User input may include one or more of the following: operation instructions, output allocation amounts, priority, emergency stop, or other user inputs.

[0359] In a non-limiting example, the controller may control the system to produce only hot water. The controller may control the system to stop steam generation if the water produced is high-temperature hot water. The controller may control the system to produce both hot water and steam. The hot water produced may be high-temperature hot water.

[0360] In non-limiting examples, the controller may control the system to produce only high-temperature hot water. High-temperature hot water may be produced in the top cycle. In some embodiments, the controller may control the system to produce both steam and low-temperature hot water. Low-temperature hot water may be produced in the bottom cycle, while steam may be produced in the top cycle.

[0361] In a non-limiting example, the controller may be configured to control the system to produce only cold hot water. The controller may also stop the top cycle if only cold hot water is needed.

[0362] In some embodiments, the controller is configured to control the system to produce steam, hot water, and / or cold water. The controller may control the system to produce any combination of steam and / or hot water. The controller may control the system to produce one or more hot water flows. In some embodiments, at least one of the one or more hot water flows produced may have different temperatures. In some embodiments, the one or more hot water flows produced may have the same temperature. The one or more hot water flows produced may have any combination of different temperatures and / or the same temperature. Cold weather operation Heating of cold air

[0363] In some embodiments, the systems described herein are configured for cold climate operation. In some embodiments, the system is configured to collect waste heat. In some embodiments, the system is configured to use waste heat to heat a fluid (e.g., working fluid, water, air, etc.), as shown in the non-limiting examples of Figures 36 and 57-67. The system may use the collected waste heat to maintain a high refrigerant saturation temperature in the heat exchanger. The heat exchanger may include an evaporator. The heat exchanger may be an air-source heat exchanger.

[0364] In some embodiments, the system may use a heater to heat a fluid. The fluid may be air. The heater may be an electric resistance heater, as shown in the non-limiting example in Figure 37. The heater may be used to maintain a high refrigerant saturation temperature in the heat exchanger. The heat exchanger may include an evaporator. The heat exchanger may be an air-source heat exchanger.

[0365] In some embodiments, the system comprises a main heat pump system (e.g., the heat pump system described herein) and a separate air source heat pump system, as shown in the non-limiting example of Figure 38. The separate air source heat pump system may comprise at least one heat exchanger, at least one compressor, and at least one expansion valve. At least one heat exchanger may comprise at least one air source heat exchanger. In some embodiments, the system is configured to use the separate air source heat pump system in extremely cold conditions. The separate air source heat pump system may be configured to supply working fluid to the bottom cycle of the main heat pump system. The working fluid supplied by the separate air source heat pump system may be a coolant. In some embodiments, the temperature of the coolant is about -10°C, -5°C, 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, or 30°C or less. The temperature of the coolant may be between any two values ​​described herein.

[0366] In some embodiments, as shown in the non-limiting example of Figure 39, the isolated air source heat pump system is coupled to the system's heat pump cycle (e.g., bottom cycle, top cycle, etc.). In some embodiments, the isolated air source heat pump system is coupled to the system of the present disclosure, and one or more heat exchangers of the isolated air source heat pump system are coupled in parallel to one or more heat exchangers of the top cycle. In some embodiments, the isolated air source heat pump system is coupled to the system of the present disclosure, and one or more heat exchangers of the isolated air source heat pump system are coupled in parallel to one or more heat exchangers of the bottom cycle. In some embodiments, the isolated air source heat pump system is coupled to the system of the present disclosure, and one or more heat exchangers of the isolated air source heat pump system are coupled in parallel to one or more heat exchangers of the heat transfer fluid cycle. Alternatively, or in addition, the isolated air source heat pump system is coupled to the system of the present disclosure, and the isolated air source heat pump system is coupled in series to one or more heat exchangers of the top cycle. In some embodiments, a separate air source heat pump system is coupled to the system of the Disclosure, with one or more heat exchangers of the separate air source heat pump system coupled in series with one or more heat exchangers of the bottom cycle. In some embodiments, a separate air source heat pump system is coupled to the system of the Disclosure, with one or more heat exchangers of the separate air source heat pump system coupled in series with one or more heat exchangers of the heat transfer fluid cycle. In some embodiments, the separate air source heat pump system may be directly coupled to the cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle). Alternatively, the separate air heat source heat pump system may be coupled to the system cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle) by an additional fluid loop (e.g., intermediate loop, glycol loop, etc.).

[0367] In some embodiments, the heat pump system comprises at least one compressor. In some embodiments, the bottom cycle comprises at least one compressor. In some embodiments, the at least one compressor comprises at least one main compressor and / or at least one additional compressor, as shown in the non-limiting example of Figure 40A. The additional compressor may be configured to maintain the intake temperature of the main compressor. The compressor may be configured to maintain the intake temperature during cold climate operation. The intake temperature may be about 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, or 30°C or higher. The intake temperature may be about 7°C. The intake temperature may be between any two values ​​described herein. The heat pump system may further comprise at least one valve. The heat pump system may further comprise at least one bypass line. In some embodiments, one or more of the at least one valve may be configured to control the bypass line. The valve and bypass line may be configured to isolate one or more of the one or more compressors. An advantage of separating the compressor is that the separated compressor can be shut down (for example, when the ambient temperature exceeds a certain temperature). The compressor may be configured to maintain the suction temperature of the centrifugal compressor. The suction temperature may be approximately 0°C, 5°C, 10°C, 15°C, 20°C, 25°C, or 30°C or higher. The suction temperature may be between any two values ​​described herein. The centrifugal compressor may be connected to the bottom cycle. Alternatively, the compressor may be connected to the top cycle.

[0368] In some embodiments, the top cycle is configured to circulate a working fluid. In some embodiments, the working fluid of the top cycle includes hydrocarbons, natural fluids, special fluids, supercritical fluids, and / or combinations thereof. The top cycle may include at least one compressor. The compressor may be operated during cold operation. The compressor may overcome the heat loss of the bottom cycle. In some embodiments, the top cycle may include at least one bypass line, as shown in the non-limiting example of Figure 41. In some embodiments, the system further includes one or more valves. The valves may be configured to control the bypass line and shut off one or more compressors. The valves and / or the bypass line may be configured to shut off one or more compressors. One or more compressors may be shut off to maintain the efficiency of one or more operating compressors. supercritical

[0369] In some embodiments, the heat pump system is configured to produce steam at a temperature higher than the critical temperature. In some embodiments, the heat pump system may comprise one or more cycles (e.g., a top cycle and a bottom cycle). The bottom cycle may circulate a first working fluid. The top cycle may circulate a second working fluid. The first working fluid may be a subcritical fluid in at least part of the bottom cycle. The second working fluid may be a supercritical fluid in at least part of the top cycle. The top cycle may comprise a steam generator. The steam generator may be located downstream of the compressor. The compressor may receive a working fluid and output a supercritical fluid. The steam generator may receive a supercritical fluid from the compressor. The steam generator may receive a feed fluid. In some embodiments, the steam generator produces steam by transferring heat from the first supercritical fluid to the feed fluid. The feed fluid may contain water. The produced steam may contain steam at a temperature higher than the critical temperature of the second working fluid.

[0370] In some embodiments, the cycle comprises one or more compressors (e.g., a first compressor, a second compressor, and a third compressor), as shown in the non-limiting example in Figure 42. The first compressor may receive a subcritical fluid. The first compressor may output a first supercritical fluid. A first steam generator may receive the first supercritical fluid from the first compressor to produce steam. The first steam generator may output a second supercritical fluid. A second compressor may receive a second supercritical fluid from the first steam generator. The second compressor may output a third supercritical fluid. The first steam generator may receive a third supercritical fluid from the second compressor to produce steam. In some embodiments, the cycle and / or system may comprise one or more (e.g., three, four, etc.) steam generators and / or one or more (e.g., three, four, etc.) compressors configured as described above. In some embodiments, the cycle comprises one or more compressors. In some embodiments, at least one of the one or more compressors may output supercritical fluid to the steam generator. In some embodiments, at least one of the one or more compressors may output non-supercritical fluid. The non-supercritical fluid may be output upstream of at least one compressor that outputs supercritical fluid to the steam generator. The compressor may comprise one or more compressor stages. The compressor stages may comprise a first compressor stage and a second compressor stage. The first compressor stage may receive and / or output non-supercritical fluid. The second compressor stage may receive the non-supercritical fluid output from the first stage. The second compressor stage may output supercritical fluid.

[0371] In some embodiments, the cycle includes one or more compressors, a first steam generator, and a second steam generator. The compressor may include one or more compressor stages. The compressor stages may include first and second compressor stages. At least one of the compressor stages may output a supercritical fluid to the steam generator. At least one of the compressor stages may output a non-supercritical fluid.

[0372] In some embodiments, the cycle includes one or more compressors. The compressors may include one or more compressor stages. A first compressor stage may receive a subcritical fluid. The first compressor stage may output a first supercritical fluid flow. A first steam generator may transfer heat from a first portion of the first supercritical fluid flow to a feed fluid to produce steam and / or hot water. The first feed fluid may contain water. A second steam generator may transfer heat from a second portion of the first supercritical fluid flow to a feed fluid to produce steam and / or hot water. In some embodiments, the cycle may include at least one economizer and / or at least one intercooler. The economizer and / or intercooler may receive a non-supercritical fluid. The non-supercritical fluid may be a working fluid from the cycle. Alternatively, the non-supercritical fluid may be a working fluid from a different cycle and / or loop.

[0373] In some embodiments, the steam generator is coupled to a cycle of the system (e.g., a bottom cycle, a top cycle, etc.). In some embodiments, the steam generator is coupled to a cycle of the disclosure, and one or more heat exchangers of the cycle are coupled in parallel with the steam generator. In some embodiments, the steam generator is coupled to a cycle of the disclosure, and the steam generator is coupled in series with one or more heat exchangers of the cycle. In some embodiments, the steam generator may be directly coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle). Alternatively, the steam generator may be coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle) via an additional fluid loop (e.g., an intermediate loop, a glycol loop, etc.). The heat exchangers of the cycle may be steam generators. Water vapor compressor

[0374] In some embodiments, the steam generation system described herein comprises one or more steam compressors and one or more heat pump cycles (e.g., a first heat pump cycle and a second heat pump cycle). One or more heat pump cycles may include steam generators. Steam generators may output steam from the heat pump cycles. As shown in the non-limiting example in Figure 43, steam compressors may be located downstream of the steam generators in the cycles. Compressors may increase the temperature of the steam generated by the heat pump cycles. The use of steam compressors(s) allows the steam generation system to compensate for the heat and pressure losses of the steam supplied by the heat pump system as a result of cold climates. This provides the system with the advantage of being able to maintain a constant pressure and temperature of the steam output by the system during periods of increased heat loss. In some embodiments, one or more steam compressors may be configured to raise the saturation temperature of the steam produced by the heat pump system to a maximum of approximately 5°C, 10°C, 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, 100°C, or higher. One or more steam compressors may be configured to raise the saturation temperature of the steam produced by the heat pump system to a temperature between any two values ​​described herein. In some embodiments, one or more steam compressors may be configured to raise the saturation temperature of the steam produced by the heat pump system to approximately 90°C, 100°C, 110°C, 120°C, 130°C, 140°C, 150°C, 175°C, 200°C, 225°C, or higher. One or more steam compressors may be configured to raise the saturation temperature of the steam produced by the heat pump system to a temperature between any two values ​​described herein. In some embodiments, one or more steam compressors may be configured to increase the pressure of the steam produced by the heat pump system from about 30 kPa to about 2500 kPa.In some embodiments, one or more steam compressors may be configured to increase the pressure of the steam generated by the heat pump system to a maximum of approximately 30 kPa, 50 kPa, 100 kPa, 200 kPa, 500 kPa, 1000 kPa, 1500 kPa, 2000 kPa, 2500 kPa, or higher. One or more steam compressors may be configured to increase the pressure of the steam generated by the heat pump system to a pressure between any two values ​​described herein. In some embodiments, one or more steam compressors may be configured to increase the pressure of the steam generated by the heat pump system to approximately 50 kPa, 100 kPa, 200 kPa, 500 kPa, 1000 kPa, 1500 kPa, 2000 kPa, 2500 kPa, or higher. One or more steam compressors may be configured to increase the pressure of the steam generated by the heat pump system to a pressure between any two values ​​described herein. In some embodiments, one or more steam compressors may be configured to raise the temperature of the steam produced by the heat pump system to a minimum temperature requirement (e.g., 120°C). In some embodiments, one or more steam compressors may be configured to raise the temperature of the steam produced by the heat pump system to more than 30°C.

[0375] In some cases, high-pressure saturated steam at a lower temperature than the steam discharged from the steam compressor may be desired (for example, if the steam at the outlet of the steam compressor is superheated). In some embodiments, water injection is used to lower the temperature of the output steam. Water injection may lower the temperature of the output steam by approximately 10°C, 12°C, 15°C, 20°C, 25°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 100°C, 125°C, 150°C, or more. The temperature reduction of the output steam may be between any two values ​​described herein. In some embodiments, water is injected upstream of the steam compressor. In some embodiments, water is injected into the steam compressor. In some embodiments, water is injected downstream of the steam compressor. In some embodiments, a heat exchanger is located downstream of the steam compressor. In some embodiments, water injection can allow the steam compressor to operate at a lower temperature (for example, by injecting water upstream of or into the compressor). The ideal injection location depends on the type of compressor used. For example, in screw or piston compressors, the ideal injection location can be anywhere, while in centrifugal steam compressors, the ideal injection location may be downstream of the compressor. Lowering the operating temperature can improve the durability of the steam compressor and / or allow for the incorporation of additional commercially available equipment (e.g., seals). In some embodiments, the heat exchanger cools the steam using a refrigerant from another location in the heat pump cycle. Alternatively, or in addition, an advantage of water injection is the increased steam flow output of the overall heat pump system. Topping cycle

[0376] In some embodiments, the systems described herein may comprise a bottom heat pump cycle, a top heat pump cycle, and a topping cycle, as shown in the non-limiting examples of Figures 44-45. The topping cycle may comprise a steam generator, valves, a compressor, a heat exchanger, and / or a steam generator. The topping cycle may circulate a working fluid. The working fluid of the topping cycle may be a hydrocarbon, a natural fluid, a special fluid, or a supercritical fluid. The topping cycle may produce steam at a higher temperature than the steam produced using only the top heat pump cycle and the bottom heat pump cycle.

[0377] The topping cycle may be turned on in response to cold weather and / or an increase in the demand for steam pressure. In some embodiments, the heat pump system may comprise one or more topping cycles. One or more topping cycles may supply steam and / or hot water. One or more topping cycles may supply steam and / or hot water at one or more different pressures. One or more topping cycles may supply steam and / or hot water at pressures of about 50 kPa, 100 kPa, 200 kPa, 500 kPa, 1000 kPa, 1500 kPa, 2000 kPa, 2500 kPa or higher. One or more topping cycles may supply steam and / or hot water at pressures between any two of the values ​​described herein. One or more topping cycles may supply steam and / or hot water simultaneously at different pressures. One or more topping cycles may supply steam and hot water simultaneously.

[0378] In some embodiments, the topping cycle is coupled to a cycle of the system (e.g., a bottom cycle, a top cycle, etc.). In some embodiments, the topping cycle is coupled to a cycle of the disclosure, with one or more heat exchangers of the cycle coupled in parallel with the topping cycle. In some embodiments, the topping cycle is coupled to a cycle of the disclosure, as shown in the non-limiting example of Figure 45, with the topping cycle coupled in series with one or more heat exchangers of the cycle (e.g., a steam generator). In some embodiments, the topping cycle may be directly coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle). Alternatively, the refrigeration cycle may be coupled to a cycle (e.g., a top cycle, a bottom cycle, and / or a heat transfer fluid cycle) via an additional fluid loop (e.g., an intermediate loop, a glycol loop, etc.). In some embodiments, the topping cycle replaces the steam generator in a top heat pump cycle. defrosting

[0379] In some embodiments, the heat pump system may comprise one or more cycles (e.g., a first heat pump cycle and a second heat pump cycle). One or more cycles may comprise one or more high-temperature gas bypass lines, as shown in the non-limiting examples of Figures 46-47. The high-temperature gas bypass lines may comprise one or more valves. The high-temperature gas bypass lines may deliver high-temperature fluid from a first section of the cycle to a second section of the cycle. The first section may be from a first cycle, and the second section may be a different section from the first cycle. Alternatively, the first section may be from a first cycle, and the second section may be from a second cycle.

[0380] In some embodiments, one or more high-temperature gas bypass lines may be configured to defrost one or more components of the cycle using a high-temperature fluid (e.g., hot water, steam, etc.). The high-temperature fluid may be obtained from the discharge port of a compressor. The high-temperature fluid may be obtained from the high-pressure section of a heat pump system. The high-temperature gas bypass lines may supply the high-temperature fluid upstream of one or more heat exchangers. One or more heat exchangers may include air-source heat exchangers. In some embodiments, one or more high-temperature gas bypass lines may be arranged in parallel. One or more high-temperature gas bypass lines may be coupled to corresponding heat exchangers among one or more heat exchangers, as shown in the non-limiting example in Figure 47. One or more high-temperature gas bypass lines may be controlled to defrost corresponding heat exchangers among one or more heat exchangers independently of each other.

[0381] In some embodiments, the heat pump system may include a cooler / recondenser to facilitate defrosting of system components (e.g., a cryogenic evaporator), as shown in the non-limiting example in Figure 48. During normal operation of the system, a first expansion valve downstream of the economizer may be fully open to minimize pressure changes in the fluid (e.g., the working fluid of the cycle). The cooler / recondenser does not alter the working fluid, and the second expansion valve and heat exchanger (e.g., a cryogenic evaporator) operate normally. If necessary (e.g., during cold operation), the cooler / recondenser may further supercool the working fluid before the second expansion valve. In some embodiments, the first expansion valve partially expands the working fluid to an intermediate pressure between the two-phase heat exchanger and the cryogenic evaporator. The cooler / recondenser may recondense and / or supercool the partially expanded working fluid output by the first expansion valve. In some embodiments, the cooler / recondenser may be a separate unit installed in the cycle and / or loop. In some embodiments, the cooler / recondenser may be an existing cryogenic evaporator configured to change its position in the cycle and / or loop by one or more valves. In some embodiments, the expansion valve may be a separate unit installed in the cycle and / or loop. In some embodiments, the expansion valve may be an existing expansion valve having a position in the cycle and / or loop that is changed by one or more valves. Resistance heater

[0382] In some embodiments, the heat pump system may include one or more resistance heaters, as shown in the non-limiting examples in Figures 49-50. The resistance heaters may be configured to defrost one or more elements of the cycle. One or more elements of the cycle may include a heat exchanger. The heat exchanger may be an air-source heat exchanger. The resistance heaters may heat a fluid (e.g., working fluid, supply fluid, water, air, etc.). The resistance heaters may heat the air entering the air-source heat exchanger. One or more resistance heaters may replace one or more heat bypass lines. Direct spray line

[0383] In some embodiments, the heat pump system may include a defrost spray line and one or more cycles (e.g., a first heat pump cycle and a second heat pump cycle). The defrost spray line may be configured to deliver a hot fluid from a first position in the cycle (e.g., a steam generator in the cycle) to a second position, as shown in the non-limiting examples in Figures 51-52. The first section may be from the first cycle, and the second section may be a different section from the first cycle. Alternatively, the first section may be from the first cycle, and the second section may be from the second cycle.

[0384] In some embodiments, one or more defrost spray lines may be configured to defrost one or more components of the cycle using a high-temperature fluid (e.g., hot water, steam, etc.). The high-temperature fluid may come from the compressor discharge, the high-pressure section of the heat pump system, a heat exchanger, or a combination thereof. The defrost spray lines may supply the high-temperature fluid to defrost one or more heat exchangers. One or more heat exchangers may include air-source heat exchangers. In some embodiments, two of the one or more defrost spray lines may be in parallel. One or more defrost spray lines may be coupled to one or more corresponding heat exchangers. One or more defrost spray lines may be controlled to defrost corresponding heat exchangers among one or more heat exchangers independently of each other. The defrost spray lines may supply the high-temperature fluid directly to multiple evaporator coils of one or more evaporators. The defrost spray lines may supply the high-temperature fluid to one or more air-source heat exchangers. In some embodiments, the heat pump system is a closed system. Heat storage + hot water

[0385] In some embodiments, the heat pump system may include a defrost spray line. In some embodiments, the defrost spray line may be coupled to a thermal storage unit (e.g., a hot water tank). The defrost spray line may be configured to deliver a hot fluid to be stored in the thermal storage unit, as shown in the non-limiting example in Figure 53. The defrost spray line may be configured to deliver at least a portion of the hot fluid flow to defrost a portion of the heat pump system and / or to be stored in the thermal storage unit.

[0386] In some embodiments, the defrost spray line may deliver a first portion of the high-temperature fluid flow directly to a portion of the heat pump system to be defrosted, and / or deliver a second portion of the high-temperature fluid flow to a thermal storage unit. The defrost spray line may draw up at least a portion of the high-temperature fluid generated by one or more heat exchangers by siphon. The proportion of high-temperature fluid drawn up by the defrost spray line may be about 2%, 5%, 10%, or 20% or less. The proportion of high-temperature fluid drawn up by the defrost spray line may be between any two values ​​described herein. One or more heat exchangers may include a hot water generator and / or a steam generator. In some embodiments, at least one of the hot water generator and / or steam generator is directly coupled to the top cycle and / or bottom cycle of the heat pump system. In some embodiments, at least one of the hot water generator and / or steam generator is disconnected from the top cycle and / or bottom cycle of the heat pump system.

[0387] In some embodiments, the thermal storage unit may be configured to collect hot fluid during periods of high system efficiency and / or release hot fluid during periods of low system efficiency. Thus, the system may be configured to generate and store excess hot fluid (e.g., water or steam) during operating periods when little or no hot fluid (e.g., water or steam) is needed to optimize and maintain system operation, such as on warm days, and to utilize the hot water (e.g., water or steam) generated, collected, and stored during the day to optimize and maintain operation during cold weather periods, such as at night. Thus, the system may be configured to generate and store excess hot fluid (e.g., water or steam) during operating periods when little or no hot fluid (e.g., water or steam) is needed, such as on warm days, and to utilize the hot fluid (e.g., water or steam) generated, collected, and stored during the day to help optimize and maintain operation during cold weather periods, such as at night.

[0388] The high-temperature fluid may include hot water and / or steam generated by the system. Depending on one or more factors, such as where the high-temperature fluid is supplied from, the needs of the system, the operation and output of the system, and the desired application of the high-temperature fluid, the high-temperature fluid may be hot water or steam.

[0389] Alternatively, the heat storage unit may comprise a heat storage fluid configured to collect heat from the system at high efficiency and / or release heat to the system at low efficiency. The heat storage fluid may comprise a sensible heat storage material, a latent heat storage material (e.g., a phase change material), a thermochemical heat storage material, or any combination thereof. The phase change material (PCM) may be an organic PCM (e.g., paraffin wax, sugar alcohol, or fatty acid), an inorganic PCM (e.g., a salt, salt hydrate, salt aqueous solution, or metal), or an organic-inorganic eutectic PCM (e.g., a combination of two or more organic and / or inorganic PCMs having a single lowest transition temperature). In some embodiments, the heat exchanger can store and release stored energy using the latent heat of the phase change material. In the case of a phase change material, the heat can be exchanged with a heat source held at a constant temperature. One or more factors not shown herein may be used to determine the type of fluid used and / or stored.

[0390] In some embodiments, the systems described herein may include a thermal storage unit. In some embodiments, the thermal storage unit may store hot fluid from one or more cycles of the system (e.g., a top cycle or a bottom cycle). The thermal storage unit may directly receive a portion of the hot fluid flow from at least one of the one or more cycles. The hot fluid may be fed to the thermal storage unit from one or more heat exchangers. One or more heat exchangers may include a hot water generator and / or a steam generator. In some embodiments, at least one of the hot water generator and / or a steam generator is directly coupled to the top cycle and / or bottom cycle of the heat pump system. In some embodiments, at least one of the hot water generator and / or a steam generator is separated from the top cycle and / or bottom cycle of the heat pump system. In some embodiments, the thermal unit may heat the fluid using one or more heat sources. One or more heat sources may include a heat exchanger and / or a secondary heat source. The secondary heat source may include a waste heat flow, a geothermal heat source, a combined heat and power (CHP) system, a refrigeration subunit, or a combination thereof. In particular, to assist in starting the top cycle, the system may temporarily rely on a secondary heat source.

[0391] In some embodiments, the heat storage unit is used to supply an additional heat source to the cycle (e.g., a top heat pump cycle or a bottom heat pump cycle) to assist in heating the working fluid at the start of system operation, to smooth the system load in the event of a rapid temperature drop and / or an increase in steam demand.

[0392] In some embodiments, the thermal storage unit is coupled to a system cycle (e.g., bottom cycle, top cycle). In some embodiments, the thermal storage unit is coupled to the system of the Disclosure in parallel with one or more heat exchangers (e.g., steam generators) in the top cycle. In the case of a steam generator, excess steam may be generated and energy stored when electricity is inexpensive or renewable energy is more available, and then released to generate steam when electricity is more expensive or renewable energy is unavailable. Alternatively, or in addition, the advantages of thermal storage include improved efficiency at low turndown (e.g., by the heat pump slowly releasing thermal energy). In some embodiments, the thermal storage unit is coupled to the system of the Disclosure in parallel with one or more heat exchangers (e.g., evaporators) in the bottom cycle. In the case of an evaporator, the performance of the heat pump system can be improved by using the thermal storage device when the ambient temperature is low or when defrosting is being performed. Alternatively, or in addition, a thermal storage unit may be used when the utilization of waste heat is intermittent (e.g., when the waste heat source is obtained from a batch process). Alternatively, or in addition, a thermal storage unit may be used to decouple the operation of the first heat pump cycle from the operation of the second heat pump cycle (e.g., when the first and second heat pump cycles are not operating simultaneously). By operating the first and second heat pump cycles at different times, load reduction and load shifting benefits may be obtained. In some embodiments, the thermal storage unit is coupled to the system of the disclosure, and the thermal storage unit is coupled in parallel with one or more heat exchangers of the heat transfer fluid cycle. Alternatively, or in addition, the thermal storage unit is connected to the system of the disclosure, and the thermal storage unit is coupled in series with one or more heat exchangers of the heat transfer fluid cycle (e.g., steam generators). In some embodiments, the thermal storage unit is coupled to the system of the disclosure, and the thermal storage unit is coupled in series with one or more heat exchangers of the bottom cycle (e.g., evaporators).In some embodiments, the thermal storage unit is coupled to the system of the Disclosure, and the thermal storage unit is coupled in series with one or more heat exchangers of the heat transfer fluid cycle. In some embodiments, the thermal storage unit may be directly connected to the cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle). Alternatively, the thermal storage unit may be coupled to the cycle (e.g., top cycle, bottom cycle, and / or heat transfer fluid cycle) via an additional fluid loop (e.g., intermediate loop, glycol loop, etc.).

[0393] In some embodiments, the system may include a controller. The controller may be configured to control the operation of one or more elements of the system. The controller may be configured to control the operation of the thermal storage unit and / or at least one cycle of the system (e.g., bottom cycle, top cycle, etc.).

[0394] In some embodiments, the systems described herein may use one or more thermal or non-thermal methods to defrost one or more components of the cycle. Non-thermal methods may include the use of heat-resistant coatings, chemical de-icing agents (e.g., ice, alcohol, magnesium chlorine, etc.), and / or physical removal (e.g., pressurized air, vibration, blunt force). Other defrosting and heating methods not described herein may also be used.

[0395] In some embodiments, the heat exchanger is configured as a condenser, evaporator, low-temperature evaporator, two-phase heat exchanger, air source heat exchanger, suction tube heat exchanger, and / or a combination thereof. In some embodiments, the system comprises one or more different types of heat exchangers. In some embodiments, the heat exchanger of the system may comprise any combination of one or more different types of heat exchangers.

[0396] In some embodiments, one or more of the compressors are electrically operated. In some embodiments, one or more of the compressors are centrifugal compressors. In some embodiments, one or more of the compressors are screw compressors. In some embodiments, one or more of the compressors are axial compressors. In some embodiments, one or more of the compressors are positive displacement compressors. In some embodiments, one or more of the compressors are double-ended compressors. Double-ended compressors may have high efficiency per stage, low operating speed, and / or low thrust to the bearing system. In some embodiments, the system comprises a multi-level compressor. In some embodiments, a multi-level compressor comprises one or more compressors. In some embodiments, multi-stage compressors are arranged in parallel. In some embodiments, multi-level compressors are arranged in series. In some embodiments, multi-level compressors are arranged in a combination of parallel and series. In some embodiments, one or more compressors further comprise bypass lines configured to bypass one or more levels of the multi-level compressor. In some embodiments, the compressors of the system are any combination of the different types of compressors described herein.

[0397] In some embodiments, the system may comprise one or more working fluids. In some embodiments, one or more cycles of the system may comprise one or more working fluids. In some embodiments, one or more cycles may comprise different working fluids. In some embodiments, one or more cycles may comprise the same working fluid. In some embodiments, the working fluids of the system may be of the same type or of different types. Using different working fluids in cycles allows for the use of working fluids with customized properties that are optimally suited to each individual cycle. Alternatively, using the same working fluid in cycles can reduce the complexity and cost of the system.

[0398] In some embodiments, a portion of the steam generation system described herein may comprise a first heat pump cycle (e.g., a bottom cycle) and a second heat pump cycle (e.g., a top cycle). The first heat pump cycle may be installed outdoors. The first heat pump cycle may use air as a heat source to supply a fluid (e.g., a high-temperature refrigerant or heat transfer fluid) to the second heat pump cycle, as shown in the non-limiting examples in Figures 14-19, and the second heat pump cycle may be installed indoors. The second heat pump cycle may generate steam. Example of operation

[0399] 1. In one example, the first heat pump cycle receives an ambient airflow of 15°C and supplies 65°C of heat to a heat exchanger coupled to the first and second heat pump cycles (e.g., the top cycle). The second heat pump cycle generates 150°C water vapor.

[0400] 2. The bottom cycle evaporator evaporates the refrigerant flow (e.g., refrigerant or refrigerant working fluid) using an ambient airflow of 15°C. The refrigerant enters the evaporator as a two-phase fluid with a vapor quality of approximately 30% and a nominal temperature of 7°C. The evaporator outlet is superheated to a temperature of 12°C (e.g., superheat degree 5°C).

[0401] 3. A condenser connected to the first heat pump cycle (e.g., bottom cycle condenser) receives a fluid superheated to approximately 80°C and condenses it at approximately 65°C. The fluid is discharged from the condenser at approximately 63.5°C. A second condenser connected to the second heat pump cycle (e.g., top cycle condenser, steam generator) receives a fluid at approximately 205°C and condenses it at approximately 155°C. The fluid is discharged at 153°C, slightly supercooled. The supply stream enters the steam generator as a pressurized water stream at 148°C and evaporates at 150°C. The fluid is discharged from the heat exchanger as saturated steam.

[0402] 4. In the economizer coupled to the first heat pump cycle (e.g., bottom cycle), the temperature of the evaporative flow is approximately 30°C, cooling the refrigerant flow from approximately 64°C to approximately 45°C. In the economizer coupled to the second heat pump cycle (e.g., top cycle), the temperature of the evaporative flow is approximately 100°C, cooling the refrigerant flow from approximately 153°C to approximately 147°C.

[0403] 5. The heat pump cycle system has a design point that uses R513a refrigerant gas (an azeotropic mixture of hydrofluorochlorine (HFC) gas and hydrofluoroolefin (HFO) gas) and receives an ambient airflow at a pressure of 394 kPa, a temperature of 11.3°C, and a saturation temperature of 7.2°C. The system discharges fluid water vapor containing water vapor at a pressure of 1983 kPa, a temperature of 81.5°C, and a saturation temperature of 65.4°C. During low-temperature operation, the inlet temperature can drop to an inlet pressure of 110 kPa, a temperature of -22.8°C, and a saturation temperature of -32.8°C. The compressor pressure ratio ranges from approximately 2 to a maximum of 9 at various stages of the heat pump cycle system. The pressure ratio of double-ended compressors can reach a maximum of approximately 6. To achieve a higher pressure ratio (up to approximately 20 or more), multiple compressor units are connected in series.

[0404] 6. During cold climate operation, the compressor may be increased to a pressure of up to 23 times the inlet pressure. For example, the compressor pressure may be increased from 86 kPa to 1962 kPa. In this particular case, the inlet temperature may be increased from -28°C to an outlet temperature of 86°C. Alternatively, the compressor pressure may be increased to 5.6 times the inlet pressure (from 348 kPa to 1962 kPa). In this case, the temperature will rise from 3.9°C to 75°C. Alternatively, the compressor pressure may be increased to 1.2 times the inlet pressure. In this case, the temperature only needs to rise by 6°C. Alternatively, the compressor pressure may be increased to 8.1 times the inlet pressure. For example, the compressor pressure may be increased from 358 kPa to 2912 kPa. In this case, the temperature may rise from 112°C to 196°C.

[0405] 7. The VCS cycle may raise the working fluid temperature from -24°C to -7°C. Alternatively, if the ambient temperature is high, the VCS cycle may have a smaller temperature rise. Alternatively, the VCS cycle may have a larger temperature rise, raising the outlet glycol temperature by, for example, 15°C.

[0406] 8. The evaporator may lower the working fluid temperature from -12°C to -28°C. Alternatively, if the ambient temperature is high, the evaporator may reduce the temperature drop. Alternatively, the glycol inlet temperature may be higher, for example, 9°C.

[0407] 9. In some embodiments, the evaporator and the air source heat exchanger may be configured to have different temperatures and / or pressures. The temperature of the air source heat exchanger may be 7°C. The pressure of the air source heat exchanger may be 414 kPa. The temperature of the evaporator may be 61.7°C. The pressure of the evaporator may be 410 kPa.

[0408] 10. In some embodiments, the system may require less power to produce a given amount of steam compared to an electric boiler. Table 1 shows examples of the power required to produce 1,000 kW of steam for 8,760 hours per year in an electric boiler, a glycol-coupled air-source heat pump, a direct-drive air-source heat pump, and a 60°C waste heat-driven heat pump. Significant cost savings are possible due to the lower power requirements. [Table 1] Example of an embodiment

[0409] Figure 1 shows a heat pump system according to several embodiments described herein. Figure 1 shows an exemplary steam generation system 100 for industrial applications. Figure 1 shows an overview of system 100, which includes a two-stage air-source heat pump including a bottom heat pump cycle 102 (i.e., a first heat pump cycle) and a top heat pump cycle 104 (i.e., a second heat pump cycle) thermally coupled by an intermediate heat exchanger (i.e., a heat exchanger). System 100 also includes a steam compressor 106. The working fluid of the bottom heat pump cycle 102 releases heat to the working fluid of the top heat pump cycle 104. The steam generator releases heat from the working fluid of the top heat pump to a third working fluid 108. The third working fluid 108 absorbs heat from the steam generator and then passes through the steam compressor 106. The third working fluid 108 contains water and may evaporate to become steam 110. The system may be driven by electricity 112.

[0410] Figure 2 is a schematic diagram of a cascade heat pump system according to some embodiments described herein. The steam generation system 200 includes a bottom heat pump cycle 202 (i.e., a first heat pump cycle) and a top heat pump cycle 204 (i.e., a second heat pump cycle) arranged in a thermal cascade configuration. The system also includes a steam compressor 206. Heat transfer 216a involves the bottom heat pump cycle 202 capturing heat from the ambient air by evaporating a working fluid, which may be a refrigerant. Electricity 212a is supplied to the bottom heat pump 202. Heat transfer 216b involves the condenser of the bottom heat pump cycle 202 releasing heat to the evaporator of the top heat pump cycle 204.

[0411] Figure 3 is a schematic diagram of a steam generation system according to some embodiments described herein. Figure 3 shows a steam generation system 300 including a thermally connected first heat pump cycle 302 and a second heat pump cycle 304. The system also includes a steam compressor 306. The first heat pump cycle 302 circulates a first working fluid 318 through a conduit 320. A heat exchanger 322 receives the first working fluid 318 from an expansion valve 324. The working fluid exits from an expansion valve outlet 326 and enters the heat exchanger inlet 328. The first working fluid 318 is vaporized by heat absorption, and the working fluid becomes low-pressure steam as it exits the heat exchanger 322 from the heat exchanger outlet 330. An intake tube heat exchanger 332 may be incorporated into the first heat pump cycle 302.

[0412] Figure 4 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 400 in Figure 4 comprises three compressors 402 connected in series between a heat exchanger 403 and a steam generator 407. The steam generator is configured to receive pressurized water 408 and the working fluid of the heat pump cycle 406, and to discharge saturated steam 409 and the working fluid of the heat pump cycle. This compressor configuration allows for increasing the pressure lift of the cycle, decreasing the pressure lift per compressor, or enabling operation at lower ambient temperatures.

[0413] Figure 5 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 500 in Figure 5 comprises compressors 502, 503, and 504 arranged in parallel 501. Each compressor 502, 503, and 504 is configured to receive the working fluid 511 independently of the other compressors of the three. The three compressors are located between a first heat exchanger (e.g., a two-phase heat exchanger) 509 and a second heat exchanger (e.g., a steam generator) 506 in the heat pump cycle. The heat pump cycle also includes an expansion valve 510 and a plurality of fluid flow control valves 505. The heat pump cycle transfers heat from the working fluid 511 to a pressurized water flow 507 to produce a saturated steam fluid flow 508. This configuration of the compressors allows for a wider turndown range, increased heat pump capacity, and / or the ability to maintain high efficiency at each compressor stage during turndown by stopping individual compressors.

[0414] Figure 6 shows an example of a compressor 600 (e.g., a double-ended compressor) equipped with a cooled lubricated ball bearing 604 according to some embodiments of one or more compressors of the present disclosure. This compressor also comprises a first-stage impeller 601, a fluid collector 602, a motor cooling jacket 603, a second-stage impeller 605, a stator 606, a motor coolant 608, and a high-speed motor rotor and shaft 607. The coolant may be sprayed by an even number of jets to maintain the thermal symmetry of the bearing. The bearing may be nitrogen-treated, which may extend the functional life of the bearing. In some embodiments, the volume collector 602 may be a discharge fluid collector 602. In some embodiments, the volume collector 602 may be one or more discharge fluid collectors 602. In some embodiments, the first-stage impeller 601 and / or the second-stage impeller 605 may be a non-shrouded impeller 611. In some embodiments, the first stage impeller 601 and / or the second stage impeller 605 may be a shrouded impeller 611. The unshrouded impeller 611 can provide increased thrust and have a wider operating range. The unshrouded impeller can achieve a higher pressure ratio than the shrouded impeller. The shrouded impeller can reduce the thrust on the compressor bearing 604 and reduce refrigerant leakage.

[0415] In some embodiments, one or more cooling lubrication ball bearings 604 may be lubricated by a refrigerant. The refrigerant may be supplied by one or more fluid jets. The refrigerant may be filtered before lubricating the ball bearings 604.

[0416] In some embodiments, the bearing for the compressor may be one or more of the following: a magnetic bearing, a foil bearing, a refrigerant-lubricated ball bearing, an oil-lubricated ball bearing, or a combination thereof.

[0417] In some embodiments, the heat pump cycle may include a compressor (e.g., an oil-free centrifugal compressor). The compressor may be configured to receive a working fluid (e.g., a refrigerant) into one or more cavities of the compressor. One or more cavities may be in thermal communication with the compressor shaft and / or rotor. The working fluid may be at least partially evaporated within one or more cavities. The working fluid may provide cooling to the compressor shaft and / or rotor. The working fluid can help the compressor maintain the temperature of the rotor and / or shaft below a threshold temperature. The threshold temperature may be the demagnetization threshold temperature of the permanent magnets in the rotor. The compressor may be configured to compress a fluid flow containing water or steam to produce an outlet flow. The outlet flow may contain steam having a temperature of at least 120°C.

[0418] In some embodiments, the ball bearing 604 is part of a ball bearing assembly that includes the ball bearing 604, a mount, and a preload spring and shim pack, according to some embodiments of the present disclosure. The ball bearing 604 may be fixed within the compressor by a mount. The mount may be an elastic mount configured to absorb rigid vibration modes. The ball bearing may be coupled to a preload spring and shim pack. The preload spring and shim pack may be configured to balance the thrust load of the compressor 600 between the compressor stages.

[0419] In some embodiments, the compressor 600 may have inlet guide vanes. The inlet guide vanes may pre-swirl the fluid flowing into the compressor 600. By giving the fluid motion in the same direction as the rotation of the compressor wheels, the inlet guide vanes can improve out-of-design performance (i.e., at partial load).

[0420] The compressor 600 may have outlet guide vanes (not shown) that help convert the fluid from a high-speed state due to the rotation of the compressor wheel to a desired high-pressure, low-speed state.

[0421] In some embodiments, the compressor 600 may include a dump-volume type fluid collector 602 having a constant diameter / cross-sectional area throughout. The dump-volume type fluid collector can significantly extend the operating range of the compressor 600 and help avoid choke and stall. This helps prevent damage to the compressor 600 or very low efficiency that may be caused by choke or stall.

[0422] In some embodiments, the compressor 600 may include a variable-shape fluid collector 602. The variable-shape fluid collector 602 can improve the efficiency of the compressor 600 at the design point. In some embodiments, the compressor 600 may include a combination of multiple types of fluid collectors and the variable-shape fluid collector 602. This allows the compressor to be configured to function based on different systems and desired effects.

[0423] In some embodiments, the compressor 600 may be equipped with a vaneless diffuser. The vaneless diffuser can extend the operating flow rate range of the compressor 600 by reducing obstacles in the low static pressure recovery of the refrigerant vapor (i.e., the conversion from a high-speed state to a high-pressure state).

[0424] In some embodiments, the compressor 600 may have a vaned diffuser. The vaned diffuser may have one or more rows of vanes. The vaned diffuser can improve the peak efficiency of the compressor 600. In some embodiments, multiple diffuser styles may be used in combination in the compressor 600 to achieve a desired operating range and / or efficiency.

[0425] In some embodiments, the double-ended compressor may be configured to balance the thrust between the compressor stages. In some embodiments, a preload spring can be used to balance the thrust between the compressor stages. In some embodiments, the bearings may be nitrogen-treated. In some embodiments, the bearings may be coupled to elastic mounts configured to absorb vibration modes. In some embodiments, implementing one or more of the above-described compressor features in one or more compressors can help improve the performance and / or extend the life of the compressors.

[0426] In some embodiments, one or more oil-lubricated ball bearings may be lubricated with oil. The oil may be supplied by one or more oil loops. One or more oil loops may include an oil separator for separating the oil from the fluid (e.g., refrigerant). In some embodiments, a magnetic coupling may be used to separate the oil from the fluid. In some embodiments, a fluid dynamic seal may be used to separate the oil from the fluid. In some embodiments, implementing one or more of the above-described compressor features in one or more compressors can help improve the performance and / or extend the life of the compressors.

[0427] Figure 7 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 700 in Figure 7 includes a top cycle 710 configured to circulate a first working fluid 712 and an oil loop 720 configured to circulate oil 724. The oil loop includes an oil separator configured to separate the oil 724 from the working fluid 712. The oil separator is located downstream of the high-temperature compressor 711 of the top cycle 710. A pump 722 is configured to pump the oil 724 separated by the oil separator through the oil loop. An oil cooler is configured to receive oil from the oil separator 721 and to lower the temperature of the oil 724. The high-temperature compressor 711 is configured to receive oil from the oil cooler 723. The oil from the oil cooler is configured to cool the compressor.

[0428] Figure 8A shows a simplified diagram of an example of a compressor according to some embodiments described herein. The compressor 800 (e.g., a double-ended compressor) comprises a bearing 801, a magnetic coil, a first-stage compressor 804, a second-stage compressor, and a motor 803. The magnetic coil 802 may be configured to monitor and balance the thrust of the compressor by supplying electrons to the magnetic coil 802. The magnetic coil 802 may be located between the first-stage compressor 804 and the second-stage compressor 805.

[0429] Figure 8B shows a simplified diagram of an example of a compressor according to several embodiments. The compressor 800 in Figure 8 rotates vertically. Rotating the compressor facilitates adjustment of the thrust balance in one direction.

[0430] Figure 9 shows an example of a glycol loop 900 according to some embodiments described herein.

[0431] Figure 10 shows an example of a heat pump cycle 1000 according to some embodiments described herein. The heat pump cycle 1000 may be coupled to a glycol loop 900 as shown in Figure 9. In some embodiments, the heat pump cycle 1000 may be coupled to the glycol loop by a heat exchanger as shown.

[0432] Figure 11 shows an example of a heat pump cycle 1100 according to some embodiments described herein. The heat pump cycle 1000 comprises a refrigerant vapor compression cycle 1101 including a condenser 1102.

[0433] Figure 12 shows an example of a steam generation system according to some embodiments described herein. The heat pump cycle 1200 in Figure 12 includes a top cycle 1210 and a bottom cycle 1220. The condenser 1201 may connect the top cycle 1210 to a coolant vapor compression cycle (similar to that shown in Figure 11).

[0434] Figure 13 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 1300 in Figure 13 includes a top cycle 1310 coupled to a coolant loop 1320 configured to circulate a coolant 1323. The coolant loop 1310 includes a pump 1322 configured to feed the coolant 1323 into the coolant loop 1320. A fluid cooler 1321 is configured to lower the temperature of the coolant 1323. The high-temperature compressor 1311 of the top cycle includes a motor 1312. The high-temperature compressor 1311 is configured to receive the coolant 1323 from the fluid cooler 1321. The coolant 1323 from the coolant cooler 1321 is configured to cool the motor 1312 of the high-temperature compressor 1311.

[0435] Figure 14 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 1400 in Figure 14 comprises a heat exchanger 1401, an economizer 1406, an intercooler 1407, and a two-stage compressor 1402. The two-stage compressor comprises a first-stage compressor 1405, a second-stage compressor 1403, and a motor 1404 between the first-stage compressor 1405 and the second-stage compressor 1403. The heat exchanger 1401 and the economizer 1406 may be arranged in parallel and configured to send fluid to the intercooler 1407. The intercooler is configured to receive fluid steam in parallel from the heat exchanger 1401 and the economizer 1406, as well as from the first-stage compressor 1405. The intercooler 1407 may be located between the first-stage compressor 1405 and the second-stage compressor 1403. The second-stage compressor is configured to receive fluid from the intercooler 1407.

[0436] Figure 15 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 1500 in Figure 15 comprises a heat exchanger 1501, an intercooler 1507, and a two-stage compressor 1502. The two-stage compressor comprises a first-stage compressor 1505, a second-stage compressor 1503, and a motor 1505 between the first-stage compressor 1505 and the second-stage compressor 1503. The heat exchanger 1501 is a three-fluid heat exchanger and is configured to supply fluid to the intercooler 1507. The intercooler may be configured to receive fluid vapor from the heat exchanger 1501 and the first-stage compressor 1505. The intercooler 1507 may be located between the first-stage compressor 1505 and the second-stage compressor 1503. The second-stage compressor is configured to receive fluid from the intercooler 1507.

[0437] Figures 89 and 90 show examples of heat pump cycles according to some embodiments described herein. Figures 89 and 90 show the configuration within a top heat pump cycle, but the features of this configuration are also applicable to a bottom heat pump cycle. The top heat pump cycle 8900 in Figure 89 comprises a steam generator 8901, an economizer 8902, an intake tube heat exchanger 8903, and a two-phase heat exchanger 8904. The top heat pump cycle 8900 further comprises a first optional motor coolant flow 8910, a second optional motor coolant flow 8920, and a third optional motor coolant flow 8930. The first optional motor coolant flow 8910 may be drawn from the bottom of the two-phase heat exchanger 8904 or from just upstream of the two-phase heat exchanger 8904. A second optional motor coolant stream 8920 may be drawn from the bottom of the steam generator 8901 or from downstream of the steam generator 8901 (e.g., the high-pressure side of the top heat pump cycle). A third optional motor coolant stream 8930 may be drawn from the discharge port of the suction tube heat exchanger 8903 (e.g., the coldest liquid in the cycle). The first optional motor coolant stream 8910 and the second optional motor coolant stream 8920 may be equipped with pumps 8911 and 9821 for transporting the liquid from the main cycle to the motor. The third optional motor coolant stream 8930 may be pressure-driven. The first optional motor coolant stream 8910 and the second optional motor coolant stream 8920 may be used during startup conditions where the pressure ratio between compressors required to supply sufficient flow to the motor coolant is limited. The third optional motor coolant stream 8930 may be used after the system has gained pressure.

[0438] Figure 90 shows one embodiment of the top heat pump cycle of Figure 89. The top heat pump cycle 9000 of Figure 90 comprises a steam generator 9001, an economizer 9002, an intake tube heat exchanger 9003, and a two-phase heat exchanger 9004. The top heat pump cycle 9000 further comprises a first optional motor coolant flow 9010, a second optional motor coolant flow 9020, and a third optional motor coolant flow 9030. The first optional motor coolant flow 9010, the second optional motor coolant flow 9020, and the third optional motor coolant flow 9030 are configured to become pooled outlet streams from all cooled compressor stages 9041. The first optional motor coolant flow 9010, the second optional motor coolant flow 9020, and the third optional motor coolant flow 9030 are configured to be injected into the low-pressure section of the top heat pump cycle (e.g., the suction side of the compressor). The first optional motor coolant flow 9010 may be injected into the outlet of the two-phase heat exchanger 9004. The second optional motor coolant flow 9020 may be injected into the inlet of the two-phase heat exchanger 9004 or just upstream of the two-phase heat exchanger 9004. The third optional motor coolant flow 9030 may be injected into the hot gas bypass flow 9050.

[0439] Figure 93 shows an example of a bottom heat pump cycle according to some embodiments described herein. The bottom heat pump cycle 9300 in Figure 93 comprises an evaporator 9301, a first compressor 9302, and a second compressor 9303. The bottom heat pump cycle 9300 further comprises a first optional motor coolant flow 9310, a second optional motor coolant flow 9320, and a third optional motor coolant flow 9330. The first optional motor coolant flow 9310, the second optional motor coolant flow 9320, and the third optional motor coolant flow 9330 are configured to be pooled outlet streams from all cooled compressor stages 9341. The first optional motor coolant flow 9310, the second optional motor coolant flow 9320, and the third optional motor coolant flow 9330 each further comprises a valve 9311. A first optional motor coolant flow 9310 may be injected into the outlet of the evaporator 9301. A second optional motor coolant flow 9320 may be injected between the first and second phases of the first compressor 9302. A third optional motor coolant flow 9030 may be injected into the output of the first compressor 9302. Valve 9311 may be open or closed. The advantage of valve 9311 is that it can be used to direct the flow to different locations within the bottom heat pump cycle 9300 depending on the operating conditions. Furthermore, this configuration may help avoid overcooling of the working fluid within the bottom heat pump cycle 9300. Valve 9311 for the first optional motor coolant flow 9310 may be open when the operating temperature is high. Valve 9311 for the second optional motor coolant flow 9320 or the third motor coolant flow 9330 may be closed when the operating temperature is high. When the operating temperature is low (for example, when the ambient temperature is below the safety limit for the compressor's electronics and internal components), the valve 9311 of the first optional motor coolant flow 9310 may be closed. The valve 9311 of the second optional motor coolant flow 9320 or the third optional motor coolant flow 9330 may be open when the operating temperature is low. The advantage of this configuration is that the motor can be cooled at an optimal temperature, avoiding overcooling or overheating of the motor and internal components.

[0440] Figures 16-19 show examples of steam generation systems according to some embodiments described herein. The steam generation system 1600 in Figure 16A comprises a top cycle 1630, a bottom cycle 1620, and a heat transfer fluid cycle 1610. The heat transfer fluid cycle 1610 comprises an air source heat exchanger 1611. The heat transfer fluid cycle 1610 is coupled to the bottom cycle 1620 via a heat exchanger 1621 (e.g., a low-temperature evaporator). The bottom cycle 1620 is coupled to the top cycle 1630 via a heat exchanger 1622 (e.g., a two-phase heat exchanger). The top cycle comprises a steam generator 1631 configured to produce steam as described herein. The top cycle may further comprise a first compressor 1632, a second compressor 1633, an economizer 1634, and an intake tube heat exchanger 1635. The bottom cycle may further include a two-stage compressor 1623 and an economizer 1624.

[0441] Figures 16B–H show an example of the operation of the steam generation system shown in Figure 16A. Figures 16B–C are tables showing the system parameters and their operating values ​​given a series of exemplary constraints (e.g., inlet air temperature, steam duty cycle). In particular, %Carnot is greater than 50%. Figure 16D shows the thermodynamic curves for a bottom heat pump cycle using R513a and a top heat pump cycle using R1233zd(E). Figure 16E is a table showing the specific speed (Ns) and specific diameter (Ds) of the bottom cycle compressor, the first top cycle compressor, and the second top cycle compressor. Notably, all compressors operate at less than 30,000 RPM, and the impeller diameters range from 3 inches to 6 inches. Figures 16F–H are NsDs graphs showing the region in which compressor efficiencies exceeding 80% can be achieved for the bottom cycle compressor, the first top cycle compressor, and the second top cycle compressor.

[0442] The steam generation system 1700 in Figure 17 shows an alternative configuration of the steam generation system shown in Figure 16, further comprising an additional heat exchanger 1701 that can be thermally coupled to the refrigeration system. In some embodiments, the additional heat exchanger 1701 may function as a heat source and receive heat from the refrigeration system. In some embodiments, the additional heat exchanger 1701 may transfer heat to the refrigeration system as described herein.

[0443] The steam generation system 1800 in Figure 18 shows an alternative configuration of a steam generation system comprising a top cycle 1820, a bottom cycle 1810, a heat fluid transfer cycle 1830 (similar to the steam generation system shown in Figure 17), and an additional bottoming cycle 1840. The bottoming cycle 1840 may be coupled to the heat transfer fluid cycle 1830 by a heat exchanger 1831 of the heat transfer fluid cycle 1830. In some embodiments, the additional bottoming cycle 1840 may be a separate cycle from the steam generation system 1800 and / or separate from the refrigeration system coupled to the heat transfer cycle 1830. In some embodiments, the additional bottoming cycle 1840 may be a vapor compression cycle. The vapor compression cycle may circulate ammonia or other working fluids as described herein. The vapor compression cycle may include a compressor 1841. The compressor 1841 may be a screw compressor. In some embodiments, the system 1800 may include an additional air-coupled heat exchanger for discharging heat from the refrigeration system. In some embodiments, the heat transfer fluid cycle 1830 may include one or more air-source heat exchangers for heating the heat transfer fluid during operation in warm weather conditions, as described herein (i.e., the bottoming vapor compression system may be shut off).

[0444] The steam generation system 1900 in Figure 19 shows an alternative configuration of the steam generation system shown in Figure 18, and system 1900 includes a heat transfer fluid cycle with an additional vapor compression cycle 1910. The heat transfer fluid cycle with the additional vapor compression cycle 1910 may be configured so that the vapor compression cycle is integrated into the heat transfer fluid cycle. The condenser of the heat transfer fluid cycle with the additional vapor compression cycle 1910 may raise the temperature of the heat transfer fluid upstream of the cryogenic evaporator. This improves the performance of the heat transfer fluid thermal cycle and allows the system's compressor to operate at a temperature close to the design point. The evaporator of the heat transfer fluid cycle with the additional vapor compression cycle 1910 can cool the heat transfer fluid downstream of the cryogenic evaporator before it flows back into the air source heat exchanger, so that heat can be transferred more efficiently from the working fluid of the heat transfer fluid cycle with the additional vapor compression cycle 1910 at the start of system 1900. In some embodiments, the working fluid of the heat transfer fluid cycle is a mixture of glycol and water. In some embodiments, the working fluid of the vapor compression cycle may include ammonia or other working fluids described herein. In some embodiments, the vapor compression cycle may include a compressor. The compressor may be a screw compressor as described herein.

[0445] The steam generation system 9400 in Figure 94 shows an alternative configuration of the steam generation system shown in Figure 19, and the system 9400 comprises a heat transfer fluid cycle 9410 with an additional steam compression cycle 9420. The heat transfer fluid cycle with the additional steam compression cycle 9420 may be configured such that the steam compression cycle is integrated into the heat transfer fluid cycle. The heat transfer fluid cycle may comprise a heat recovery heat exchanger 9411, an evaporator 9412, a condenser 9413, an air source heat exchanger 9414, and a low-temperature evaporator 9415. The additional steam compression cycle 9420 may include a compressor 9421. The heat recovery heat exchanger 9411 may be configured to receive a first working fluid output stream from the low-temperature evaporator 9415. The heat recovery heat exchanger 9411 may be configured to lower the temperature of the first working fluid flow before it enters the evaporator 9412. The evaporator may be configured to lower the temperature of the first working fluid flow before it enters the air source heat exchanger 9414. The additional vapor compression cycle output stream of the evaporator 9412 may be configured to enter the compressor 9421. The heat recovery heat exchanger 9411 may be configured to raise the temperature of the second working fluid flow before it enters the condenser 9413. The condenser 9413 may be configured to raise the temperature of the second working fluid flow before it enters the cryogenic evaporator 9415. This configuration may improve the performance of the heat pump and / or allow the compressor (e.g., the compressor in a bottom heat pump cycle) to operate at a temperature close to its design point. Alternatively, or in addition, this configuration may allow operation at very low ambient temperatures. Very low ambient temperatures may be approximately -40°C, -30°C, -20°C, -10°C, 0°C, 10°C, or 20°C or lower. Very low ambient temperatures may be between any two values ​​specified herein. Alternatively, or in addition, the heat recovery heat exchanger 9411 may allow for a reduction in the capacity of the additional vapor compression cycle 9420 (for example, by reducing the amount of heat pump required for the additional vapor compression cycle). The heat recovery heat exchanger 9411, the evaporator 9412, and the condenser 9413 may be bypassed by a bypass line 9416. The bypass line may be used when the ambient temperature is high.

[0446] Figure 20 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 2000 in Figure 20 comprises a top cycle 2010 and a refrigeration system 2020. In some embodiments, the refrigeration system 2020 may be directly coupled to the top cycle 2010 by a heat exchanger 2011. The refrigeration system 2020 may supply cooling from the top cycle 2010 to a fluid 2030. The fluid 2030 may include air, water, brine, and / or other fluids. The refrigeration system 2020 may also include an air-cooled condenser / condensate loop 2021 used in combination with the heat exchanger 2011 coupled to the top cycle, so that the system can continue to operate even when steam generation is not required. In some embodiments, an intermediate fluid loop (e.g., a heat transfer fluid cycle as shown in Figure 17) may be used to connect the top cycle 2010 and the refrigeration system 2020 to dissipate heat when steam is not being generated. In some embodiments, the working fluid of the refrigeration system 2020 cycle may include ammonia or other working fluids described herein. In some embodiments, the refrigeration system 2020 may include a compressor. The compressor may be a screw compressor.

[0447] Figure 21 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 2100 in Figure 21 comprises a top cycle 2120, a bottom cycle 2110, and a cooling fluid stream 2130. The bottom cycle 2110 may comprise a first heat exchanger 2112 in parallel with a second heat exchanger 2111. The first heat exchanger may transfer heat from the cooling fluid stream 2130 to the working fluid of the bottom cycle 2110. The second heat exchanger 2111 may be an air-source heat exchanger, which is configured to operate in conjunction with the heat exchanger 2112. The heat exchanger 2112 does not receive sufficient heat from the cooling fluid stream 2130. Depending on the environment, the cooling fluid stream may be chilled water at a temperature range of approximately -5°C to approximately 15°C, approximately -5°C to approximately 0°C, approximately 0°C to approximately 5°C, approximately 5°C to approximately 10°C, or approximately 10°C to approximately 15°C. Depending on the environment, the cooling fluid stream may be chilled water at a temperature below 0°C. Depending on the environment, the cooling fluid stream may be chilled water at a temperature above 15°C. In some embodiments, the cooling fluid stream 2130 may include a cooling brine at a temperature below 0°C. The cooling brine may include a glycol mixture and / or another heat transfer fluid (e.g., air). In some embodiments, the system 2100 may further include a separate electric refrigeration system to complement the cooling generated by the system 2100.

[0448] Figures 22-24 show examples of steam generation systems according to some embodiments described herein. The steam generation system 2200 in Figure 22 comprises a top cycle 2220, a bottom cycle 2210, and a refrigeration system 2230. System 2200 may use condenser fluid from the refrigeration system 2230 as a heat source. The refrigeration system 2230 may include a heat exchanger 2231. The refrigeration system 2230 may be coupled to the bottom cycle 2210 by an intermediate loop 2240 as described herein. The heat exchanger 2231 may be a condenser coupled to the intermediate loop 2240, which is coupled to the bottom loop 2210 by a heat exchanger 2212. The heat exchanger 2212 may be an evaporator configured to transfer heat from the condenser fluid from the refrigeration system 2230 to the bottom cycle 2210. The bottom cycle 2210 may further include an air source heat exchanger 2211 in parallel with the evaporator 2212. When the condenser 2231 of the refrigeration system 2230 is coupled to the bottom cycle, the condenser fluid of the refrigeration system 2230 becomes hotter than the air temperature, improving the performance of the system 2200, thereby eliminating the need for a cooling tower and reducing the power required to operate the cooling tower fan. The temperature of the condenser fluid may be 35°C or higher. In some embodiments, the system may further include additional features such as a combination of condenser hydrothermal recovery and an air-source heat exchanger, a cooling tower or air-cooled heat exchanger connected to the refrigeration system 2230, and / or a cooling tower or air-cooled heat exchanger connected to the intermediate loop 2240. In some embodiments, the refrigeration system 2230 may be part of a standard chiller system, a direct expansion system, or a distributed cooling system.

[0449] The steam generation system 2300 in Figure 23 shows an alternative configuration of the steam generation system shown in Figure 22, comprising a top cycle 2320, a bottom cycle 2310, and a refrigeration system 2330. System 2200 may use condenser fluid from the refrigeration system 2230 as a heat source. The refrigeration system 2330 may be directly coupled to the bottom cycle 2310 by a heat exchanger 2331. The coupled heat exchanger 2331 may be a condenser, and the condenser fluid of the refrigeration system 2330 functions as a heat source for the bottom cycle 2310. The bottom cycle 2310 may further comprise an air-source heat exchanger 2311 arranged in parallel with the heat exchanger 2331, as described herein. In some embodiments, the system may further comprise additional functions such as a combination of condenser hydrothermal recovery and an air-source heat exchanger, and / or an air-cooled heat exchanger coupled to a cooling tower or refrigeration system 2230. In some embodiments, the refrigeration system 2230 may be part of a standard chiller system, a direct expansion system, or a distributed cooling system.

[0450] The steam generation system 2400 in Figure 24 shows an alternative configuration of the steam generation system shown in Figure 22, and comprises a top cycle 2420, a bottom cycle 2410, and a refrigeration system 2430. The refrigeration system 2430 includes a compressor 2431. The refrigeration system 2430 may be coupled to the bottom cycle 2410 via an oil loop 2440. The oil loop 2440 is configured to cool the motor of the compressor 2431 of the refrigeration system 2430, as shown in Figure 7, and the oil loop 2440 is coupled to the compressor 2431 of the refrigeration system 2430 and the evaporator 2412 of the bottom cycle 2410. The oil loop circulates a fluid (e.g., oil) to transfer heat from the motor of the compressor 2431 to the heat exchanger 2412. The heat exchanger 2412 may include an evaporator. The fluid in the oil loop 2440 may act as a coolant for the compressor, and heat from the compressor 2431 may act as a heat source for the bottom cycle 2410. The bottom cycle 2410 may further include an air source heat exchanger 2411 in parallel with the heat exchanger 2431. The refrigeration system 2430 may further be coupled to a cooling tower 2450. The cooling tower 2450 is coupled to the condenser of the refrigeration system 2430. In some embodiments, a back pressure regulator may be used, and / or the evaporators of the air source heat exchanger 2411 and heat exchanger 2412 may be located in separate compressor stages, as described herein. In some embodiments, the air source heat exchanger of the bottom cycle and the second heat exchanger that collects heat from the refrigeration system may be at different pressures / temperatures.

[0451] Figure 25 shows an example of a steam generation system according to some embodiments described herein, in which heat from a refrigeration system is indirectly coupled to a heat pump system. The steam generation system 2500 in Figure 25 comprises a top cycle 2520, a bottom cycle 2510, and a refrigeration system 2530. The refrigeration system 2530 may be coupled to the top cycle 2520, similar to how the refrigeration system 2230 is coupled to the bottom cycle 2210 as shown in Figure 22. System 2500 may use condenser fluid from the refrigeration system 2530 as a heat source for the top cycle 2520. The refrigeration system 2530 may include a heat exchanger 2531. The refrigeration system 2530 may be coupled to the top cycle 2520 by an intermediate loop 2540. The heat exchanger 2531 may be a condenser coupled to the intermediate loop 2540, and the intermediate loop 2540 is a condenser coupled to the bottom cycle 2520 by a heat exchanger 2522. The heat exchanger 2522 may be an evaporator configured to transfer heat from the refrigeration system 2530 to the bottom cycle 2210 of the condenser fluid. The top cycle 2520 may further include a two-phase heat exchanger 2521 coupled to the bottom cycle 2510.

[0452] Figure 26 shows an example of a steam generation system according to some embodiments described herein, in which heat from a refrigeration system is directly coupled to a heat pump system. The steam generation system 2600 in Figure 26 shows an alternative configuration of the steam generation system shown in Figure 25, comprising a top cycle 2620, a bottom cycle 2610, and a refrigeration system 2630. System 2600 may use condenser fluid from the refrigeration system 2630 as a heat source. The refrigeration system 2630 may be directly coupled to the top cycle 2620 by a heat exchanger 2631. The coupled exchanger 2631 may include a condenser, in which case the condenser fluid of the refrigeration system 2630 functions as a heat source for the top cycle 2620. The top cycle 2620 may further include a two-phase heat exchanger 2621 coupled to the bottom cycle 2610. In some embodiments, the refrigeration system may further include an air-cooled condenser or a condenser-water loop heat exchanger 2632. In some embodiments, the refrigeration system 2630 may be part of a standard chiller system, a direct expansion system, or a distributed cooling system.

[0453] Figure 27 shows an example of a steam generation system according to some embodiments described herein, which can also generate hot water in the bottom cycle. The steam generation system 2700 in Figure 27 comprises a top cycle 2720 and a bottom cycle 2710. The bottom cycle comprises a hot water heat exchanger 2712 arranged in parallel with a two-phase heat exchanger 2721. The two-phase heat exchanger 2721 couples the bottom cycle 2710 to the top cycle 2720. The hot water heat exchanger 2712 may receive a water flow and transfer heat from a portion of the working fluid flow in the bottom cycle 2710 to generate hot water. The condensing working fluid output from the hot water heat exchanger 2712, along with the condensing working fluid output from the two-phase heat exchanger 2721, is circulated back to the bottom cycle 2710 from the two-phase heat exchanger 2821. The temperature of the generated hydrothermal fluid is approximately 20°C to 30°C, 30°C to 40°C, 40°C to 50°C, 50°C to 60°C, 60°C to 70°C, 70°C to 80°C, 80°C to 90°C, 90°C to 100°C, or 100°C to 110°C, or higher as described herein.

[0454] Figures 28-33 show examples of steam generation systems capable of generating steam and / or hot water in a top cycle according to some embodiments described herein. The steam generation system 2800 in Figure 28 is capable of generating steam and / or hot water and comprises a top cycle 2820 and a bottom cycle 2810. The top cycle 2810 comprises a hot water heat exchanger 2822 arranged in series with a two-phase heat exchanger 2821, the two-phase heat exchanger 2821 coupling the top cycle 2820 and the bottom cycle 2810. The hot water heat exchanger 2822 may receive a portion of the working fluid flow in the intermediate stage of the first compressor 2823 and the second compressor 2824 of the top cycle 2820. The compressors 2823 and 2824 may be high-temperature compressors. The hot water heat exchanger 2812 may receive a portion of the working fluid flow between the first compressor 2823 and the second compressor 2824 at an intermediate pressure (i.e., the pressure before the fluid passes through the second compressor 2824). The first compressor may be a low-pressure compressor. The hot water heat exchanger 2822 may receive the water flow and transfer heat from a portion of the working fluid flow from the first compressor 2823 to produce hot water. The condensed working fluid output by the hot water heat exchanger 2822 may then be circulated back to the top cycle 2820 upstream of the two-phase heat exchanger 2821. In some embodiments, the condensed working fluid output by the hot water heat exchanger 2822 is throttled to the evaporator pressure by the expansion valve 2825 before being circulated back to the top cycle 2820 upstream of the two-phase heat exchanger 2821. The generated hot water may be at a temperature of about 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, 100°C, 110°C, or higher, as described herein.

[0455] Figure 29 shows another embodiment of the steam generation system of Figure 28. The steam generation system 2900 of Figure 29 can generate steam and / or hot water and comprises a top cycle 2920 and a bottom cycle 2910. The top cycle 2910 comprises a hot water heat exchanger 2922 arranged in series with a two-phase heat exchanger 2921. The two-phase heat exchanger 2921 connects the top cycle 2920 and the bottom cycle 2910. The hot water heat exchanger 2922 may receive a portion of the working fluid flow from an economizer 2923. The hot water heat exchanger 2922 may receive a water flow and transfer heat from a portion of the working fluid flow from the economizer 2923 to generate hot water. The condensed working fluid output from the hot water heat exchanger may then be circulated back to the top cycle 2920 located upstream of the two-phase heat exchanger 2921. In some embodiments, the condensing working fluid output from the hot water heat exchanger 2922 is throttled to the evaporator pressure by the expansion valve 2925 and then circulated back to the top cycle 2920 upstream of the two-phase heat exchanger 2921. The generated hot water may be at temperatures of about 20°C, 30°C, 40°C, 50°C, 60°C, 70°C, 80°C, 90°C, 100°C, 110°C, or higher, as described herein. In some embodiments, the hot water generator may receive the working fluid from the intercooler of the top cycle.

[0456] Figure 30 shows an alternative embodiment of the steam generation system of Figure 28. The steam generation system 3000 of Figure 30 can generate steam and / or hot water and comprises a top cycle 3020 and a bottom cycle 3010. The top cycle 3010 comprises a hot water heat exchanger 3022 arranged in series with a two-phase heat exchanger 3021, and the two-phase heat exchanger 3021 connects the top cycle 3020 and the bottom cycle 3010. The hot water heat exchanger 3022 may receive a portion of the working fluid flow from an economizer 3023. The hot water heat exchanger 3022 may receive a water flow and transfer heat from a portion of the working fluid flow from the economizer 3023 to generate hot water. In some embodiments, the condensing working fluid output from the hot water heat exchanger 3022 is throttled to evaporator pressure and / or intermediate pressure by an expansion valve 3025 and then re-injected into the top cycle 3020 between the compressor stages. The throttled working fluid is injected between compressor stages 3026 and 3027 of the first compressor 3024. In some embodiments, after being throttled in the hot water heat exchanger, the working fluid may become a two-phase mixture. The two-phase mixture may be thoroughly mixed with the superheated steam from the previous compressor stage. The mixed fluid may then be superheated. The system may be configured so that no liquid flows in from the compressor inlet when the output from the hot water heat exchanger 3022 is throttled by a valve and mixed with the working fluid of the top cycle 3020 between the compressor stages of the first and second compressors. In another embodiment, the condensed working fluid output from the hot water heat exchanger 3022 may be injected directly into the intercooler 3023 between the first compressor 3024 and the second compressor 3028 without being throttled by a valve. The resulting hot water may have a temperature of about 100°C as described herein. In some embodiments, the hot water generator may receive the working fluid from the intercooler of the top cycle.

[0457] Figure 31 shows another embodiment of the steam generation system of Figure 30. The steam generation system 3100 of Figure 30 can produce steam and / or hot water and comprises a top cycle 3120 and a bottom cycle 3110. The top cycle 3120 comprises a hot water heat exchanger 3122 coupled in series with a steam generator 3133. The hot water heat exchanger 3122 may receive a working fluid output from a compressor 3123, where the working fluid is hot steam. The hot water heat exchanger 3122 may transfer heat from the hot steam to a water flow to produce hot water. The condenser of the hot water heat exchanger 3122 may output the working fluid to a steam generator 3124. The working fluid output from the hot water heat exchanger may be low-temperature steam or a partially condensed two-phase fluid. The steam generator may transfer the remaining heat of the working fluid to a pressurized water flow to produce steam.

[0458] In some embodiments (not shown), a hot water heat exchanger 3122 may be located downstream of the condenser of a steam generator 3124. The steam generator may receive a high-temperature steam flow from a compressor 3123, and the steam generator transfers heat from the high-temperature steam to a pressurized water flow to produce steam. The condenser of the steam generator may then output at least partially condensed working fluid (e.g., a two-phase mixture of steam and liquid). The hot water heat exchanger 3122 transfers the remaining heat from the partially condensed working fluid to a water flow to produce hot water, and the working fluid may be further condensed as described herein.

[0459] Figure 32 shows another embodiment of the steam generation system of Figure 30. The steam generation system 3200 of Figure 32 comprises a top cycle 3220 and a bottom cycle 3210. The top cycle comprises a hot water heat exchanger 3222 arranged in parallel with a steam generator 3224. The hot water heat exchanger 3222 may receive a water flow and transfer heat from a portion of the working fluid flow from the compressor 3223 to produce hot water. The steam generator 3224 may receive the remainder of the working fluid flow from the compressor 3223, and the steam generator may transfer heat from the remainder of the working fluid flow from the compressor 3223 to produce steam. The working fluid from the compressor 3223 may be high-temperature steam. The hot water or high-temperature hot water produced will be described herein.

[0460] Figure 33 shows an alternative embodiment of the steam generation system in Figure 32, in which the hot water heat exchanger and steam generator are configured as a single three-fluid heat exchanger 3322 as described herein.

[0461] Figures 34-35 show examples of steam generation systems according to some embodiments described herein, which can generate steam and / or hot water in a top cycle. The steam generation system 3200 in Figure 34 comprises a hot water heat exchanger 3422 and a steam generator 3421. The hot water heat exchanger 3422 is positioned in parallel with the steam flow of the steam equipment, and the hot water generator 3422 receives a portion of the steam flow generated from the steam generator 3421. The hot water heat exchanger 3422 may generate hot water by transferring heat from a portion of the steam flow to the water flow. The remaining portion of the steam flow generated by the steam generator 3421 is sent to the steam equipment described herein. By positioning the hot water heat exchanger 3422 in parallel with the steam equipment, the steam quality of the steam equipment can be improved compared to when the hot water heat exchangers are positioned in series.

[0462] Figure 35 shows another embodiment of the steam generation system of Figure 34. System 3500 comprises a hot water heat exchanger 3522, a steam compressor 3523, and a steam generator 3521. The hot water heat exchanger 3522 is located in series with the stream of the steam equipment. The steam compressor 3523 is located between the steam generator 3521 and the hot water generator 3522. The steam compressor 3523 superheats the steam produced by the steam generator 3521. The hot water heat exchanger 3522 may transfer heat from the superheated steam to the water stream to produce hot water. The hot water heater outputs desuperheated steam. The desuperheated steam output from the hot water generator may then be supplied to the steam equipment described herein. The desuperheated steam may be saturated steam.

[0463] Figure 36 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 3600 in Figure 36 comprises a compressor 3603, a heat exchanger 3602 (e.g., an air source evaporator), and a waste heat air heater 3601. The waste heat air heater may utilize waste heat from a part of the heat pump cycle 3600 (e.g., the compressor 3602) to heat the air flowing into the air source heat exchanger 3602 as described herein. Using the waste heat air heater 3601 as shown allows the air source evaporator 3602 to be kept at a higher working fluid saturation temperature, facilitating implementation into the heat cycle.

[0464] Figure 37 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 3700 in Figure 37 comprises a heat exchanger 3702 (e.g., an air source evaporator) and an electric resistance heater 3701. The electric resistance heater 3701 may heat the air flowing into the air source heat exchanger 3702. By using the electric resistance heater 3701 as shown, the air source evaporator 3702 can maintain a higher working fluid saturation temperature, which facilitates implementation into the heat cycle. In some embodiments, the electric resistance heater 3701 may be used when there is not enough waste heat to heat the air.

[0465] Figure 38 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 3800 in Figure 38 comprises a first heat pump cycle 3820 and another cycle 3810. The other cycle 3810 may comprise a first heat exchanger 3811 (e.g., an air source evaporator) and a second heat exchanger 3812. The first heat pump cycle 3820 may comprise a heat exchanger 3821 (e.g., an evaporator). The first heat pump cycle 3820 may be coupled to the other cycle 3810 by an intermediate loop 3830. The second heat exchanger of the other cycle may transfer heat from the working fluid of the other cycle to an intermediate fluid (e.g., glycol, water, etc.). The intermediate loop 3830 may be coupled to the first heat cycle 3810 via an evaporator 3821. The evaporator 3821 may transfer heat from the intermediate fluid to the working fluid of the first heat pump cycle. In some embodiments, the first heat pump cycle is a bottom cycle, and another cycle 3810 may be a bottoming cycle, as described herein. The bottoming cycle may be used to supply chilled water to the bottom cycle of a water vapor generation system in extremely cold weather conditions.

[0466] Figure 39 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 3900 in Figure 39 comprises a first heat pump cycle 3920 and another cycle 3910. The other cycle 3910 may include a first heat exchanger 3911 (e.g., an air source evaporator). The first heat pump cycle 3920 may include a heat exchanger 3921 (e.g., an evaporator). The first heat pump cycle 3920 may be directly coupled to the other cycle 3810 by the heat exchanger 3921. In some embodiments, as described herein, the first heat pump cycle may be a bottom cycle and the other cycle 3810 may be a bottoming cycle. The bottoming cycle can be used to supply chilled water to the bottom cycle of a water vapor generation system in cold climates.

[0467] Figure 40A shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 4000 in Figure 40 includes a main compressor (e.g., centrifugal compressor) 4002 between a heat exchanger (e.g., air source evaporator) 4001 and a two-phase heat exchanger 4005 within the heat pump cycle. The heat pump cycle 4000 further includes an auxiliary compressor and a valve 4004. The auxiliary compressor 4003 helps to keep the suction pressure of the main compressor (e.g., centrifugal compressor) 4002 constant. The valve 4004 is configured to control the flow rate of the working fluid in the cycle. The valve 4004 may be configured to shut off the auxiliary compressor 4003 when no further lift is needed. The valve 4004 can direct the working fluid to the auxiliary compressor and centrifugal compressor 4002 if the main compressor is not supplying sufficient lift to the working fluid, as described herein. In some embodiments, the auxiliary compressor 4003 is added to the bottom cycle (as shown). In some embodiments, the additional compressor 4003 is added to the top cycle (not shown), as shown in Figure 40A. In some embodiments, if the saturation temperature / heat transfer temperature of the top cycle and / or bottom cycle decreases due to cold weather or other operating changes, the additional compressor may be integrated into the cycle to maintain the main compressor of the cycle in a relatively constant operating state.

[0468] Figures 40B–F show an example of the operation of the steam generation system from Figure 16 with an additional compressor added, as shown in Figure 40A. Figures 40B–C are tables showing the system parameters and their operating values ​​given a series of exemplary constraints (e.g., inlet air temperature, steam load). Notably, the % Carnot exceeds 50% even when the ambient air temperature is below -10°C. Figure 40D shows the thermodynamic curves for the bottom heat pump cycle using R513a and the top heat pump cycle using R1233zd(E). Figure 40E is a table showing the specific speed (Ns) and specific diameter (Ds) of the additional compressor. Notably, all compressors operate at less than 30,000 RPM and have impeller diameters between 3 and 6 inches. Figure 40F is an NsDs graph showing the region where the efficiency of the additional compressor exceeds 80%.

[0469] Figure 41 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4100 in Figure 41 comprises a top cycle 4120 and a bottom cycle 4110. The top cycle comprises a first compressor 4121, a second compressor 4122, a third compressor 4123, and a steam generator 4125. The steam generator 4125 may receive a working fluid (e.g., hot steam) output from the third compressor 4123. The top cycle 4120 may further comprise an optional bypass line 4124. The optional bypass line may connect the steam generator 4125 to an intermediate stage between two compressors, such as between the second compressor 4122 and the third compressor 4123. With the optional bypass line 4124 and shut-off valve (not shown), the top cycle 4120 can shut off one or more unnecessary compressor stages to maintain operation at optimal efficiency, or with the optional bypass line 4124 and shut-off valve, one or more additional compressors can be turned on to overcome the operating losses or cold weather losses described herein.

[0470] Figure 42 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4200 in Figure 42 comprises a top cycle 4220 and a bottom cycle 4210. The top cycle comprises a first compressor stage 4221, a second compressor stage 4222, a third compressor stage 4223, and a steam generator 4224. The first compressor of the first compressor stage 4221 may receive a subcritical working fluid. The second compressor of the second compressor stage 4222 may receive a subcritical fluid from the first compressor stage 4221. The second compressor of the second compressor stage 4222 may output a first supercritical fluid to the steam generator 4125. The steam generator 4125 generates steam by transferring heat from the first supercritical fluid to a pressurized water flow. The steam generator 4224 may output working fluid to the third compressor of the third compressor stage 4223. The third compressor of the third compressor stage 4223 may output a second supercritical fluid to the steam generator 4224. The steam generator 4224 generates steam by transferring heat from the second supercritical fluid to a pressurized water flow. The steam generator 4224 may be a single unit or a plurality of independent units arranged in series and / or parallel. In some embodiments, an intercooler and / or economizer (not shown) may be part of the top cycle 4220. The economizer / intercooler line should circulate a subcritical working fluid and should therefore be located at an intermediate pressure between non-supercritical compressors (e.g., after the first or second stage of the first compressor), as described herein. In alternative embodiments (not shown), the steam generator may be a plurality of heat exchangers configured to operate in series or parallel. The advantages of operating multiple heat exchangers in parallel include the ability to generate steam at different pressures and temperatures (for example, a 150°C stream after two compressors and a 180°C stream after a third compressor).

[0471] Figure 81 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 8100 in Figure 81 comprises a top cycle 8120 and a bottom cycle 8110. The bottom cycle comprises a compressor 8111 and a heat exchanger 8112. The compressor 8111 may output a supercritical fluid to the heat exchanger 8112. The heat exchanger 8112 transfers heat from the supercritical fluid to the working fluid of the top cycle 8120. In some embodiments, an intercooler and / or economizer may be part of the bottom cycle 8110. The economizer / intercooler line needs to be located at an intermediate pressure because it needs to circulate a subcritical working fluid.

[0472] Figure 43 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 4300 in Figure 43 comprises a heat exchanger 4301 (e.g., a steam generator). In some embodiments, the steam generated by the steam generator 4301 is received by a steam compressor 4302. Steam compressors(s) may be used to compensate for the loss of heat pump steam discharge pressure during cold climate operation, as described herein. When the ambient temperature is low, the saturation point of the bottom cycle evaporator decreases. This can cause the steam discharge temperature to decrease from about 200°C, 175°C, 150°C, 125°C, or below 100°C to about 150°C, 130°C, 120°C, 110°C, or below 100°C. The steam discharge temperature may decrease from a temperature between any two values ​​described herein. The steam discharge temperature may decrease to a temperature between any two values ​​described herein. The steam compressor(s) 4302 can be used to raise the steam temperature to the facility's demand. To reduce steam superheating, water injection may be used into and / or downstream of the steam compressor 4302. This increases the steam discharge flow rate of the steam generation system.

[0473] Figure 91 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 9100 in Figure 91 comprises a top cycle 9110, a working fluid flow 9120, and a steam generator 9121. The working fluid flow 9120 enters the steam generator 9121 as pressurized water and is discharged as saturated steam 9123. The working fluid flow 9120 includes a steam compressor 9122. The steam compressor 9122 may be configured to increase the pressure (and thereby increase the temperature) of the output water or steam 9123. One or more water flows 9130 may be injected into the working fluid flow 9120 upstream, inside, or downstream of the steam compressor 9122. Injecting a working fluid flow upstream of or inside the steam compressor 9122 allows the steam compressor to operate at a lower temperature, thus enabling the use of more commercially available equipment (steam compressor, valves and seals around the steam compressor, etc.).

[0474] Figure 92 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 9200 in Figure 92 comprises a top cycle 9210, a working fluid flow 9220, and a steam generator 9221. The working fluid flow 9220 enters the steam generator 9221 as pressurized water and is discharged as saturated steam 9222. The working fluid flow 9220 comprises a steam compressor 9223. The steam compressor 9223 may be configured to increase the pressure (and thereby increase the temperature) of the output steam 9222. The working fluid flow 9220 may further comprise a heat exchanger 9224 that cools the working fluid flow 9222 using a refrigerant 9225 from another location in the system. Alternatively, the heat exchanger 9224 may use a different heat transfer fluid (e.g., glycol from a bottom heat pump cycle). In alternative embodiments (not shown), the heat exchanger may be located downstream of or inside the compressor. The advantages of heat exchangers include the advantages of water injection described herein.

[0475] Figure 44 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4400 in Figure 44 comprises a top cycle 4420, a bottom cycle 4410, and a topping cycle 4430. The topping cycle may comprise a heat exchanger 4432 (e.g., a steam generator), a compressor 4431, and an expansion valve 4433, as described herein. The topping cycle may be coupled to the top cycle 4420 by a two-phase heat exchanger 4421. The topping cycle 4430 may circulate a working fluid, including hydrocarbons, natural fluids, special fluids, supercritical fluids, and / or other working fluids described herein, to achieve higher steam supply temperatures and / or to cope with cold climates.

[0476] Figure 45 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4500 in Figure 45 comprises a top cycle 4520, a bottom cycle 4510, and a topping cycle 4530 (shown in Figure 44). The topping cycle may comprise a heat exchanger 4532 (e.g., a steam generator), a compressor, and an expansion valve. The topping cycle may be coupled to the top cycle 4520 by a two-phase heat exchanger 4521. The top cycle 4520 may further comprise a steam generator 4522 upstream of the two-phase heat exchanger 4521. The topping cycle may be turned on when additional heat and / or pressure is required to generate steam. The topping cycle may be turned on in response to cold climates and / or increased demand for steam pressure. The topping cycle 4530 can circulate a working fluid, including hydrocarbons, natural fluids, specialty fluids, supercritical fluids, or other working fluids described herein, to achieve higher steam supply temperatures and / or to cope with cold climates. In some embodiments, the system 4500 may comprise one or more topping cycles. The topping cycles may be configured to generate steam and hot water or steam at multiple pressures as described herein.

[0477] Figure 46 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4600 in Figure 46 comprises a top cycle 4620 and a bottom cycle 4610. The bottom cycle comprises a high-temperature gas bypass line 4611. The high-temperature gas bypass line 4611 is configured to receive a working fluid (e.g., high-temperature gas) from a compressor 4612. The high-temperature gas bypass line 4611 comprises a valve 4613 configured to turn the high-temperature gas bypass line 4611 on and off. The high-temperature gas bypass line 4611 may be turned on to supply the working fluid to a heat exchanger 4614 (e.g., a low-temperature evaporator) and to defrost the coils of the evaporator. The high-temperature gas bypass line 4611 may be turned on to defrost the evaporator in cold weather, as described herein.

[0478] Figure 47 shows another embodiment of the steam generation system of Figure 46. System 4700 comprises a top cycle 4720 and a bottom cycle 4710. The bottom cycle comprises a plurality of hot gas bypass lines 4711 arranged in parallel. The hot gas bypass lines 4711 are configured to receive working fluid (e.g., hot gas) from a compressor 4712. The hot gas bypass lines 4711 include valves 4713 configured to turn hot gas bypass lines 4611 on and off. Turning on the hot gas bypass lines 4611 may supply working fluid to a heat exchanger 4614 (e.g., an evaporator) arranged in series. The hot gas bypass lines 4611 can supply working fluid from the compressor 4712 and defrost the coils of the evaporator 4714, as described herein. In cold weather, the hot gas bypass lines 4611 may be turned on to defrost the evaporator and may operate independently of each other.

[0479] Figure 48 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 4800 in Figure 48 comprises a top cycle 4820 and a bottom cycle 4810. The bottom cycle 4810 comprises a two-phase heat exchanger 4815, a low-temperature heat exchanger 4811, a cooler / re-condenser 4813, a first valve 4812 (e.g., an expansion valve), and a second valve (e.g., an expansion valve) 4814. The first valve 4812 may be configured to receive working fluid from the two-phase heat exchanger 4815. The first valve 4812 may partially expand the working fluid to an intermediate pressure between the two-phase heat exchanger and the low-temperature evaporator. The cooler / re-condenser 4813 may be located between the first valve 4812 and the second valve 4814. The cooler / recondenser 4813 may then recondense and / or supercool the partially expanded working fluid output by the first expansion valve 4812, and send the condensed working fluid to the cryogenic evaporator 4811. The system 4800 may operate as described herein.

[0480] Figure 49 shows an example of a heat pump cycle according to some embodiments described herein. The heat pump cycle 4900 in Figure 49 comprises a heat exchanger 4902 (e.g., an air source evaporator) and an electric resistance heater 4901. The electric resistance heater 4901 may heat the air flowing into the air source heat exchanger 4902. By using the electric resistance heater 4901 as shown, the air source evaporator 4902 can maintain a higher working fluid saturation temperature, which facilitates implementation into the heat cycle. In some embodiments, the electric resistance heater 4901 may be used when there is not enough waste heat to heat the air.

[0481] Figure 50 shows an alternative embodiment of the steam generation system in Figure 49. The heat pump cycle 5000 in Figure 50 comprises a heat exchanger 5001 (e.g., an air source evaporator) with an electric resistance heater directly wound around the coil of the evaporator 5001. The use of an electric resistance heater helps to maintain a high saturation temperature of the working fluid and is also easy to implement in the heat cycle. In some embodiments, an electric resistance heater 4901 may be used when there is not enough waste heat to heat the air as described herein.

[0482] In some embodiments, electric resistance heaters may be used in the air source heat exchangers of intermediate loops (e.g., glycol loops) and / or cycles (e.g., heat transfer cycles).

[0483] Figures 51-53 show examples of steam generation systems according to some embodiments described herein. System 5100 comprises a top cycle 5120 and a bottom cycle 5110. The system further comprises a defrost spray line 5112, which receives a portion of the steam generated by the steam generator 5122 and supplies it to a heat exchanger 5111 (e.g., an air source heat exchanger). The supplied steam may be used to defrost the coils of the evaporator 5111, as described herein.

[0484] Figure 52 shows an alternative embodiment of the steam generation system of Figure 51. System 5200 comprises a top cycle 5220 and a bottom cycle 5210. The system further comprises a defrost spray line 5212, which receives hot water from the facility and supplies it to a heat exchanger 5211 (e.g., an air source heat exchanger). The supplied steam may be used to defrost the evaporator 5211 coils as described herein.

[0485] Figure 53 shows an alternative embodiment of the steam generation system of Figure 51. System 5300 comprises a top cycle 5320 and a bottom cycle 5310. The system further comprises a defrost spray line 5313, which receives hot water from the hot water heat exchanger 5312 of the bottom cycle 5310 and supplies it to a heat exchanger 5311 (e.g., an air source heat exchanger). The supplied steam can be used to defrost the coils of the evaporator 5311. The defrost spray line 5313 may further comprise a thermal storage unit 5314 as described herein. The thermal storage unit may be used to generate hot water during peak efficiency (e.g., daytime) and release it during colder periods (e.g., nighttime).

[0486] Figures 54-56 show examples of steam generation systems according to some embodiments described herein. The steam generation system 5400 in Figure 54 comprises a top cycle 5420, a bottom cycle 5410, and a heat transfer fluid cycle 5430. The heat transfer fluid cycle 5430 comprises a heat exchanger 5431 (e.g., an air source heat exchanger). The heat transfer fluid cycle 5430 may be coupled to the bottom cycle 5410 by a heat exchanger 5411 (e.g., a low-temperature evaporator). The heat transfer fluid cycle 5430 may further include an electric resistance heater 5432 between the low-temperature evaporator 5411 and the air source heat exchanger 5431. The electric resistance heater 5432 is output from the low-temperature evaporator 4511 and configured to heat the working fluid upstream of the air source heat exchanger 5431. The electric resistance heater 5432 may be used for defrosting the evaporator 5431 and / or to prevent the evaporator coils from freezing in cold weather. In some embodiments, the heat transfer fluid cycle 5430 may be an intermediate loop (e.g., a glycol loop).

[0487] Figure 55 shows an alternative embodiment of the steam generation system of Figure 54. The steam generation system 5500 of Figure 55 comprises a top cycle 5520, a bottom cycle 5510, and a heat transfer fluid cycle 5530. The heat transfer fluid cycle 5530 comprises a heat exchanger 5531 (e.g., an air source heat exchanger). The heat transfer fluid cycle 5530 may be coupled to the bottom cycle 5510 via a heat exchanger 5511 (e.g., a low-temperature evaporator). The heat transfer fluid cycle 5530 may further comprise a glycol loop 5540. The glycol loop 5540 may comprise an electric resistance heater 5541. The electric resistance heater 5541 may receive a portion of the working fluid output by the air source heat exchanger 5531 and heat a portion of the working fluid before injecting the heated portion of the working fluid upstream of the air source heat exchanger 5531. The electric resistance heater 5541 may be used to defrost the evaporator 5531 in cold climates and / or to prevent the evaporator coil from freezing, as described herein.

[0488] Figure 56 shows an alternative embodiment of the steam generation system of Figure 55. The steam generation system 5600 of Figure 56 comprises a top cycle 5620, a bottom cycle 5610, and a heat transfer fluid cycle 5630. The heat transfer fluid cycle 5630 comprises a plurality of glycol loops 5640 arranged in parallel. The plurality of glycol loops 5640 are configured to receive a portion of the working fluid (e.g., glycol) in parallel from one or more heat exchangers 5631 (e.g., air heat exchangers). The plurality of glycol loops 5640 are provided with valves configured to turn each of the plurality of glycol loops 5640 on and off. The plurality of glycol loops 5640 may be turned on to supply a portion of the working fluid to an electric resistance heat exchanger 5641. The electric resistance heat exchanger 5641 may heat a portion of the working fluid and inject it upstream of the heat exchanger 5631. Multiple glycol loops 5640 may be turned on to defrost the air source heat exchanger 5631 in cold weather, and the multiple glycol loops 5640 may operate independently of each other as described herein.

[0489] In some embodiments, one or more additional defrosting methods may be used in conjunction with one or more electric resistance heaters, as described herein.

[0490] Figures 69-72 show examples of steam generation systems according to some embodiments described herein. The steam generation system 6900 in Figures 69A-B comprises a top cycle 6920, a bottom cycle 6910, and a heat transfer fluid cycle 6930. The heat transfer fluid cycle 6930 comprises a heat exchanger 6931 (e.g., an air source heat exchanger). The heat transfer fluid cycle 6930 may be coupled to the bottom cycle 6910 via a heat exchanger 6911 (e.g., a low-temperature evaporator). The heat transfer fluid cycle 6930 may further comprise a glycol loop 6940. The glycol loop 6940 may comprise a glycol heater 6941. The glycol heater 6941 may be located in the bottom cycle 6910. The glycol heater 6941 may be located upstream of a heat exchanger 6912 (e.g., a two-phase heat exchanger) and downstream of a compressor 6913 (e.g., a two-stage compressor). The glycol heater 6941 may be configured to heat the glycol flowing into the glycol heater 6941 from the heat transfer fluid cycle 6930 by transferring heat from the bottom cycle 6910. The glycol loop may be configured to be injected upstream of the heat exchanger 6931. The glycol heater 6941 may be configured to receive all of the working fluid discharged from the compressor 6913 (for example, as shown in Figure 69A). Alternatively, the glycol heater 6941 may be configured to receive a portion of the working fluid discharged from the compressor 6913 and divert the rest of the working fluid 6914 around the glycol heater 6941 (for example, as shown in Figure 96B). The proportion of the working fluid discharged from the compressor that passes through the glycol heater may be approximately 0-10%, 10-20%, 20-30%, 30-40%, 40-50%, 50-60%, 60-70%, 70-80%, 80-90%, or 90-100%. The glycol loop 6940 may be used for defrosting the heat exchanger 6931 and / or to prevent the heat exchanger coils from freezing in cold weather.

[0491] Figure 70 shows an alternative embodiment of the steam generation system of Figure 69. The steam generation system 7000 of Figure 70 comprises a top cycle 7020, a bottom cycle 7010, and a heat transfer fluid cycle 7030. The heat transfer fluid cycle 7030 may include a glycol loop 7040, and the glycol loop 7040 may include a glycol heater 7041. The glycol heater 7041 may be located in the bottom cycle 7010 on a parallel stream 7011 that bypasses the heat exchanger 7012 (e.g., a two-phase heat exchanger). The glycol heater 7041 may be configured to condense the working fluid in the bottom cycle 7010 before the working fluid re-flows into the bottom cycle downstream of the heat exchanger 7012. A control valve 7013 may be used to shut off the parallel stream 7011 when not in use.

[0492] Figure 71 shows an alternative embodiment of the steam generation system of Figure 69. The steam generation system 7100 of Figure 71 comprises a top cycle 7120, a bottom cycle 7110, and a heat transfer fluid cycle 7130. The heat transfer fluid cycle 7130 may include a glycol loop 7140, and the glycol loop 7140 may include a glycol heater 7141. The glycol heater 7141 may be located in the top cycle 7120 upstream of the expansion valve 7121 and downstream of the heat exchanger 7122 (e.g., an intake tube heat exchanger). Supercooling of the working fluid in the top cycle 7120 may have a positive effect on the performance of the top cycle by degrading the steam quality at the inlet of the evaporator 7123.

[0493] Figure 72 shows an alternative embodiment of the steam generation system of Figure 69. The steam generation system 7200 of Figure 72 comprises a top cycle 7220, a bottom cycle 7210, and a heat transfer fluid cycle 7230. The heat transfer fluid cycle 7230 comprises a plurality of glycol loops 7240 arranged in parallel. The plurality of glycol loops 7240 are configured to receive a portion of the working fluid (e.g., glycol) in parallel from one or more heat exchangers 7231 (e.g., air heat exchangers). The plurality of glycol loops 7240 are provided with valves configured to turn each of the plurality of glycol loops 7240 on and off. By turning on the plurality of glycol loops 7240, a portion of the working fluid can be supplied to a glycol heater 7241. The glycol heater may be located at any position in the top cycle or bottom cycle as described herein. The glycol heater 7241 may heat a portion of the working fluid and inject it upstream of the heat exchanger 7231. Multiple glycol loops 7240 may be turned on in cold weather to defrost the air source heat exchanger 7231, and may operate independently of each other as described herein.

[0494] Figure 73 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 7300 in Figure 73 comprises a top cycle 7320, a bottom cycle 7310, and a heat transfer fluid cycle 7330. The heat transfer fluid cycle 7330 comprises a heat exchanger 7331 (e.g., an air source heat exchanger). The heat transfer fluid cycle 7330 may be coupled to the bottom cycle 7310 by a heat exchanger 7311 (e.g., a low-temperature evaporator). The heat transfer fluid cycle 7330 may comprise a glycol loop 7340. The glycol loop 7340 may comprise a thermal regenerator 7341. The thermal regenerator 7341 may be any thermal regenerator described herein. The glycol loop may be configured to be injected upstream of the heat exchanger 7331. The glycol loop 7340 can be used for defrosting the heat exchanger 7331 and / or for preventing the heat exchanger coils from freezing in cold weather. The heat transfer fluid cycle may include one or more heat exchangers (e.g., air heat exchangers) in parallel (for example, as shown in Figure 72).

[0495] Figures 57-66 show examples of heat pump cycles according to some embodiments described herein. The heat pump cycle 5700 in Figure 57 comprises a heat exchanger 5701 (e.g., a two-phase heat exchanger), a first compressor 5702, a second compressor 5703, a heat exchanger 5704 (e.g., a steam generator), a heat exchanger 5706 (e.g., a waste heat (WH) heat exchanger), a first valve 5705, and a second valve 5707. The two-phase heat exchanger 5701 may be arranged in parallel with the WH heat exchanger 5706. The WH heat exchanger 5706 may receive working fluid from the steam generator 5704 and output working fluid in an intermediate pressure stage between the first compressor 5702 and the second compressor 5702. The two-phase heat exchanger 5701 may receive the working fluid output from the steam generator 5704 and output the working fluid to the first compressor 5702. The WH heat exchanger 5706 may receive waste heat from the compressor stage or an external heat source (e.g., process heat, combined heat and power, geothermal heat, etc.) to heat the working fluid. Valves 5705 and 5707 may control the flow of the working fluid between the WH exchanger 5706 and the two-phase heat exchanger 5701. Valve 5705 may be used to switch the WH exchanger 5706 on and / or off. The WH exchanger 5706 configured as shown in Figure 57 may evaporate the working fluid at a temperature of about 30°C in the bottom cycle and / or about 100°C in the top cycle. As shown in Figure 57, the WH exchanger 5706 can evaporate the working fluid at a temperature of approximately 0°C to approximately 60°C in the bottom cycle, and / or evaporate the working fluid at a temperature of approximately 60°C to approximately 130°C or approximately 90°C to approximately 100°C in the top cycle.

[0496] Figure 58 shows an alternative embodiment of the heat pump cycle of Figure 57. The heat pump cycle 5800 of Figure 58 comprises a heat exchanger 5801 (e.g., a two-phase heat exchanger), a first compressor 5802, a second compressor 5803, a heat exchanger 5804 (e.g., a steam generator), a heat exchanger 5806 (e.g., a waste heat (WH) heat exchanger), a first valve 5805, and a second valve 5807. The two-phase heat exchanger 5801 may be arranged in parallel with the WH heat exchanger 5806. The WH heat exchanger 5806 may receive working fluid output from the steam generator 5804 and output the working fluid to the first compressor 5802. The two-phase heat exchanger 5801 may receive working fluid output from the steam generator 5804 and output the working fluid to the first compressor 5802. The WH heat exchanger 5806 may receive waste heat from the compressor stage or an external heat source (e.g., process heat, combined heat and power, geothermal heat, etc.) to heat the working fluid. The heat pump cycle 5800, including the WH heat exchanger 5806 shown in Figure 58, may be used in conjunction with the refrigeration system integration described herein (e.g., chilled water), and very low-grade engine waste heat (e.g., lubricating oil), and / or the hot water storage described herein. The WH heat exchanger 5806 configured as shown in Figure 58 may evaporate the working fluid at a temperature of about 15°C in the bottom cycle and / or about 60°C in the top cycle. The WH heat exchanger 5806 configured as shown in Figure 58 may evaporate the working fluid at a temperature of about -20°C to about 50°C in the bottom cycle and / or about 50°C to about 90°C in the top cycle.

[0497] Figure 59 shows an alternative embodiment of a heat pump cycle combining the WH heat exchanger configurations shown in Figures 57 and 58. The heat pump cycle 5900 in Figure 59 comprises a first WH heat exchanger 5901 shown in Figure 57 and a second WH heat exchanger 5902 shown in Figure 58. The heat pump cycle 5900 combining the WH heat exchanger configurations may evaporate the working fluid at a temperature of approximately 0 to 15°C in the bottom cycle and / or approximately 55 to 65°C in the top cycle. The heat pump cycle 5900 combining the WH heat exchanger configurations may evaporate the working fluid at a temperature in the range of approximately -20°C to approximately 60°C in the bottom cycle and / or approximately 50°C to approximately 130°C in the top cycle.

[0498] Figure 60 shows an alternative embodiment of the heat pump cycle of Figure 57. The heat pump cycle 6000 of Figure 60 comprises a heat exchanger 6001 (e.g., a two-phase heat exchanger), a first compressor 6002, a second compressor 6003, a heat exchanger 6004 (e.g., a steam generator), a heat exchanger 6006 (e.g., a waste heat (WH) heat exchanger), an economizer 6008, a first valve 6005, a second valve 6007, and a third valve 6010. The economizer 6008 may be arranged in parallel with the WH heat exchanger 6006. The WH heat exchanger 6006 may receive the working fluid output from the steam generator 6004 and output the working fluid to the mixer 6009. The economizer may receive the working fluid output from the steam generator 6004 and output the working fluid to the mixer 6009. The mixer mixes the working fluid output from the WH heat exchanger 6006 and the economizer 6009, and injects the mixed working fluid between the first compressor 6002 and the second compressor 6003 (e.g., the intermediate compressor stage). The WH heat exchanger 6006 configured as shown in Figure 60 may evaporate the working fluid at a temperature of about 30°C in the bottom cycle (e.g., using condenser heat from a refrigeration system) and / or at a temperature of about 100°C in the top cycle (e.g., using engine exhaust). The WH heat exchanger 6006 configured as shown in Figure 60 may evaporate the working fluid at a temperature in the range of about 0°C to about 60°C in the bottom cycle and / or about 60°C to about 130°C or about 90°C to about 100°C in the top cycle.

[0499] Figure 61 shows an alternative embodiment of the heat pump cycle, combining the WH heat exchanger configurations shown in Figures 58 and 60. The heat pump cycle 6100 in Figure 61 includes a first WH heat exchanger 6102 arranged in parallel with the two-phase heat exchanger 6101 as shown in Figure 58, and a second WH heat exchanger 6104 coupled in parallel with the economizer 6103 as shown in Figure 60.

[0500] Figure 62 shows an alternative embodiment of the heat pump cycle combining the WH heat exchanger configuration shown in Figure 59. The heat pump cycle 6200 in Figure 62 comprises a heat exchanger 6201 (e.g., a two-phase heat exchanger), a first compressor 6203, a second compressor 6204, a heat exchanger 6205 (e.g., a steam generator), a heat exchanger 6202 (e.g., a waste heat (WH) heat exchanger), and an economizer 6206. The two-phase heat exchanger 6201 may be arranged in parallel with the WH heat exchanger 6202. The WH heat exchanger 6202 may receive the working fluid output from the steam generator 6205 and output the working fluid to the first compressor 6203. The two-phase heat exchanger 6201 may receive the working fluid output from the steam generator 6205 and output the working fluid to the first compressor 6203. The economizer 6206 may receive the working fluid output from the steam generator 6205 and output the working fluid in an intermediate pressure stage between the first compressor 6203 and the second compressor 6204. The cycle 6200 may further include one or more valves configured to control the flow rate of the working fluid to the two-phase heat exchanger 6201, the WH heat exchanger 6202, and the economizer 6206, respectively.

[0501] Figure 63 shows an alternative embodiment of the heat pump cycle of Figure 60. The heat pump cycle 6300 of Figure 63 comprises a heat exchanger 6301 (e.g., a two-phase heat exchanger), a first compressor 6302, a second compressor 6303, a third compressor 6305, a heat exchanger 6304 (e.g., a steam generator), a heat exchanger 6306 (e.g., a waste heat (WH) heat exchanger), and an economizer 6308. The economizer 6308 may be arranged in parallel with the WH heat exchanger 6306. The WH heat exchanger 6306 may receive working fluid output from the steam generator 6304 and inject the working fluid at a first pressure between the second compressor 6303 and the third compressor 6305. The economizer may receive the working fluid output from the steam generator 6304 and inject the working fluid at a second pressure between the first compressor 6302 and the second compressor 6303. The first pressure may be higher than the second pressure. In some embodiments, if the first pressure is lower than the second pressure, the WH exchanger 6306 injects the working fluid into the low-pressure stage (e.g., between the first compressor 6302 and the second compressor 6303), and the economizer injects the working fluid into the high-pressure stage (e.g., between the second compressor 6303 and the third compressor 6305). The WH exchanger 6306 configured as shown in Figure 63 may evaporate the working fluid at a temperature of approximately 20 to 45°C in the bottom cycle (e.g., 30°C for the economizer and 20 to 45°C for the WH heat exchanger) and / or approximately 80 to 100°C in the top cycle (e.g., approximately 100°C for the economizer and approximately 80°C for the WH heat exchanger). The WH exchanger 6306 configured as shown in Figure 63 may evaporate the working fluid at a temperature of approximately 0°C to approximately 60°C in the bottom cycle and / or approximately 60°C to approximately 130°C or approximately 90°C to approximately 100°C in the top cycle.

[0502] Figure 64 shows an alternative embodiment of the heat pump cycle in Figure 63. The heat pump cycle 6400 in Figure 64 further includes a WH heat exchanger 6401 incorporated into the cycle, similar to that in Figure 58, in addition to the heat pump cycle shown in Figure 63. The configuration of the heat pump cycle 6400 may be more thermodynamically optimal than combining the output of the WH heat exchanger and economizer with the intercooler flow. In some embodiments, the compressor of the heat pump cycle 6400 may utilize a mixed fluid flow to maintain thrust balance.

[0503] Figure 65 shows an alternative embodiment of the heat pump cycle of Figure 57. The heat pump cycle 6500 of Figure 65 incorporates all the waste heat functions of the heat pump cycles shown in Figures 57-64. This configuration maximizes the control and operating options of the cycle. In some embodiments, the heat pump cycle 6500 may further include an inlet heat exchanger 6601, as shown in the heat pump cycle 6600 of Figure 66.

[0504] In some embodiments of the heat pump cycle shown in Figures 57-66, all elements except the evaporator or steam generator, the two-phase heat exchanger, and at least one compressor are optional to the cycle.

[0505] Figure 67 shows an example of a steam generation system according to some embodiments described herein. System 6700 comprises a top cycle 6720 and a bottom cycle 6710. Both the top cycle 6720 and the bottom cycle 6710 have all the waste heat functions shown in Figure 66. System 6700 may control the functions of the waste heat functions described herein.

[0506] Figure 74 shows an example of a steam generation system according to some embodiments described herein. System 7400 comprises a top cycle 7420, a bottom cycle 7410, and a heat transfer fluid cycle 7430. The top cycle 7420 comprises a suction tube heat exchanger 7421, an economizer 7422, an economizer expansion valve 7423, and a two-phase heat exchanger 7424. The economizer 7422 may be located downstream of the suction tube heat exchanger 7421 and upstream of the two-phase heat exchanger 7424. This configuration allows the working fluid flowing into the economizer expansion valve 7423 to be cooled (for example, to below 120°C, which is a typical heat resistance temperature for commercially available expansion valves), thereby reducing the risk of damage to the economizer expansion valve 7423 due to high temperatures. In some embodiments, the economizer may cool the working fluid entering the expansion valve to below 150°C, 140°C, 130°C, 120°C, 115°C, 110°C, 105°C, 100°C, 95°C, 90°C, 85°C, 80°C, 75°C, or 70°C.

[0507] Figure 75 shows an example of a steam generation system according to some embodiments described herein. System 7500 comprises a top cycle 7520, a bottom cycle 7510, and a heat transfer fluid cycle 7530. The top cycle 7520 comprises an intake tube heat exchanger 7521, an economizer 7522, an economizer expansion valve 7523, and a two-phase heat exchanger 7524. The economizer 7522 may be located upstream of the intake tube heat exchanger 7521. The working fluid entering the economizer expansion valve 7523 may be drawn from the outlet flow of the intake tube heat exchanger 7521. This configuration may cool the working fluid entering the economizer expansion valve 7523 to about 0°C to about 10°C, about 10°C to about 20°C, about 20°C to about 30°C, about 30°C to about 40°C, and about 40°C to about 50°C. Cooling the working fluid reduces the risk of damage to the economizer expansion valve 7523 due to high temperatures.

[0508] Figure 76 shows an example of a steam generation system according to several embodiments described herein. System 7600 comprises a top cycle 7620, a bottom cycle 7610, and a heat transfer fluid cycle 7630. The bottom cycle 7610 comprises a first two-stage compressor 7611 and a second two-stage compressor 7612. The bottom cycle further comprises an economizer 7613, a first intercooler 7614, and a second intercooler 7615. The two-stage compressor comprises a first-stage compressor 76111, a second-stage compressor 76112, and a motor 76113 between the first-stage compressor 76111 and the second-stage compressor 76112. The economizer 7613 may be configured to supply fluid to the first intercooler 7614 and the second intercooler 7615. The first intercooler 7614 may be positioned between the first-stage compressor 76111 and the second-stage compressor 76112 of the second two-stage compressor 76111. The first intercooler 7614 may be configured to lower the temperature of the working fluid flow between the first-stage compressor 76111 and the second-stage compressor 76112 to about 0.1°C, 0.2°C, 0.3°C, 0.4°C, 0.5°C, 0.6°C, 0.8°C, 1°C, 1.2°C, 1.5°C, 2°C, 3°C, 4°C, 6°C, 8°C, 10°C, 12°C, 15°C, 20°C, or higher. The temperature drop of the working fluid flow between the first-stage compressor 76111 and the second-stage compressor 76112 may be between any two values ​​described herein. The second intercooler 7615 may be positioned between the first two-stage compressor 7611 and the second two-stage compressor 7612. The second intercooler 7615 may be configured to receive fluid from the economizer 7613 and / or the heat exchanger 7616. The second intercooler 7615 may be configured to lower the temperature of the working fluid flow between the first two-stage compressor 7611 and the second two-stage compressor 7612 to about 0.1°C, 0.2°C, 0.3°C, 0.4°C, 0.5°C, 0.6°C, 0.8°C, 1°C, 1.2°C, 1.5°C, 2°C, 3°C, 4°C, 6°C, 8°C, 10°C, 12°C, 15°C, 20°C, or higher. The temperature drop of the working fluid flow between the first two-stage compressor 7611 and the second two-stage compressor 7612 may be between any two values ​​described herein. During operation, the second two-stage compressor 7612 may be bypassed.In this case, the fluid from the economizer 7613 may be sent only to the first intercooler 7614. Alternatively, the first two-stage compressor 7611 and the second two-stage compressor 7612 may be operated. In this case, some or all of the fluid from the economizer 7613 may be sent to the second intercooler 7615. In alternative embodiments (not shown), more than two compressors or more than two intercoolers may be used. In alternative embodiments (not shown), multiple intercoolers may be placed in the top cycle. In alternative embodiments (not shown), intercoolers may be placed at various positions in the top cycle or bottom cycle.

[0509] Figure 77 shows another embodiment of the steam generation system of Figure 76. The steam generation system 7700 of Figure 77 comprises a top cycle 7720, a bottom cycle 7710, and a heat transfer fluid cycle 7730. The bottom cycle comprises a first economizer 7711, a second economizer 7712, a first intercooler 7713, and a second intercooler 7714. The first economizer 7711 may be configured to supply fluid to the first intercooler 7713. The second economizer 7712 may be configured to supply fluid to the second intercooler 7714. The first economizer 7711 and the second economizer 7712 are configured to operate in parallel.

[0510] Figure 78 shows an alternative embodiment of the steam generation system of Figure 76. The steam generation system 7800 of Figure 78 comprises a top cycle 7820, a bottom cycle 7810, and a heat transfer fluid cycle 7830. The bottom cycle comprises a first economizer 7811, a second economizer 7812, a first intercooler 7813, and a second intercooler 7814. The first economizer 7811 may be configured to supply fluid to the first intercooler 7813. The second economizer 7812 may be configured to supply fluid to the second intercooler 7814. The first economizer 7811 and the second economizer 7812 are configured to operate in series.

[0511] Figure 79 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 7900 in Figure 79 comprises a top cycle 7920, a bottom cycle 7910, and a heat transfer fluid cycle 7930. The bottom cycle 7910 comprises a heat exchanger 7911, a flash tank economizer 7912, an intercooler 7913, and a two-stage compressor 7914. The two-stage compressor comprises a first-stage compressor 7915, a second-stage compressor 7916, and a motor 7917 between the first-stage compressor 7915 and the second-stage compressor 7916. The intercooler is configured to receive steam flow from the flash tank economizer 7912 and the first-stage compressor 7915. The intercooler 7913 may be located between the first-stage compressor 7915 and the second-stage compressor 7916. The second-stage compressor is configured to receive fluid from the intercooler 7913. The intercooler 7913 may be configured to lower the temperature of the working fluid flow between the first-stage compressor 7915 and the second-stage compressor 7616 to about 0.1°C, 0.2°C, 0.3°C, 0.4°C, 0.5°C, 0.6°C, 0.8°C, 1°C, 1.2°C, 1.5°C, 2°C, 3°C, 4°C, 6°C, 8°C, 10°C, 12°C, 15°C, 20°C, or higher. The temperature drop of the working fluid flow between the first-stage compressor 7915 and the second-stage compressor 7616 may be between any two values ​​described herein. The top heat pump cycle 7920 comprises a flash tank economizer 7921, an intercooler 7922, a first two-stage compressor 7923, and a second two-stage compressor 7924. The intercooler 7922 is configured to receive a vapor flow from the flash tank economizer 7921. The intercooler 7922 may be positioned between the first two-stage compressor 7923 and the second two-stage compressor 7924. The intercooler 7922 may be configured to lower the temperature of the working fluid flow between the first two-stage compressor 7923 and the second two-stage compressor 7924 by about 0.1°C, 0.2°C, 0.3°C, 0.4°C, 0.5°C, 0.6°C, 0.8°C, 1°C, 1.2°C, 1.5°C, 2°C, 3°C, 4°C, 6°C, 8°C, 10°C, 12°C, 15°C, 20°C, or more. The temperature drop of the working fluid flow between the first two-stage compressor 7923 and the second two-stage compressor 7924 may be between any two values ​​described herein.The second two-stage compressor 7924 is configured to receive fluid from the intercooler 7922.

[0512] Figure 95 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 9500 in Figure 95 comprises a bottom cycle 9510 and a heat transfer fluid cycle 9530. The bottom cycle 9510 may comprise a first compressor 9511, a second compressor 9512, a flash tank 9513, and an economizer 9514. The flash tank 9513 may be configured to receive the working fluid flow of the output flow from the first compressor 9511 and the economizer 9514. The flash tank 9513 may be configured to contain saturated liquid at the bottom of the tank and evaporating fluid at the top of the tank. The saturated liquid may be sent to an expansion valve 9515 and then to a cryogenic evaporator 9516. The expansion valve 9515 and the cryogenic evaporator 9516 reduce the pressure of the saturated liquid, which may absorb heat from an external heat source and evaporate. The evaporated fluid discharged from the evaporator 9516 may flow into the first compressor 9511. The evaporated fluid in the flash tank 9513 may be sent to the second compressor 9512. Placing the flash tank 9513 between the two compressors reduces overheating at the intake of the second compressor 9512 or reduces the volumetric flow rate of the first compressor 9511. This configuration allows more flow to be sent to the second compressor 9512. The first compressor 9511 may be bypassed using a bypass valve 9517. Valve 9517 may be used in the line discharged from the top of the flash tank 9513. Closing valve 9517 allows the entire flow to pass through the evaporator 9516 (for example, when the first compressor 9511 is bypassed). Valve 9518 may be used in the outlet working fluid flow of the economizer 9514. Valve 9518 may be closed when the ambient temperature is high.

[0513] Figure 80 shows an example of a steam generation system according to some embodiments described herein. The steam generation system 8000 in Figure 80 comprises a top cycle 8020 and a bottom cycle 8010. The top cycle 8020 comprises an intake tube heat exchanger 8021, a two-phase heat exchanger 8022, a two-phase ejector 8023, an expansion valve 8024, and a separator 8025. The bottom cycle 8010 comprises an economizer 8011, an evaporator 8012, a two-phase ejector 8013, an expansion valve 8014, a separator 8015, and a two-stage compressor 8016. The two-phase ejectors 8023 and 8013 may be configured to recover energy in the throttling process of the refrigerant flow. The two-phase ejectors 8023 and 8013 may also be configured to allow the refrigerant to flow into the two-phase heat exchanger 8022 or the evaporator 8012 as a low-quality steam or saturated liquid, thereby increasing the heat absorption capacity. The steam quality flowing into the two-phase heat exchanger 8022 may be approximately 0%, 5%, 10%, 15%, 20%, 25%, 30%, 40%, or 50% or more. The steam quality flowing into the two-phase heat exchanger 8022 may be between any two values ​​described herein. The two-phase ejectors 8023 and 8013 may be configured to function as thermocompressors, thereby increasing the suction pressure of the compressor and reducing the workload of the compressor. The pressure ratio between the pressure in the separator and the pressure downstream of the downstream heat exchanger may be approximately 1, 1.2, 1.4, 1.5, 1.6, 1.8, 2.0, 2.5, 3.0, 3.5, 4.0, 4.5, or 5.0 or more. The pressure ratio between the pressure in the separator and the pressure in the downstream heat exchanger may be between any two values ​​described herein.

[0514] Figures 82-85 show examples of steam generation systems according to some embodiments described herein. The steam generation system 8200 in Figure 82 comprises a top cycle 8220 and a bottom cycle 8210. The bottom cycle 8210 and top cycle 8220 comprise a two-phase heat exchanger 8211 and a supercooler 8212. The top cycle 8220 further comprises an expansion valve 8221 and a top cycle liquid line 8222. The working fluid from the top cycle is drawn into the supercooler 8212 from the bottom of the two-phase heat exchanger 8211. The supercooler 8212 may be configured to transfer heat from the working fluid from the bottom cycle to the working fluid from the top cycle. The supercooler 8212 can operate as a thermosiphon (e.g., passively cooling the working fluid of the bottom cycle without requiring additional valves or pumps). The supercooler 8212 may be located at the same position as the two-phase heat exchanger 8211 or below it. An advantage of positioning the subcooler 8212 at the same location as, or below, the two-phase heat exchanger 8211 is that it can generate a pressure difference (e.g., both density difference and hydrostatic pressure difference) between the two-phase heat exchanger and the connecting piping, thereby ensuring sufficient flow rate in the top cycle portion of the subcooler. The working fluid evaporates and is pushed upward, joining with the outlet of the expansion valve 8221 or being injected directly into the two-phase heat exchanger 8211.

[0515] Figure 83 shows an alternative embodiment of the steam generation system of Figure 82. The steam generation system 8300 of Figure 83 comprises a top cycle 8320 and a bottom cycle 8310. The top cycle 8320 comprises a top cycle liquid line 8321, a first expansion valve 8322, a second expansion valve 8323, a two-phase heat exchanger 8324, and a subcooler 8325. The top cycle liquid line 8321 enters the first expansion valve 8322, then the two-phase heat exchanger 8324, or the second expansion valve 8323, then the subcooler 8325. The working fluid output from the subcooler enters the outlet flow of the first expansion valve 8322. The second expansion valve 8323 may be configured to control the flow rate entering the subcooler 8325.

[0516] Figure 84 shows an alternative embodiment of the steam generation system in Figure 82. The steam generation system 8400 in Figure 84 comprises a top cycle 8420 and a bottom cycle 8410. The top cycle 8420 comprises a top cycle liquid line 8421, an expansion valve 8422, a flow limiter 8423, a two-phase heat exchanger 8324, and a subcooler 8325. The top cycle liquid line 8421 enters the expansion valve 8422. The working fluid output of the expansion valve 8422 enters the flow limiter 8423 and the subcooler 8425. The working fluid output of the subcooler 8425 enters the working fluid output of the flow limiter 8423, and then enters the two-phase heat exchanger 8424. The flow limiter 8423 may be configured to reduce the flow rate entering the subcooler 8425. The flow rate flowing into the subcooler may be about 0%, 2%, 5%, 10%, or 20% or less of the total flow rate. The flow rate into the subcooler may be approximately 0%, 2%, 5%, 10%, or 20% or more of the total flow rate. A. The flow rate into the subcooler may be between any two values ​​described herein, for example, between 0% and 20%.

[0517] Figure 85 shows an alternative embodiment of the steam generation system of Figure 82. The steam generation system 8500 of Figure 85 comprises a top cycle 8520, a bottom cycle 8510, and a glycol loop 8530. The bottom cycle 8510 and the glycol loop 8530 are equipped with a supercooler 8511. The supercooler 8511 may be configured to transfer heat from a first working fluid from the bottom cycle 8510 to a second working fluid from the glycol loop 8530.

[0518] Figures 86-87 show examples of steam generation systems according to some embodiments described herein. The steam generation system 8600 in Figure 86 comprises a plurality of heat pumps 8601 and a heat transfer fluid cycle 8610. The plurality of heat pump cycles 8601 may be coupled to the same heat transfer fluid cycle 8610. The heat transfer fluid cycle 8610 may be a glycol loop. The heat transfer cycle may include one or more air source heat exchangers 8611. One or more air source heat ...

Claims

1. a. The first heat transfer fluid is circulated through an intermediate loop comprising (i) a first heat exchanger that receives the first heat transfer fluid and ambient airflow and transfers heat from the ambient airflow to the first heat transfer fluid, and (ii) a second heat exchanger that receives the heat transfer fluid and the first working fluid and transfers heat from the first heat transfer fluid to the first working fluid. b. Circulating the first working fluid through a first heat pump cycle comprising (i) a second heat exchanger and (ii) a third heat exchanger that receives the first working fluid and the second working fluid and transfers heat from the first working fluid to the second working fluid, c. (i) Circulating the second working fluid through a second heat pump cycle comprising a third heat exchanger and (ii) a steam generator, d. Supplying a water-containing supply stream to a steam generator that generates steam by transferring heat from a second working fluid to the supply stream, A method for generating water vapor, comprising the following characteristics.

2. The process further includes transferring heat from a heat source subunit to an intermediate loop via a heat exchanger, wherein the heat source subunit is coupled to the intermediate loop. The method according to claim 1.

3. The heat source subunit is (i) a refrigeration system, (ii) a geothermal source, (iii) waste heat flow from a process, wastewater or waste heat flow from a heat system, power system, or combined heat and power system, (iv) a carbon capture process, (v) a body of water, (vi) a regional energy system, (vii) a solar thermal source, or (viiii) a nuclear reactor. The method according to claim 2.

4. The body of water is either a lake or a river. The method according to claim 3.

5. The carbon capture process is a direct air capture system. The method according to claim 3.

6. The intermediate loop subunit heat exchanger receives the subunit fluid and the first heat transfer fluid, and transfers heat from the subunit fluid to the first heat transfer fluid. The method according to claim 2.

7. The subunit heat exchanger condenses at least a portion of the subunit fluid. The method according to claim 6.

8. The process involves transferring heat from the subunit fluid of the heat source subunit to the second heat transfer fluid, and then transferring heat from the second heat transfer fluid to the intermediate loop. The method according to claim 2, further comprising:

9. The first heat transfer fluid supplies cooling directly to the heat source subunit. The method according to claim 2.

10. The first heat transfer fluid is a water flow or a water tank that directly cools. The method according to claim 1.

11. The method further includes guiding a fluid airflow to an additional heat exchanger in an intermediate loop, and transferring heat from the ambient air to the first heat transfer fluid via the additional heat exchanger, wherein the additional heat exchanger is arranged in parallel with the first heat exchanger. The method according to claim 1.

12. The method further includes guiding a fluid airflow to an additional heat exchanger in an intermediate loop, and transferring heat from the ambient air to the first heat transfer fluid via the additional heat exchanger, the additional heat exchanger being arranged in series with the first heat exchanger. The method according to claim 1.

13. The process further includes transferring heat from the vapor compression system to a heat transfer fluid, and the intermediate loop is coupled to the vapor compression system. The method according to claim 1.

14. The first heat exchanger is located within the cycle of the vapor compression system. The method according to claim 13.

15. The vapor compression fluid of the vapor compression system is ammonia (NH 6 ), water (H 2 O), carbon dioxide (CO 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC(CH 3 )) 3 ), propane (C 3 H 8 ), or propene (C 3 H 6 ), and includes one or more of The method according to claim 13.

16. The intermediate loop is connected to the vapor compression system using a condenser and evaporator. The method according to claim 13.

17. The intermediate loop further comprises a heat recovery heat exchanger, which enables at least one of (i) operation at very low ambient temperatures, or (ii) sizing the vapor compressor cycle to a lower capacity. The method according to claim 16.

18. The intermediate loop further comprises a fourth heat exchanger that receives a first heat transfer fluid and a third working fluid, and transfers heat from the first heat transfer fluid to the third working fluid. The method according to claim 1.

19. a. (i) Circulating the third working fluid via a third heat pump cycle comprising a fourth heat exchanger and (ii) a fifth heat exchanger that receives the third working fluid and the fourth working fluid and transfers heat from the third working fluid to the fourth working fluid, b. The fourth working fluid is circulated through a fourth heat pump cycle comprising (i) a fifth heat exchanger and (ii) a second steam generator, c. Supplying a second supply stream containing water to a second steam generator that generates steam by transferring heat from a fourth working fluid to a supply stream, The method according to claim 18, further comprising:

20. The second and fourth heat exchangers are configured in parallel. The method according to claim 19.

21. The second and fourth heat exchangers are configured in series. The method according to claim 19.

22. The vapor compression system uses air as its source. The method according to claim 13.

23. The vapor compression fluid of the vapor compression system includes one or more hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants. The method according to claim 13.

24. The first heat exchanger (i) transfers heat to the first heat transfer fluid when the refrigeration load is low or zero or the steam load is high, or (ii) transfers heat from the first heat transfer fluid when the refrigeration load is high or the heat pump load is low or zero. The method according to claim 1.

25. Compressing water vapor using a steam compressor. The method according to claim 1, further comprising:

26. a. Using the fluid from the steam generator to fill the storage tank, b. Discharging the fluid from the storage tank as water vapor, The method according to claim 1, further comprising:

27. To isolate a storage tank by closing one or more valves, thereby preventing filling and discharging. The method according to claim 26, further comprising:

28. An intermediate loop comprising a first heat exchanger and a second heat exchanger, wherein the intermediate loop is configured to circulate a first heat transfer fluid, and the first heat exchanger is configured to receive ambient airflow and the first heat transfer fluid and transfer heat from the ambient airflow to the first heat transfer fluid, A first heat pump cycle configured to circulate a first working fluid between a second heat exchanger and a third heat exchanger, wherein the second heat exchanger is configured to receive a first heat transfer fluid and a first working fluid and to transfer heat from the first heat transfer fluid to the first working fluid, and the third heat exchanger is configured to receive a first working fluid and a second working fluid and to transfer heat from the first working fluid to the second working fluid, A second heat pump cycle configured to circulate a second working fluid between a third heat exchanger and a fourth heat exchanger, wherein the fourth heat exchanger is configured to receive the second working fluid and a supply stream, the supply stream containing water, and the first heat exchanger is isolated from the first and second heat pump cycles. A system that generates water vapor and is equipped with the following features.

29. The system further comprises a heat source subunit, the heat source subunit having at least one component connected to an intermediate loop. The system according to claim 28.

30. The heat source subunit is a refrigeration system, geothermal source, waste heat flow from a process, or wastewater or waste heat flow from a heat system, power system, or combined heat and power system. The system according to claim 29.

31. The heat source subunit includes a subunit fluid, and the intermediate loop includes a subunit heat exchanger configured to receive the subunit fluid and a first heat transfer fluid and transfer heat from the subunit fluid to the first heat transfer fluid. The system according to claim 29.

32. At least a portion of the subunit fluid is condensed by the subunit heat exchanger. The system according to claim 31.

33. It further includes a heat source subunit, which contains a condenser, and the condenser is disconnected from the intermediate loop. The system according to claim 28.

34. The condenser is configured to transfer heat from the subunit fluid of the subunit to a second heat transfer fluid, and the second heat transfer fluid supplies heat to the intermediate loop. The system according to claim 33.

35. The first heat transfer fluid supplies cooling directly to the heat source subunit. The system according to claim 29.

36. The first heat transfer fluid is a water flow or a water tank that directly cools. The system according to claim 29.

37. The intermediate loop includes an additional heat exchanger positioned in parallel with the first heat exchanger, which receives ambient air and transfers heat from the ambient air to the first heat transfer fluid. The system according to claim 28.

38. The intermediate loop includes an additional heat exchanger positioned in series with the first heat exchanger, which receives ambient air and transfers heat from the ambient air to the first heat transfer fluid. The system according to claim 28.

39. The intermediate loop is coupled to the vapor compression system, which supplies heat to the heat transfer fluid. The system according to claim 28.

40. The first heat exchanger is located within the cycle of the vapor compression system. The system according to claim 39.

41. The vapor-compressed fluid in a vapor compression system is ammonia (NH₃). 3 ), water (H 2 O), carbon dioxide (CO2) 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC (CH 3 ) 3 ), propane (C 3 H 8 ), or propene (C 3 H 6 ) including one or more of the following: The system according to claim 39.

42. The intermediate loop is equipped with an integrated steam compression system. The system according to claim 28.

43. The integrated steam compression system includes a compressor, which is a positive displacement compressor. The system according to claim 42.

44. The positive displacement compressor is a screw compressor, a scroll compressor, or a reciprocating compressor, according to claim 43.

45. The positive displacement compressor is a screw compressor, according to claim 43.

46. The system further comprises one or more centrifugal compressors (or groups thereof), The system according to claim 28.

47. One or more centrifugal compressors (groups) are one or more oil-free centrifugal compressors (groups). The system according to claim 46.

48. The supply stream contains water, and the fourth heat exchanger is configured to heat the supply stream without changing the phase of the water in the supply stream. The system according to claim 28.

49. Further comprising a flash tank downstream of the fourth heat exchanger configured to receive at least water from the supply stream from the fourth heat exchanger, The system according to claim 48.

50. The flash tank is configured to reduce the pressure of at least the water in the supply stream to generate steam. The system according to claim 49.

51. The outlet of the fourth heat exchanger is water vapor, and the temperature of the surrounding airflow is below -20°C. The system according to claim 28.

52. It is configured to generate water vapor at the outlet of the fourth heat exchanger when the ambient airflow temperature is below -40°C. The system according to claim 28.

53. Further comprising at least two flash tanks downstream of the fourth heat exchanger, the at least two flash tanks are configured to receive at least water from the supply stream from the fourth heat exchanger. The system according to claim 48.

54. The intermediate loop further includes a fifth heat exchanger. The system further, A third heat pump cycle configured to circulate a third working fluid between a fifth heat exchanger and a sixth heat exchanger, wherein the fifth heat exchanger is configured to receive a first heat transfer fluid and a third working fluid and transfer heat from the first heat transfer fluid to the third working fluid, and the sixth heat exchanger is configured to receive a third working fluid and a fourth working fluid and transfer heat from the fourth working fluid to the fifth working fluid, A fourth heat pump cycle configured to circulate a fourth working fluid between a sixth heat exchanger and a seventh heat exchanger, wherein the seventh heat exchanger receives the fourth working fluid and a second supply stream, the second supply stream containing water, and the first heat exchanger is disconnected from the third and fourth heat pump cycles. The system according to claim 28, comprising:

55. The second and fifth heat exchangers are configured to be arranged in parallel. The system according to claim 54.

56. The second and fifth heat exchangers are configured to be arranged in series. The system according to claim 54.

57. Furthermore, a supercooler is provided, which is located downstream of the third or fourth heat exchanger. The system according to claim 28.

58. The supercooler is positioned at the same height as or lower than the third or fourth heat exchanger. The system according to claim 57.

59. The saturated or supercooled liquid from the top cycle is drawn from the bottom of the third or fourth heat exchanger and coupled to the supercooler. The system according to claim 57.

60. The saturated or supercooled liquid absorbs heat from the bottom cycle, evaporates and moves upward, and is either (i) coupled at the expansion valve outlet or (ii) directly injected into the third or fourth heat exchanger. The system according to claim 59.

61. The fluid flow of the top cycle entering the supercooler is controlled by a valve located upstream of the supercooler. The system according to claim 57.

62. The fluid flow of the top cycle entering the supercooler is controlled by a flow limiter, which is located on the bypass stream upstream of the supercooler. The system according to claim 57.

63. The supercooler uses glycol to cool the bottom cycle fluid, and glycol is used for defrosting the heat exchanger. The system according to claim 57.

64. Furthermore, it is equipped with a heat storage system. The system according to claim 28.

65. The heat storage system includes a phase change material, which is (i) incorporated into a heat exchanger or (ii) provided outside the heat exchanger, and the phase change material is further configured to use the latent heat of the phase change to store and release the stored energy. The system according to claim 28.

66. a. The first working fluid is circulated through a refrigeration cycle that receives the first working fluid and the cooled fluid and transfers heat from the cooled fluid to the first working fluid, b. The heat pump cycle comprises (i) a second heat exchanger that receives a first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid, and (ii) a steam generator that receives the second working fluid and a supply stream and transfers heat from the second working fluid to the supply stream to generate a saturated steam flow, wherein the supply stream contains water. A method for generating water vapor.

67. The first working fluid in the refrigeration cycle is ammonia (NH₄). 3 ), water (H 2 O), carbon dioxide (CO2) 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC (CH 3 ) 3 ), propane (C 3 H 8 ), or propene (C 3 H 6 ) including one or more of the following: The method according to claim 66.

68. The refrigeration cycle includes a positive displacement compressor or a centrifugal compressor. The method according to claim 66.

69. Positive displacement compressors include screw compressors, scroll compressors, and reciprocating compressors. The method according to claim 68.

70. Positive displacement compressors or centrifugal compressors are oil-free compressors. The method according to claim 68.

71. The refrigeration cycle includes a third heat exchanger, which transfers heat from the first working fluid to the ambient airflow. The method according to claim 66.

72. The maximum temperature of the first working fluid during operation is 100°C or less. The method according to claim 66.

73. The first working fluid of the refrigeration cycle includes one or more hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants. The method according to claim 66.

74. A refrigeration cycle configured to circulate a first working fluid, comprising a first heat exchanger configured to receive the first working fluid and a cooled fluid and to transfer heat from the cooled fluid to the first working fluid, A heat pump cycle configured to circulate a second working fluid, comprising (i) a second heat exchanger, and (ii) a steam generator configured to receive the second working fluid and a supply stream and transfer heat from the second working fluid to the supply stream to generate a saturated steam flow, wherein the supply stream contains water. A system that generates water vapor and is equipped with the following features.

75. The first working fluid in a refrigeration cycle or the second working fluid in a heat pump cycle is ammonia (NH₃). 3 ), water (H 2 O), carbon dioxide (CO2) 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC (CH 3 ) 3 ), propane (C 3 H 8 ), propene (C 3 H 6 ), comprising one or more hydrocarbon fluids, hydrofluoroolefin (HFO) fluids, and hydrofluorochlorine (HFC) fluids, hydrochlorofluoroolefin (HCFO) fluids, or natural refrigerants, The system according to claim 74.

76. The refrigeration cycle includes a positive displacement compressor or a centrifugal compressor. The system according to claim 74.

77. The positive displacement compressor in a refrigeration cycle is a screw compressor. The system according to claim 76.

78. The refrigeration cycle further includes at least one of a cryogenic evaporator, an air-cooled condenser, or a heat exchanger, coupled to a water loop including a condenser. The system according to claim 74.

79. The heat pump cycle further comprises at least one of an economizer, a compressor, an intercooler, or an intake tube heat exchanger. The system according to claim 74.

80. The maximum temperature of the first working fluid in the refrigeration cycle is 100°C or lower. The system according to claim 74.

81. a. Circulating a first working fluid, which is in a subcritical state in at least a portion of the first heat pump cycle, through the first heat pump cycle, b. Circulating a second working fluid through a second heat pump cycle, wherein the second heat pump cycle includes a first steam generator, the second working fluid is subcritical in at least part of the second heat pump cycle, the first working fluid is supercritical in at least part of the first heat pump cycle, the second working fluid is supercritical in at least part of the second heat pump system, or the first and second working fluids are supercritical in at least part of the first and second heat pump cycles. c. To provide a heat exchanger for receiving a first working fluid and a second working fluid and transferring heat from the first working fluid to the second working fluid. A method for generating water vapor, comprising the following characteristics.

82. The first working fluid is ammonia (NH 3 ), water (H 2 O), carbon dioxide (CO2) 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC (CH 3 ) 3 ), propane (C 3 H 8 ), or propene (C 3 H 6 ) including one or more of the following: The method according to claim 81.

83. The second working fluid is ammonia (NH 3 ), water (H 2 O), carbon dioxide (CO2) 2 ), pentane (C 5 H 12 ), butane (C 4 H 10 ), isobutane (HC (CH 3 ) 3 ), propane (C 3 H 8 ), or propene (C 3 H 6 ) including one or more of the following: The method according to claim 81.

84. The first working fluid or the second working fluid includes one or more of the following: hydrocarbon fluid, hydrofluoroolefin (HFO) fluid, hydrofluorochlorine (HFC) fluid, hydrochlorofluoroolefin (HCFO) fluid, or natural refrigerant. The method according to claim 81.

85. The first heat pump cycle moves air from the ambient airflow to the first working fluid. The method according to claim 81.

86. At least one of the first or second heat pump cycle includes an oil-free compressor. The method according to claim 81.

87. An oil-free compressor is either a positive displacement compressor or a centrifugal compressor. The method according to claim 86.

88. The second heat pump cycle includes a second steam generator. The method according to claim 81.

89. Either the first heat pump cycle or the second heat pump cycle further comprises an economizer, an intercooler, an intake tube heat exchanger, or at least two condensers thereof. The method according to claim 81.

90. A first heat pump cycle configured to circulate a first working fluid, wherein the first working fluid is in a subcritical state in at least a portion of the first heat pump cycle, A second heat pump cycle comprising a first steam generator, wherein the second heat pump cycle is configured to circulate a second working fluid, the second working fluid being subcritical in at least a portion of the second heat pump cycle, the first working fluid being supercritical in at least a portion of the first heat pump, the second working fluid being supercritical in at least a portion of the second heat pump system, or the first and second working fluids being supercritical in at least a portion of the first and second heat pump cycles, and the first steam generator is configured to (i) receive a supply stream containing the second working fluid and water from a first compressor, and (ii) transfer heat from the second working fluid to the supply stream to produce steam or hot water, A first heat exchanger configured to receive a first working fluid and a second working fluid and to transfer heat from the first working fluid to the second working fluid, A system that generates steam or hot water, comprising the following features.

91. The system further comprises a second steam generator arranged in parallel with the first steam generator, the second steam generator (i) receiving a second supercritical fluid flow and water flow from the first compressor, and (ii) generating saturated steam. The system according to claim 90.

92. The system further comprises a first compressor and a second compressor arranged in series with the first steam generator, wherein the first steam generator sends a first supercritical fluid to the second compressor, and the second compressor sends a second supercritical fluid flow to either the first or second steam generator. The system according to claim 90.

93. The first and second steam generators produce steam at different temperatures. The system according to claim 92.

94. The portion of the second heat pump cycle in which the second working fluid is supercritical includes at least a portion of the second working fluid in the steam generator. The system according to claim 90.

95. a. Circulating the first working fluid through the first heat pump cycle, b. Circulating the second working fluid through the second heat pump cycle, c. To provide a first heat exchanger that receives a first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid, d. A first evaporator that receives ambient airflow and either the first working fluid or the second working fluid and transfers heat from the ambient airflow to either the first working fluid or the second working fluid, and a supply of ambient airflow, e. To provide a second evaporator that receives either the first working fluid or the second working fluid and transfers heat from a heat source to either the first working fluid or the second working fluid, and an external heat source, A method for generating water vapor, comprising the following characteristics.

96. External heat sources include (i) refrigeration cycles, (ii) geothermal sources, (iii) waste heat sources from processes, heat systems, power systems, or wastewater or waste heat flows from combined heat and power systems, (iv) carbon capture processes, (v) bodies of water, (vi) regional energy systems, (vii) solar thermal sources, or (viiii) nuclear reactors. The method according to claim 95.

97. The body of water is either a lake or a river. The method according to claim 96.

98. The carbon capture process is a direct air capture system. The method according to claim 96.

99. The inlet temperature of the first evaporator is lower than the inlet temperature of the second evaporator. The method according to claim 95.

100. At least 500 kg / hour of steam is generated. The method according to claim 95.

101. A first heat pump cycle configured to circulate a first working fluid, A second heat pump cycle comprising at least one compressor, at least one expansion valve, and a first steam generator, configured to circulate a second working fluid, A first heat exchanger configured to receive a first working fluid and a second working fluid and to transfer heat from the first working fluid to the second working fluid, A first evaporator configured to receive ambient airflow and a first working fluid or a second working fluid and to transfer heat from the ambient airflow to the first working fluid or the second working fluid, A second evaporator configured to transfer heat from a heat source to a first working fluid or a second working fluid, A system that generates water vapor and is equipped with the following features.

102. The second evaporator is coupled to (i) a connected or disconnected refrigeration cycle, (ii) a geothermal source, or (iii) a waste heat source from a process, (iv) a carbon capture process, (v) a body of water, (vi) a regional energy system, (vii) a solar heat source, or (viiii) a nuclear reactor. The system according to claim 101.

103. The body of water is either a lake or a river. The system according to claim 102.

104. The carbon capture process is a direct air capture system. The system according to claim 102.

105. The second evaporator is arranged in parallel with the first evaporator. The system according to claim 101.

106. At least one of the first evaporator or the second evaporator is intermittently bypassed. The system according to claim 101.

107. The first evaporator and the second evaporator are located within the first heat pump cycle. The system according to claim 101.

108. The first evaporator and the second evaporator are located within the second heat pump cycle. The system according to claim 101.

109. One of the first and second evaporators is located within the first heat pump cycle, and the other of the first and second evaporators is located within the second heat pump cycle. The system according to claim 101.

110. The first heat pump cycle comprises at least a first compressor and a second compressor, and the second evaporator is arranged in series with the second compressor and in parallel with the first compressor. The system according to claim 101.

111. The second heat pump cycle comprises at least a first compressor and a second compressor, the second evaporator being arranged in series with the second compressor and in parallel with the first compressor. The system according to claim 101.

112. a. Circulating the first working fluid through the first heat pump cycle, b. Circulating the second working fluid through a second heat pump cycle equipped with a first steam generator, c. To provide a first heat exchanger that receives a first working fluid and an ambient airflow and transfers heat from the ambient airflow to the first working fluid, d. To provide a second heat exchanger that receives a first working fluid and a second working fluid and transfers heat from the first working fluid to the second working fluid, e. Supplying a first supply stream containing water to a first steam generator, transferring heat from the second working fluid to the first supply stream to generate steam, f. A second supply stream containing water is supplied to the third heat exchanger to transfer heat from the second working fluid to the second supply stream, A method for generating water vapor, comprising the following characteristics.

113. A first heat pump cycle configured to circulate a first working fluid, A second heat pump cycle including a first steam generator, the second heat pump cycle configured to circulate a second working fluid, and the first steam generator configured to receive a first water flow and a second working fluid, and to transfer heat from the second working fluid to the first water flow to generate steam, and A first heat exchanger configured to receive a first working fluid and a second working fluid and to transfer heat from the first working fluid to the second working fluid, (i) a second heat exchanger configured to receive a first working fluid and ambient airflow, and (ii) to transfer heat from the ambient airflow to the first working fluid, A third heat exchanger configured to receive a second water flow and at least one of the first working fluid and the second working fluid, and to transfer heat from either the first working fluid or the second working fluid to the second water flow, A system that generates water vapor and is equipped with the following features.

114. The third heat exchanger and the first heat exchanger are arranged in parallel in the first heat pump cycle. The system according to claim 113.

115. The third heat exchanger is located within the second heat pump cycle. The system according to claim 113.

116. The process involves circulating the working fluid through a heat pump cycle that includes a compressor, The process involves transferring heat from the working fluid to a water-containing supply stream to generate an outlet stream containing water vapor, A method for generating water vapor, comprising the following characteristics.

117. A heat pump cycle includes one or more oil-free compressors(groups), The method according to claim 116.

118. The water vapor temperature in the outlet stream is at least 120°C. The method according to claim 116.

119. The invention further includes supplying a thermally coupled ambient airflow to a heat pump cycle to transfer heat from the ambient airflow to the working fluid. The method according to claim 116.

120. The compressor has bearings that are lubricated with liquid refrigerant. The method according to claim 116.

121. The compressor is equipped with at least one jet for supplying liquid refrigerant to the bearings. The method according to claim 120.

122. The compressor has at least two jets for supplying liquid refrigerant to the bearings. The method according to claim 120.

123. The compressor is of the double-ended type. The method according to claim 116.

124. The compressor has a preload spring between the mount housing the bearing and the compressor chassis. The method according to claim 120.

125. The bearings include nitrogen-treated stainless steel. The method according to claim 120.

126. a. Transferring heat from the ambient air to the heat pump cycle using one or more heat exchangers (groups), b. Defrost at least one of one or more heat exchangers (or groups thereof). The method according to claim 116, further comprising:

127. One or more heat exchangers (or groups thereof) are defrosted by electric resistance heaters embedded in or on one or more coils of the heat exchanger. The method according to claim 126.

128. One or more heat exchangers (or groups thereof) are defrosted by heating the surrounding air with an electric resistance heater before heat transfer by the heat transfer fluid. The method according to claim 126.

129. One or more heat exchangers (or groups thereof) are defrosted by thermal coupling with the high-temperature gas bypass from the compressor discharge pipe. The method according to claim 126.

130. One or more heat exchangers (or groups thereof) are defrosted by heating an intermediate fluid and circulating the intermediate fluid, which has been in thermal contact with one or more heat exchangers. The method according to claim 126.

131. One or more heat exchangers (or groups thereof) are defrosted by introducing a fluid flow containing water or steam onto the surface of one or more heat exchangers. The method according to claim 126.

132. One or more heat exchangers (groups) are defrosted sequentially or simultaneously. The method according to claim 126.

133. The method according to claim 116, wherein the heat pump cycle further includes an oil loop for lubricating one or more ball bearings in the compressor.

134. The compressor has one or more magnetic coils at the end of the shaft to balance the thrust. The method according to claim 116.

135. The compressor is cooled by a motor coolant flow, and the motor coolant flow contains a refrigerant. The method according to claim 116.

136. The motor coolant flow is cooled by (i) a glycol cooler, (ii) an air cooler, or (iii) a vapor compression cycle. The method according to claim 135.

137. The compressor is cooled by a water flow. The method according to claim 116.

138. The compressor is cooled by injecting a portion of the working fluid between the compressor stages, and a portion of the working fluid is cooled in an economizer before injection. The method according to claim 116.

139. The compressor is equipped with one or more shaft seals. The method according to claim 116.

140. The compressor is equipped with one or more guide vanes. The method according to claim 116.

141. The compressor has one or more collectors. The method according to claim 116.

142. The compressor is equipped with a diffuser. The method according to claim 116.

143. The compressor is equipped with a shroud. The method according to claim 116.

144. The system further includes cooling the space with air from a heat pump system, and the heat pump system comprises a heat pump cycle. The method according to claim 116.

145. After cooling the space, it further includes transferring heat from the air to the heat pump system. The method according to claim 144.

146. a. A first system, equipped with a heat transfer fluid cycle, which transfers heat from the ambient airflow to the heat transfer fluid, is installed in an outdoor space. b. A second system is provided in the indoor space, comprising at least one heat pump cycle, which receives a heat transfer fluid and transfers heat to a water-containing supply stream to generate steam. A method for generating water vapor, comprising the following characteristics.

147. The heat transfer fluid is the refrigerant fluid. The method according to claim 146.

148. The refrigerant fluid contains one or more of water or glycol. The method according to claim 147.

149. The second system comprises at least two heat pump cycles coupled together. The method according to claim 146.

150. Steam is generated as an outlet stream from a heat exchanger coupled to at least one heat pump cycle, and the heat exchanger is configured to accept a supply stream containing water. The method according to claim 146.

151. The method further includes reducing the pressure of a pressurized flow containing water in a flash tank to generate steam, wherein the flash tank is located in or coupled to a second heat pump system and receives a fluid flow containing water from a heat exchanger of the second heat pump system. The method according to claim 146.

152. The heat exchanger of the first heat pump system, which is configured to accept ambient air, is defrosted. The method according to claim 146.

153. The heat exchanger is defrosted by an electric resistance heater embedded in or on one or more coils of the heat exchanger. The method according to claim 152.

154. The heat exchanger is defrosted by heating the surrounding air using an electric resistance heater before heat transfer with the heat transfer fluid. The method according to claim 152.

155. The heat exchanger is defrosted by thermal coupling with the high-temperature gas bypass from the compressor's discharge pipe. The method according to claim 152.

156. Heat exchangers are defrosted by heating the intermediate fluid and circulating it through thermal contact with the heat exchanger. The method according to claim 152.

157. Heat exchangers are defrosted by introducing a fluid flow containing water or steam onto the surface of the heat exchanger. The method according to claim 152.

158. The process further includes transferring heat from a heat transfer fluid to a working fluid, and the heat transfer loop includes the heat transfer fluid. The method according to claim 116.

159. The heat transfer loop is an intermediate heat transfer loop located between the heat pump and the second heat pump. The method according to claim 158.

160. This further includes delivering a heat transfer fluid to the end user, where the heat transfer fluid is hot water. The method according to claim 158.

161. A coolant fluid is supplied to a cavity that is in thermal contact with at least one of the shaft or rotor, and the coolant fluid at least partially evaporates within the cavity, cooling at least one of the shaft or rotor of the oil-free compressor so that the temperature of the rotor is maintained below the temperature threshold for demagnetization of the permanent magnets in the rotor. A method for cooling at least one of the shaft or rotor of an oil-free compressor, comprising:

162. The demagnetization temperature threshold is 150°C or lower. The method according to claim 158.

163. The compressor compresses a fluid stream containing water or steam to produce an outlet stream containing steam with a temperature of 120°C or higher. The method according to claim 158.

164. The compressor compresses the fluid to produce an outlet stream containing gas with a temperature of 80°C or higher. The method according to claim 158.

165. a. To provide a carbon capture system that includes a recycling step, b. To guide the saturated vapor fluid flow, which is at least partially condensed, to the regeneration step, c. The fluid flow discharged from the regeneration step is guided to the heat pump cycle, the fluid flow from the regeneration step supplies heat to the heat pump cycle, and the heat pump cycle generates steam. A method for generating water vapor, comprising the following characteristics.

166. The fluid flow exiting the regeneration step is CO 2 including, The method according to claim 162.

167. The fluid flow exiting the regeneration step is nitrogen (N 2 ) and / or oxygen (O 2 ) further includes, The method according to claim 163.

168. At least a portion of the steam generated by the heat pump cycle is sent to the regeneration step of the carbon capture system. The method according to claim 162.

169. (i) cooling the space with air from a heat pump system including a heat pump cycle, and (ii) supplying the air to an adsorbent layer of a carbon recovery system. The method according to claim 162, further comprising:

170. a. During startup conditions in which the pressure ratio between multiple compressors of the system falls below a threshold, one or more pumps are used to transport liquid as motor coolant from one or more locations in the main cycle to one or more motors, b. When the system gains pressure and completes the startup conditions, it transitions to a pressure-driven flow of motor coolant by using the fluid from one or more positions in the main cycle and turning off one or more pumps, A method for cooling a high-temperature compressor, comprising [a specific component / feature].

171. One or more positions in (a) are different from one or more positions in (b), The method according to claim 167.

172. One or more locations in (a) are: (i) between the system's expansion valve and evaporator; (ii) between the system's condenser and economizer; (iii) from the condenser; (iv) the condenser outlet; (v) the outlet of the suction tube heat exchanger; (vi) the coldest liquid in the system; (vii) any location between the system's condenser and expansion valve; or (viii) any location on the high-pressure side of the main cycle having a liquid reservoir. The method according to claim 167.

173. Another location in (b) is (i) between the system's expansion valve and evaporator, (ii) between the system's condenser and economizer, (iii) from the condenser, (iv) the condenser outlet, (v) the outlet of the suction tube heat exchanger, (vi) the coldest liquid in the system, (vii) any location between the system's condenser and expansion valve, or (viii) any location on the high-pressure side of the main cycle having a liquid reservoir. The method according to claim 167.

174. a. Dividing the motor coolant between multiple compressor stages within the system, b. Pooling together the motor coolant that has been divided among multiple compressors as described in (a), c. Send the motor coolant pooled from (b) to the suction side of the compressor where the pressure is lowest, A method for cooling a high-temperature compressor having [a specific feature / feature].

175. (c) supplying motor coolant includes (i) piping the motor coolant to the outlet of the system's evaporator, (ii) piping the motor coolant to the inlet of the evaporator, or between the expansion valve and the evaporator, or (iii) combining the motor coolant with a high-temperature gas bypass flow. The method according to claim 171.

176. a. Dividing the motor coolant between multiple compressor stages within the system, b. Pooling together the motor coolant that has been divided among multiple compressors as described in (a), c. The motor coolant pooled from (b) is sent to one or more locations within the system, at least in part based on one or more operating conditions of the system. A method for cooling a high-temperature compressor, comprising [a specific component / feature].

177. One or more of the system's operating conditions include the system's operating temperature. The method according to claim 173.

178. If the operating temperature exceeds the threshold temperature, the motor coolant is sent to the compressor suction side, where the pressure is lowest. The method according to claim 174.

179. If the operating temperature falls below the threshold temperature, the motor coolant is supplied between two or more compressor stages, or downstream of the subsequent compressor stage. The method according to claim 174.

180. a. Obtaining a fluid mixture through a direct air recovery (DAC) regeneration step, b. Using a fluid mixture as a heat source for a heat pump system that condenses and supercools the fluid mixture, c. Using the supercooled water separated from the fluid mixture as feedwater for the heat pump to generate steam for repeating the DAC regeneration step, A method for integrating the operation of a heat pump and carbon recovery, comprising:

181. a. Install a glycol heater in one or more locations in the system, b. By diverting a certain amount of glycol to a glycol heater, and utilizing at least some of the heat from the working fluid of the heat pump cycle to heat a certain amount of glycol, c. Sending a certain amount of glycol to one or more heat exchangers (groups) of the heat pump, d. Defrosting one or more heat exchangers (groups) using a certain amount of glycol, A defrosting method having the following characteristics.

182. One or more positions include the discharge position of the bottom cycle compressor, the discharge position of the top cycle compressor, or any position on the top cycle. The method according to claim 178.

183. The downstream of the cyclic refrigerant is used in parallel with the main flow of the cyclic refrigerant to heat a certain amount of glycol. The method according to claim 179.

184. The glycol heater is operated in parallel with the heat exchanger by (i) using the glycol heater to condense the refrigerant and (ii) sending the refrigerant to the outlet of the two-phase heat exchanger, The method according to claim 178.

185. One or more positions include a position before the expansion valve on the system's top cycle, in which case the performance of the top cycle is improved by the subcooling of the refrigerant. The method according to claim 178.

186. Supercooling degrades the quality of the steam at the evaporator inlet. The method according to claim 182.

187. One or more heat exchangers(s) are defrosted in parallel using a single glycol loop, and the glycol in the single glycol loop is used to defrost each individual heat exchanger(s) of the one or more heat exchangers(s) sequentially or simultaneously. The method according to claim 178.

188. The system includes using the heat storage or heat release of a thermal storage device to heat glycol used in a defrosting cycle, and the defrosting cycle includes single defrosting or parallel defrosting. Method for heating glycol.

189. A system equipped with an intake tube heat exchanger and an economizer, with the positions of the intake tube heat exchanger and economizer being switchable in any cycle configuration.

190. Because the positions of the suction tube heat exchanger and economizer can be switched, the liquid at the outlet of the system's steam generator is cooled by the suction tube heat exchanger before entering the economizer. The system according to claim 186.

191. A system comprising a suction tube heat exchanger and an economizer, wherein the fluid flowing into the expansion valve of the economizer is drawn out from the downstream of the suction tube heat exchanger, thereby cooling the fluid by at least 10–50°C.

192. A system comprising multiple compressor stages, wherein an economizer or intercooler is configured to be injected into one or more of the multiple compressor stages, at least partially based on the operating mode.

193. The operating mode is at least partially based on whether one or more compressors are operating or bypassed in a given cycle. The system according to claim 189.

194. The operating mode is at least partially based on the total pressure ratio across one or more compressors. The system according to claim 189.

195. The operating mode is, at least partially, based on the ambient air temperature. The system according to claim 189.

196. It comprises multiple compressor stages and multiple economizers located in multiple intercoolers or injection positions, and the multiple economizers are configured to operate in parallel or in series. system.

197. A method for using ejectors in one or more cycles to recover energy in a refrigerant flow throttling process by increasing the heat absorption capacity, at least partially, and reducing the work performed by one or more compressors.

198. a. Forming a two-phase fluid by restricting the fluid flowing out of the condenser to a low pressure, b. Supplying a two-phase fluid to a flash tank, c. By supplying steam from the top of the flash tank to an intercooler between two or more compressor stages, cooling and increased flow rate are supplied to the subsequent compressor stages. d. The liquid at the bottom of the flash tank is reduced to the evaporator pressure, and the liquid is heated by a heat source or bottom cycle. A method using a flash tank economizer that has the following characteristics.

199. a. Cooling the refrigerant and reducing it to an intermediate pressure so that the fluid exits the first heat exchanger and forms a two-phase fluid, b. Mixing the two-phase fluid with the flow from the outlet of the first compressor to form a two-phase mixture, c. Supplying the two-phase mixture to the flash tank, d. Sending the saturated liquid at the bottom of the flash tank to the second heat exchanger to evaporate the refrigerant and introduce it into the intake of the first compressor, e. Sending saturated steam from the top of the flash tank to the intake of the second compressor, A method of using a flash tank between compressor stages, which has the following characteristics.

200. This further includes closing the valve on the outlet stream at the top of the flash tank, thereby sending all fluid discharged from the flash tank to the second heat exchanger. The method according to claim 196.

201. This further includes closing the valve in the stream between the economizer and the second compressor, the valve being closed while the ambient temperature is high. The method according to claim 196.

202. It features multiple heat pumps and a centralized air coil cluster, the centralized air coil cluster having glycol loops configured to collect heat from the surrounding air. system.

203. Multiple heat pumps are installed in separate locations or in a centralized location. The system according to claim 199.

204. Multiple heat pumps are arranged in series or in parallel. The system according to claim 200.

205. The integrated device comprises multiple heat exchanger functions, and the integrated device comprises at least two inlet ports or at least two outlet ports. A heat pump that generates water vapor from an air source.

206. The integrated device is a combination of a steam generator, an economizer, and an intake tube heat exchanger. A water vapor generating air source heat pump according to claim 202.

207. The integrated device is a combination of a two-phase heat exchanger, an economizer, and an evaporator. A water vapor generating air source heat pump according to claim 202.

208. The process further includes superheating and removing the water vapor after it has been compressed. The method according to claim 25.

209. Superheating of the steam is removed by injecting water into the steam at one or more locations to cool it to a saturated state, and these one or more locations are downstream of the steam compressor, upstream of the steam compressor, or at the steam compressor itself. The method according to claim 208.

210. The steam is de-superheated by cooling it to saturation using heat transfer fluid from one or more cycles of a heat pump at one or more locations, where one or more locations are downstream of the steam compressor, upstream of the steam compressor, or at the steam compressor itself. The method according to claim 208.

211. a. Heating the working fluid of the topping cycle by transferring heat from the working fluid of the heat pump cycle to the working fluid of the topping cycle, b. Compressing the working fluid of the topping cycle, c. Generating steam by transferring heat from the working fluid of the topping cycle to the supply water flow, A method for generating water vapor, comprising the following features.

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