Industrial heat pumps for transporting heat with a refrigerant and a method of operating the same

Abstract

An industrial heat pump includes an evaporator configured to transfer heat into a refrigerant, a condenser configured to transfer the heat out of the refrigerant to a heat sink, a first fluid path, a second fluid path, and an expansion valve defining a portion of the first fluid path. The industrial heat pump includes a thermal storage unit defining a portion of the second fluid path. The thermal storage unit is configured to receive and store heat from the refrigerant in the second fluid path. The industrial heat pump includes a compressor defining a portion of the second fluid path between the thermal storage unit and the condenser. The heat received by the thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the compressor where the refrigerant phase changes to a gas.

Description

INDUSTRIAL HEAT PUMPS FOR TRANSPORTING HEAT WITH A REFRIGERANT AND A METHOD OF OPERATING THE SAMETECHNICAL FIELD

[0001] The present specification generally relates to industrial heat pumps and, more specifically, industrial heat pumps that reach high temperatures with improved efficiency.BACKGROUND

[0002] The manufacturing industry in the United States is responsible for about 25% of the country's total energy consumption and greenhouse gas emissions. One of the major contributors to this energy demand is heat, which represents almost one-fifth of the global energy demand and about two-thirds of the final energy demand in the industrial sector. In the US, thermal processes account for approximately 75% of the total final energy demand. Therefore, decarbonizing the industrial heat demand through the use of electrification could have a significant impact on mitigating climate change. Industrial heat pumps (IHPs) have emerged as a promising technology for energy-efficient and sustainable industrial processes. IHPs are used to upgrade waste heat from industrial processes to higher temperatures, enabling their use for various applications such as drying, distillation, and sterilization. Studies have shown that IHPs have the potential to reduce primary energy consumption in the industrial sector by up to 30% and reduce CO2 emissions by up to 50% compared to conventional heating technologies.

[0003] To cover the wide range of industrial applications, IHPs should reach temperatures of 200°C or higher. However, increasing the temperature reduces the efficiency of IHPs. Accordingly, a need exists for an alternative IHPs for reaching high temperatures with improved efficiency.SUMMARY

[0004] In one embodiment, an industrial heat pump for transporting heat with a refrigerant may include an evaporator having an input port for receiving the refrigerant and an output port for expelling the refrigerant. The evaporator is configured to transfer the heat into the refrigerant from a heat source. The industrial heat pump may further include a condenser having an input port for receiving the refrigerant and an output port for expelling the refrigerant. The condenser is configured to transfer the heat out of the refrigerant to a heat sink. The industrial heat pump may further include a first fluid path extending between the output port of the condenser and the input port of the evaporator and a second fluid path extending between the output port of the evaporator and the input port of the condenser. The industrial heat pump may further include an expansion valve defining a portion of the first fluid path between the evaporator and the condenser that causesat least a portion of the refrigerant flowing from the condenser to the evaporator to phase change from a liquid to a gas. The industrial heat pump may further include a thermal storage unit defining a portion of the second fluid path. The thermal storage unit is configured to receive and store heat from the refrigerant in the second fluid path. The industrial heat pump may further include a compressor defining a portion of the second fluid path between the thermal storage unit and the condenser. The heat received by the thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the compressor where the refrigerant phase changes to a gas.

[0005] In another embodiment, an industrial heat pump for transporting heat with a refrigerant may include an evaporator having an input port for receiving the refrigerant and an output port for expelling the refrigerant. The evaporator is configured to transfer the heat into the refrigerant from a heat source. The industrial heat pump may further include a condenser having an input port for receiving the refrigerant and an output port for expelling the refrigerant. The condenser is configured to transfer the heat out of the refrigerant to a heat sink. The industrial heat pump may further include a first fluid path extending between the output port of the condenser and the input port of the evaporator and a second fluid path extending between the output port of the evaporator and the input port of the condenser. The industrial heat pump may further include a first thermal storage unit defining a portion of the first fluid path and a portion of the second fluid path. The first thermal storage unit is configured to receive and store heat from the refrigerant in the first fluid path and from the refrigerant in the second fluid path. The industrial heat pump may further include a second thermal storage unit defining a portion of the first fluid path between the first thermal storage unit and the condenser and a portion of the second fluid path between the first thermal storage unit and the condenser. The second thermal storage unit is configured to receive and store heat from the refrigerant in the first fluid path and from the refrigerant in the second fluid path. The industrial heat pump may further include a first expansion valve defining a portion of the first fluid path between the evaporator and the first thermal storage unit that causes at least a portion of the refrigerant flowing from the first thermal storage unit to the evaporator to phase change from a liquid to a gas. The industrial heat pump may further include a second expansion valve defining a portion of the first fluid path between the first thermal storage unit and the second thermal storage unit that causes at least a portion of the refrigerant flowing from the second thermal storage unit to the first thermal storage unit to phase change from a liquid to a gas. The industrial heat pump may further include a third expansion valve defining a portion of the first fluid path between the second thermal storage unit and the condenser that causes at least aportion of the refrigerant flowing from the condenser to the second thermal storage unit to phase change from a liquid to a gas. The industrial heat pump may further include a first compressor defining a portion of the second fluid path between the evaporator and the first thermal storage unit. The industrial heat pump may further include a second compressor defining a portion of the second fluid path between the first thermal storage unit and the second thermal storage unit. The heat received by the first thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the second compressor where the refrigerant phase changes to a gas. The industrial heat pump may further include a third compressor defining a portion of the second fluid path between the second thermal storage unit and the condenser. The heat received by the second thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the third compressor where the refrigerant phase changes to a gas.

[0006] In yet another embodiment, a method of operating an industrial heat pump is disclosed. The industrial heat pump may include an evaporator having an input port and an output port, a condenser having an input port and an output port, a first fluid path extending between the output port of the condenser and the input port of the evaporator, a second fluid path extending between the output port of the evaporator and the input port of the condenser, an expansion valve defining a portion of the first fluid path between the evaporator and the condenser, a thermal storage unit defining a portion of the second fluid path, and a compressor defining a portion of the second fluid path between the thermal storage unit and the condenser. The method may include transporting the refrigerant through the first fluid path from the output port of the condenser, phase changing at least a portion of the refrigerant flowing from the condenser to the evaporator through the expansion valve from a liquid to a gas, receiving the refrigerant into the input port of the evaporator from the first fluid path, and transferring the heat into the refrigerant from a heat source with the evaporator. The method may further include expelling the refrigerant through the output port of the evaporator into the second fluid path, receiving and storing heat from the refrigerant in the thermal storage unit, phase changing at least a portion of the refrigerant from a gas to liquid, and wet compressing the refrigerant through the compressor. The method may further include phase changing the refrigerant to a gas, receiving the refrigerant into the input port of the condenser from the second fluid path, transferring the heat out of the refrigerant to a heat sink with the condenser, and expelling the refrigerant through the output port of the condenser into the first fluid path.

[0007] These and additional features provided by the embodiments described herein will be more fully understood in view of the following detailed description, in conjunction with the drawings.BRIEF DESCRIPTION OF THE DRAWINGS

[0008] The embodiments set forth in the drawings are illustrative and exemplary in nature and not intended to limit the subject matter defined by the claims. The following detailed description of the illustrative embodiments can be understood when read in conjunction with the following drawings, where like structure is indicated with like reference numerals and in which:

[0009] FIG. 1 depicts a schematic illustration of an industrial heat pump, according to one or more embodiments shown and described herein;

[0010] FIG. 2 depicts a line graph showing enthalpy of a refrigerant within the industrial heat pump of FIG. 1 relative to a pressure of a refrigerant, according to one or more embodiments shown and described herein;

[0011] FIG. 3A depicts a schematic illustration of the industrial heat pump of FIG. 1 showing heat flow and refrigerant flow while a first thermal storage unit and a second storage thermal unit are charging, according to one or more embodiments shown and described herein;

[0012] FIG. 3B depicts a schematic illustration of the industrial heat pump of FIG. 3 A showing heat flow and refrigerant flow while the first thermal storage unit is discharging, according to one or more embodiments shown and described herein; and

[0013] FIG. 3C depicts a schematic illustration of the industrial heat pump of FIG. 3B showing heat flow and refrigerant flow while the second thermal storage unit is discharging, according to one or more embodiments shown and described herein.DETAILED DESCRIPTION

[0014] FIG. 1 generally depicts an embodiment of an industrial heat pump for transporting heat with a refrigerant. The industrial heat pump as illustrated generally includes an evaporator for transferring heat into the refrigerant from a heat source, a condenser for transferring the heat out of the refrigerant to a heat sink, first and second thermal storage units for receiving and storing heat from the refrigerant, first, second, and third expansion valves for phase changing the refrigerant, and first, second, and third compressors for compressing the refrigerant. Various embodiments of the industrial heat pump and the operation of the industrial heat pump will be described in more detail herein.

[0015] The industrial heat pump described herein is contemplated for industrial applications. To cover the wide range of industrial applications, industrial heat pumps may reachtemperatures of 200°C or more. However, increasing the operating temperature reduces the efficiency of conventional industrial heat pumps. The embodiments described herein overcome these limitations by utilizing wet compression and thermal storage to allow for increased operating temperature while increasing the efficiency of the industrial heat pump and reducing energy demand to reach the high temperature.

[0016] Referring now to the drawings, FIG. 1 schematically depicts an exemplary embodiment of an industrial heat pump 20 for transporting heat with a refrigerant. In one example, the refrigerant is water. In another example, the refrigerant is 1,1,1,2-tetrafluoroethane (R134a). However, the refrigerant may be any fluid capable of undergoing repeated phase changes between a liquid and a gas.

[0017] The industrial heat pump 20 includes an evaporator 22 having an input port 24 for receiving the refrigerant and an output port 26 for expelling the refrigerant. The evaporator 22 is configured to transfer the heat into the refrigerant from a heat source. While the heat source contemplated herein is generated by industrial applications, the heat source may suitable source of heat, including commercial applications, residential applications, etc. The evaporator 22 may be a heat exchanger having a coil through which the refrigerant flow and fins coupled to the coil that increase surface area of the coil that is in contact with the heat source, thereby efficiently absorbing heat into the refrigerant. However, the evaporator 22 may have any suitable configuration for absorbing heat from the heat source.

[0018] The industrial heat pump 20 may include a condenser 28 having an input port 30 for receiving the refrigerant and an output port 32 for expelling the refrigerant. The condenser 28 is configured to transfer the heat out of the refrigerant to a heat sink. Like the evaporator 22, the condenser 28 may include a heat exchanger having a coil through which the refrigerant flow and fins coupled to the coil that increase surface area of the coil that is in contact with the heat sink, thereby efficiently transferring the heat out of the refrigerant. However, the condenser 28 may have any suitable configuration for absorbing heat from the heat source.

[0019] As shown in FIG. 1, the industrial heat pump 20 further includes a first fluid path 34 extending between the output port 32 of the condenser 28 and the input port 24 of the evaporator 22. Similarly, the industrial heat pump 20 further includes a second fluid path 36 extending between the output port 26 of the evaporator 22 and the input port 30 of the condenser 28. The first fluid path 34 and the second fluid path 36 collectively form a circuit through which the refrigerant flows between the evaporator 22 and the condenser 28. The first fluid path 34 and thesecond fluid path 36 may include components that will be described in detail below that are connected by tubing, hosing, pipes, or the like.

[0020] The industrial heat pump 20 further includes a first thermal storage unit 38 defining a portion of the first fluid path 34 and a portion of the second fluid path 36. The first thermal storage unit 38 is configured to receive and store heat from the refrigerant in the first fluid path 34 and from the refrigerant in the second fluid path 36. More specifically, the refrigerant is configured to flow into the first thermal storage unit 38 before flowing into the evaporator 22 along the first fluid path 34 and upon exiting the evaporator 22 along the second fluid path 36. Therefore, the first thermal storage unit 38 is capable of absorbing heat from both of the first fluid path 34 and the second fluid path 36.

[0021] The first thermal storage unit 38 may include a housing 40 defining an interior 42 for holding a phase change material 44. The phase change material 44 may be any material or composition of the materials capable of absorbing and retaining heat therein. For example, the phase change material 44 may be paraffins, salts, salt hydrates, metal alloys, etc.

[0022] The first thermal storage unit 38 may further include a first line 46 defining a portion of the first fluid path 34 and a second line 48 defining a portion of the second fluid path 36. The first line 46 and the second line 48 may be any form of conduit, such as flexible tubing, hose, piping, etc. The first line 46 and the second line 48 are disposed within the interior 42 and contact the phase change material 44 to cause heat transfer between the refrigerant and the phase change material 44. Therefore, as refrigerant flows through the first line 46 and / or the second line 48, the heat is transferred to the first line 46 and / or second line 48, respectively. The first line 46 and / or the second line 48 in turn transfer the heat to the phase change material 44 through contact with the phase change material 44. It is to be appreciated that in certain conditions (as will be described below) the opposite may be true. More specifically, heat stored within the phase change material 44 may be transferred to the first line 46 and / or the second line 48 and further to the refrigerant within the first line 46 and / or the second line 48.

[0023] Both of the first line 46 and the second line 48 may be coiled within the interior 42 of the housing 40, as shown in FIG. 1, to efficiently contact and promote heat transfer with the phase change material 44. However, the first line 46 and the second line 48 may have any suitable configuration(s) for within the interior 42 of the housing 40.

[0024] The industrial heat pump 20 may further include a second thermal storage unit 50 defining a portion of the first fluid path 34 between the first thermal storage unit 38 and the condenser 28 and a portion of the second fluid path 36 between the first thermal storage unit 38and the condenser 28. The second thermal storage unit 50 is configured to receive and store heat from the refrigerant in the first fluid path 34 and from the refrigerant in the second fluid path 36. More specifically, the refrigerant is configured to flow into the second thermal storage unit 50 before the first thermal storage unit 38 and before flowing into the evaporator 22 along the first fluid path 34 and upon exiting the evaporator 22 and the first thermal storage unit 38 along the second fluid path 36. Therefore, the second thermal storage unit 50 is capable of absorbing heat from both of the first fluid path 34 and the second fluid path 36.

[0025] The second thermal storage unit 50 may be similar in construction to the first thermal storage unit 38, with the second thermal storage unit 50 including a housing 52 defining an interior 54, a phase change material 56, a first line 58, and a second line 60 defining a portion of the second fluid path 36, similar to the housing 40, the interior 42, the phase change material 44, the first line 46, and the second line 48 of the first thermal storage unit 38. Therefore, the description of the first thermal storage unit 38 above and throughout is directly applicable to the second thermal storage unit 50.

[0026] As shown in FIG. 1, the industrial heat pump 20 may include one or more expansion valves. For example, as depicted the industrial heat pump 20 include a first expansion valve 62 defining a portion of the first fluid path 34 between the evaporator 22 and the condenser 28 that causes at least a portion of the refrigerant flowing from the condenser 28 to the evaporator 22 to phase change from a liquid to a gas. More specifically, the first expansion valve 62 defines a portion of the first fluid path 34 between the evaporator 22 and the thermal storage unit that causes at least a portion of the refrigerant flowing from the first thermal storage unit 38 to the evaporator 22 to phase change from a gas to a liquid. The industrial heat pump 20 may further include a second expansion valve 64 defining a portion of the first fluid path 34 between the first thermal storage unit 38 and the condenser 28. More specifically, the second expansion valve 64 defines a portion of the first fluid path 34 between the first thermal storage unit 38 and the second thermal storage unit 50. The second expansion valve 64 causes at least a portion of the refrigerant flowing from the second thermal storage unit 50 to the first thermal storage unit 38 to phase change from a gas to a liquid. The industrial heat pump 20 may further include a third expansion valve 66 defining a portion of the first fluid path 34 between the second thermal storage unit 50 and the condenser 28 that causes at least a portion of the refrigerant flowing from the condenser 28 to the second thermal storage unit 50 to phase change from a gas to liquid.

[0027] Each of the first expansion valve 62, the second expansion valve 64, and the third expansion valve 66 may include an orifice that meters the flow of the refrigerant there through.More specifically, the orifice restricts the flow of the refrigerant, thereby reducing the pressure of the refrigerant. Accordingly, the pressure of the refrigerant upon exiting the first expansion valve 62, the second expansion valve 64, or the third expansion valve 66 is less than the pressure of the refrigerant prior to entering the first expansion valve 62, the second expansion valve 64, or the third expansion valve 66, respectively. It is to be appreciated that each of the first expansion valve 62, the second expansion valve 64, and the third expansion valve 66 may be configured as orifice tubes or any other suitable components that meter the flow of the refrigerant.

[0028] As shown in FIG. 1, the industrial heat pump 20 may further include a first compressor 68 defining a portion of the second fluid path 36 between the evaporator 22 and the first thermal storage unit 38. The first compressor 68 may be configured as a rotary compressor, scroll compressor, or any other suitable compressor configuration. Further, the first compressor 68 contemplated herein is electrically powered. However, the first compressor 68 may be powered by hydraulics, pneumatics, or in any other suitable manner.

[0029] The first compressor 68 receives the refrigerant coming from the evaporator 22. The refrigerant may be partially in the liquid phase and partially in the gas phase and the first compressor 68 compresses the refrigerant through wet compression, which refers to the presence of liquid in the refrigerant as opposed to compression of a refrigerant that is almost entirely in the gas phase (i.e., dry compression). However, the refrigerant may exit the evaporator 22 in a fully gas phase, causing the first compressor 68 to dry compress the refrigerant. In either state, the compression of the refrigerant through the first compressor 68 causes the refrigerant to phase change into a gas before entering the first thermal storage unit 38.

[0030] The industrial heat pump 20 may further include a second compressor 70 defining a portion of the second fluid path 36 between the first thermal storage unit 38 and the condenser 28, with the second thermal storage unit 50 defining a portion of the second fluid path 36 between the second compressor 70 and the condenser 28. More specifically, the second compressor 70 defines a portion of the second fluid path 36 between the first thermal storage unit 38 and the second thermal storage unit 50. The heat received by the first thermal storage unit 38 causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the second compressor 70 and a phase change of the refrigerant to a gas. As will be explained in greater detail below, the use of wet compression achieves high temperatures and improved efficiency, which enhances the coefficient of performance of the industrial heat pump 20 and produces potential energy savings in comparison to dry compression.

[0031] The industrial heat pump 20 may further include a third compressor 72 defining a portion of the second fluid path 36 between the second thermal storage unit 50 and the condenser 28. The heat received by the second thermal storage unit 50 causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the third compressor 72 and a phase change of the refrigerant to a gas.

[0032] The second compressor 70 and the third compressor 72 may be similar in construction to the first compressor 68. Therefore, the description of the first compressor 68 above and throughout is directly applicable to the second compressor 70 and the third compressor 72 and is not repeated for brevity.

[0033] The industrial heat pump 20 may further include a first regulator valve 74 connected to the second fluid path 36 between the first compressor 68 and the second compressor 70, bypassing the first thermal storage unit 38. The first regulator valve 74 is movable between a closed configuration that directs all of the refrigerant from the first compressor 68 through the first thermal storage unit 38, and an open configuration that directs at least a portion of the refrigerant as a gas from the first compressor 68 to the second compressor 70 to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the second compressor 70. Said differently, the first regulator valve 74 may be adjusted to control the flow of the refrigerant into the first thermal storage unit 38. Since the refrigerant exiting the first compressor 68 is in the gas phase, opening the first regulator valve 74 causes the amount of gaseous refrigerant entering the second compressor 70 to increase. On the other hand, closing the first regulator valve 74 causes all of the refrigerant to enter the first thermal storage unit 38 to thereby lose heat in the first thermal storage unit 38. As such, the refrigerant at least partially phase changes to a liquid before entering the second compressor 70. The first regulator valve 74 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration.

[0034] In some examples, the movement of the first regulator valve 74 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the first regulator valve 74 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the first regulator valve 74 may be controlled in any suitable manner.

[0035] The industrial heat pump 20 may further include a second regulator valve 76 connected to the second fluid path 36 between the second compressor 70 and the third compressor 72, bypassing the second thermal storage unit 50. The second regulator valve 76 is movable between a closed configuration that directs all of the refrigerant from the second compressor 70through the second thermal storage unit 50, and an open configuration that directs at least a portion of the refrigerant as a gas from the second compressor 70 to the third compressor 72 to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the third compressor 72. The second regulator valve 76 may be similar in construction and function to the first regulator valve 74. Therefore the discussion of the first regulator valve 74 above is directly applicable to the second regulator valve 76 and is not repeated for brevity.

[0036] As shown in FIG. 1, the industrial heat pump 20 may further include a first bypass discharge valve 78 fluidically coupled to both the first fluid path 34 between the first thermal storage unit 38 and the evaporator 22 and the second fluid path 36 between the first thermal storage unit 38 and the evaporator 22. The first bypass discharge valve 78 is movable between a closed configuration that directs the refrigerant through the evaporator 22 to receive the heat from the heat source, and an open configuration that redirects at least a portion of the refrigerant between the first fluid path 34 and the second fluid path 36 bypassing the evaporator 22 to discharge the heat stored in the first thermal storage unit 38 into the refrigerant before entering the compressor. The first bypass discharge valve 78 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the first bypass discharge valve 78 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the first bypass discharge valve 78 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the first bypass discharge valve 78 may be controlled in any suitable manner.

[0037]

[0038] The industrial heat pump 20 may include a first stop valve 80 adjacent the first expansion valve 62 that moves between an open configuration and a closed configuration. In the open configuration, the first stop valve 80 allows refrigerant to pass through the first expansion valve 62. In the closed configuration, the first stop valve 80 inhibits the flow of refrigerant to the first expansion valve 62. The first stop valve 80 works in unison with the first bypass discharge valve 78, with the first stop valve 80 in the open configuration when the first bypass discharge valve 78 is in the closed position and with the first stop valve 80 in the closed configuration when the first bypass discharge valve 78 is in the open position. The first stop valve 80 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the first stop valve 80 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the first stopvalve 80 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the first stop valve 80 may be controlled in any suitable manner.

[0039] When the first bypass discharge valve 78 is in the open configuration and the first stop valve 80 is in the closed configuration, the first bypass discharge valve 78 disconnects the evaporator 22, the first compressor 68, and the first expansion valve 62 from the remainder of the industrial heat pump 20. As such, the evaporator 22 can no longer introduce heat into the refrigerant. In turn, the first thermal storage unit 38 functions as a heat source for the refrigerant, thereby discharging the heat into the refrigerant and through the system to the condenser 28 where the heat is transferred out of the refrigerant to the heat sink. When the first bypass discharge valve 78 is in the closed configuration and the first stop valve 80 is in the open configuration, the first bypass discharge valve 78 connects the evaporator 22, the first compressor 68, and the first expansion valve 62 to the remainder of the industrial heat pump 20, allowing the evaporator 22 to introduce heat into the refrigerant.

[0040] The industrial heat pump 20 further includes a second bypass discharge valve 82 fluidically coupled to both the first fluid path 34 between the second thermal storage unit 50 and the first thermal storage unit 38 and the second fluid path 36 between the second thermal storage unit 50 and the first thermal storage unit 38. The second bypass discharge valve 82 is movable between a closed configuration that directs the refrigerant through the first thermal storage unit 38 and the evaporator 22 (if the first bypass discharge valve 78 is in the closed configuration) to receive the heat from the first thermal storage unit 38 and / or the evaporator 22, and an open configuration that redirects at least a portion of the refrigerant between the first fluid path 34 and the second fluid path 36 bypassing both the first thermal storage unit 38 and the evaporator 22 to discharge the heat stored in the second thermal storage unit 50 into the refrigerant before entering the compressor. The second bypass discharge valve 82 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the second bypass discharge valve 82 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the second bypass discharge valve 82 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the second bypass discharge valve 82 may be controlled in any suitable manner.

[0041] The industrial heat pump 20 includes a second stop valve 84 adjacent the second expansion valve 64 that moves between an open configuration and a closed configuration. In the open configuration, the second stop valve 84 allows refrigerant to pass through the second expansion valve 64. In the closed configuration, the second stop valve 84 inhibits the flow ofrefrigerant to the second expansion valve 64. The second stop valve 84 works in unison with the second bypass discharge valve 82, with the second stop valve 84 in the open configuration when the second bypass discharge valve 82 is in the closed position and with the second stop valve 84 in the closed configuration when the second bypass discharge valve 82 is in the open position. The second stop valve 84 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the second stop valve 84 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the second stop valve 84 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the second stop valve 84 may be controlled in any suitable manner.

[0042] When the second bypass discharge valve 82 is in the open configuration and the second stop valve 84 is in the closed configuration, the second bypass discharge valve 82 disconnects the evaporator 22, the first compressor 68, the first expansion valve 62, the first thermal storage unit 38, the second compressor 70, and the second expansion valve 64 from the remainder of the industrial heat pump 20. As such, the evaporator 22 and the first thermal storage unit 38 can no longer introduce heat into the refrigerant. In turn, the second thermal storage unit 50 functions as a heat source for the refrigerant, thereby discharging the heat into the refrigerant and through the system to the condenser 28 where the heat is transferred out of the refrigerant to the heat sink. When the second bypass discharge valve 82 is in the closed configuration and the second stop valve 84 is in the open configuration, the second bypass discharge valve 82 the evaporator 22, the first compressor 68, the first expansion valve 62, the first thermal storage unit 38, the second compressor 70, and the second expansion valve 64 to the remainder of the industrial heat pump 20, allowing the evaporator 22 and / or the first thermal storage unit 38 to introduce heat into the refrigerant.

[0043] The operation of charging and discharging the first thermal storage unit 38 and the second thermal storage unit 50 will be described in greater detail below. Therefore, the operation of the first bypass discharge valve 78 and the second bypass discharge valve 82 will be better understood in the description below.

[0044] As shown in FIG. 1, the industrial heat pump 20 may further include a first bypass charge valve 86 fluidically coupled to each of the first line 46 and the second line 48 of the first thermal storage unit 38. The first bypass charge valve 86 is movable between a closed configuration that separates the first line 46 and the second line 48 to direct all of the refrigerant through the condenser 28 and an open configuration that connects the first line 46 and the secondline 48 to reduce flow of the refrigerant to the condenser 28 and increase the transfer of heat from the refrigerant into the phase change material 44 for storage in the first thermal storage unit 38. Said differently, when in the open configuration, the first bypass charge valve 86 at least partially disconnects the condenser 28, the third expansion valve 66, the third compressor 72, the second thermal storage unit 50, the second expansion valve 64, and the second compressor 70 from the remainder of the industrial heat pump 20. As such, the condenser 28 and the second thermal storage unit 50 can no longer remove heat from the refrigerant. In turn, more heat goes through the first thermal storage unit 38 and the first thermal storage unit 38 absorbs the heat at a faster rate than when the first bypass charge valve 86 is in the closed configuration. Accordingly, the first bypass charge valve 86 functions to charge the first thermal storage unit 38 with heat.

[0045] In another configuration, the first bypass charge valve 86 is partially open (e.g., 50% open), allowing a portion of the refrigerant to circulate through the second fluid path 36 to the condenser 22. At the same time, the remaining portion of the refrigerant will transition from a gas to a liquid, thereby increasing the amount of heat stored in the first thermal storage unit 38 and extending the time of peak demand reduction (i.e., reduced energy consumption).

[0046] The first bypass charge valve 86 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the first bypass charge valve 86 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the first bypass charge valve 86 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the first bypass charge valve 86 may be controlled in any suitable manner.

[0047] The industrial heat pump 20 may further include a second bypass charge valve 88 fluidically coupled to each of the first line 58 and the second line 60 of the second thermal storage unit 50. The second bypass charge valve 88 is movable between a closed configuration that separates the first line 58 and the second line 60 to direct all of the refrigerant through the condenser 28 and an open configuration that connects the first line 58 and the second line 60 to reduce flow of the refrigerant to the condenser 28 and increase the transfer of heat from the refrigerant into the phase change material 56 for storage in the second thermal storage unit 50. Said differently, when in the open configuration, the second bypass charge valve 88 disconnects the condenser 28, the third expansion valve 66, and the third compressor 72 from the remainder of the industrial heat pump 20. As such, the condenser 28 can no longer remove heat from the refrigerant. In turn, more heat goes through the second thermal storage unit 50 and the second thermal storage unit 50 absorbs the heat at a faster rate than when the second bypass charge valve88 is in the closed configuration. Accordingly, the second bypass charge valve 88 functions to charge the first thermal storage unit 38 with heat.

[0048] In another configuration, the second bypass charge valve 88 is partially open (e.g., 50% open), allowing a portion of the refrigerant to circulate through the second fluid path 36 to the condenser 22. At the same time, the remaining portion of the refrigerant will transition from a gas to a liquid, thereby increasing the amount of heat stored in the second thermal storage unit 50 and extending the time of peak demand reduction (i.e., reduced energy consumption).

[0049] The second bypass charge valve 88 may be a ball valve, a gate valve, a butterfly valve, a needle valve, a globe valve, or any other suitable valve configuration. In some examples, the movement of the second bypass charge valve 88 is controlled manually by an operator, such as via a handle, knob, etc. In other examples, the movement of the second bypass charge valve 88 is controlled automatically by a controller, computer, or the like. It is to be appreciated that movement of the second bypass charge valve 88 may be controlled in any suitable manner.

[0050] The operation of charging and discharging the first thermal storage unit 38 and the second thermal storage unit 50 will be described in greater detail below. Therefore, the operation of the first bypass discharge valve 78 and the second bypass discharge valve 82 will be better understood in the description below.

[0051] The operation of the industrial heat pump 20 will now be described, beginning with a standard operation cycle that both transports heat from the evaporator 22 to the condenser 28, as well as charges the first thermal storage unit 38 and the second thermal storage unit 50 with heat. The operation will generally refer to the schematic illustration of the industrial heat pump 20 shown in FIG. 3 A. Specific reference will also be made throughout the description of the operation to FIG. 2, which is a line graph showing the enthalpy of the refrigerant relative to the pressure of the refrigerant.

[0052] In general, flow of the refrigerant within the heat pump is caused by first compressor 68, the second compressor 70, and the third compressor 72. Beginning with the refrigerant at the evaporator 22, the evaporator 22 absorbs heat from the heat source into the refrigerant therein. The refrigerant exits the evaporator 22 through the output port 26 into the second fluid path 36 in a combination of a liquid phase and a gas phase. The refrigerant enters the first compressor 68 (point 1 of FIG. 2). The first compressor 68 wet compresses the refrigerant, which leaves the first compressor 68 as a gaseous saturated vapor (point 2 of FIG. 2). With the first bypass discharge valve 78 in the closed configuration, the refrigerant enters the first thermal storage unit 38. The first thermal storage unit 38 is colder than the refrigerant and will absorb theheat from the refrigerant, condensing a certain amount of the refrigerant into the liquid phase, and storing its latent heat in the first thermal storage unit 38, moving the refrigerant condition from point 2 to point 3 in FIG. 2.

[0053] The refrigerant enters the second compressor 70 (point 3 of FIG. 2). The second compressor 70 wet compresses the refrigerant, which leaves the second compressor 70 as a gaseous saturated vapor (point 4 of FIG. 2). With the second bypass discharge valve 82 in the closed configuration, the refrigerant enters the second thermal storage unit 50. The second thermal storage unit 50 is colder than the refrigerant and will absorb the heat from the refrigerant, condensing a certain amount of the refrigerant into the liquid phase, and storing its latent heat in the second thermal storage unit 50, moving the refrigerant condition from point 4 to point 5 in FIG. 2.

[0054] The refrigerant enters the third compressor 72 (point 5 of FIG. 2). The third compressor 72 wet compresses the refrigerant, which leaves the third compressor 72 as a gaseous saturated vapor (point 6 of FIG. 2). The refrigerant enters the condenser 28 through the input port 30. The condenser 28 is colder than the refrigerant and will absorb the heat from the refrigerant, condensing the refrigerant into the liquid phase, and transporting the heat to the heat sink, moving the refrigerant condition from point 6 to point 7 in FIG. 2.

[0055] The refrigerant exits the condenser 28 through the output port 32 into the first fluid path 34 in the liquid phase. The refrigerant enters the third expansion valve 66. The refrigerant exits the third expansion valve 66 at reduced pressure (point 7 to point 8 of FIG. 2) in a combination of a liquid phase and a gas phase. The refrigerant enters the second thermal storage unit 50. The second thermal storage unit 50 is colder than the refrigerant and will absorb the heat from the refrigerant, condensing the refrigerant into the liquid phase, and storing its latent heat released during condensing in the second thermal storage unit 50, moving the refrigerant condition from point 8 to point 9 in FIG. 2.

[0056] The refrigerant exits the second thermal storage unit 50 and enters the second expansion valve 64. The refrigerant exits the second expansion valve 64 at reduced pressure (point 9 to point 10 of FIG. 2) in a combination of a liquid phase and a gas phase. The refrigerant enters the first thermal storage unit 38. The first thermal storage unit 38 is colder than the refrigerant and will absorb the heat from the refrigerant, condensing the refrigerant into the liquid phase, and storing its latent heat released during condensing in the first thermal storage unit 38, moving the refrigerant condition from point 10 to point 11 in FIG. 2.

[0057] The refrigerant exits the first thermal storage unit 38 and enters the first expansion valve 62. The refrigerant exits the first expansion valve 62 at reduced pressure (point 11 to point 12 of FIG. 2) in a combination of a liquid phase and a gas phase. The refrigerant enters the evaporator 22 through the input port 24, where the refrigerant absorbs the heat from the heat source, moving the refrigerant condition from point 12 to point 1 in FIG. 2, and thereby starting the cycle over again.

[0058] FIG. 2 shows a comparison of the operation of the industrial heat pump 20 when wet compression is used as described herein versus an operation where wet compression is not achieved (i.e., dry compression). The difference in the cycles is shown between the points 1-6 (indicating wet compression) and points l’-6’ (indicating dry compression). The wet compression produces less enthalpy at the same respective pressures as the dry compression, leading to improved efficiency of the industrial heat pump 20.

[0059] As described above, the first regulator valve 74 and the second regulator valve 76 may be operated to adjust the proportion of refrigerant in the gas phase to refrigerant in the liquid phase entering the second compressor 70 and the third compressor 72, respectively. Accordingly, during operation the first regulator valve 74 and / or the second regulator valve 76 may be adjusted to achieve the optimal or desired enthalpy.

[0060] As also described above, the first bypass charge valve 86 and the second bypass charge valve 88 may be operated to selectively reduce flow of the refrigerant to the condenser 28 and increase the transfer and storage of heat in the first thermal storage unit 38 and the second thermal storage unit 50, respectively. Accordingly, during operation the first bypass charge valve 86 and / or the second bypass charge valve 88 may be adjusted to achieve the optimal or desired heat storage level in the first thermal storage unit 38 and / or the second thermal storage unit 50, respectively.

[0061] When the first bypass charge valve 86 is in the open configuration, the first bypass charge valve 86 at least partially disconnects the condenser 28, the third expansion valve 66, the third compressor 72, the second thermal storage unit 50, the second expansion valve 64, and the second compressor 70 from the remainder of the industrial heat pump 20 and from the flow of the refrigerant as described in the operation above. As such, the condenser 28 and the second thermal storage unit 50 can no longer remove heat from the refrigerant. In turn, more heat goes through the first thermal storage unit 38 and the first thermal storage unit 38 absorbs the heat at a faster rate than when the first bypass charge valve 86 is in the closed configuration. Accordingly, the first bypass charge valve 86 functions to charge the first thermal storage unit 38 with heat.

[0062] When the second bypass charge valve 88 is in the open configuration, the second bypass charge valve 88 disconnects the condenser 28, the third expansion valve 66, and the third compressor 72 from the remainder of the industrial heat pump 20 and from the flow of the refrigerant as described in the operation above. As such, the condenser 28 can no longer remove heat from the refrigerant. In turn, more heat goes through the second thermal storage unit 50 and the second thermal storage unit 50 absorbs the heat at a faster rate than when the second bypass charge valve 88 is in the closed configuration. Accordingly, the second bypass charge valve 88 functions to charge the first thermal storage unit 38 with heat.

[0063] The operation of the industrial heat pump 20 to discharge the heat from the first thermal storage unit 38 and the second thermal storage unit 50 to the condenser 28, will now be described. When any of the first thermal storage unit 38 and the second thermal storage unit 50 are fully charged (i.e., achieved the maximum storage of heat), the industrial heat pump 20 will operate in a discharge mode which increases the efficiency of the industrial heat pump 20. In the discharge mode, the fully charged first thermal storage unit 38 or second thermal storage unit 50 becomes a heat source. The operation will generally refer to the schematics illustrations of the industrial heat pump 20 shown in FIGS. 3B and 3C.

[0064] When the first thermal storage unit 38 is fully charged, the first stop valve 80 moves from the open configuration to the closed configuration, inhibiting flow of the refrigerant to the first expansion valve 62. The first bypass discharge valve 78 moves from the closed configuration that directs the refrigerant through the evaporator 22 to receive the heat from the heat source to the open configuration that redirects the refrigerant between the first fluid path 34 and the second fluid path 36 bypassing the evaporator 22 to discharge the heat stored in the first thermal storage unit 38 into the refrigerant before entering the compressor.

[0065] Accordingly, the operation of discharging the first thermal storage unit 38 is the same as the general charging operation described above, but for the following differences. With reference to FIG. 3B, the refrigerant flowing from the second expansion valve 64 in the first fluid path 34 passes through the first line 46 of the first thermal storage unit 38. Upon exiting the first thermal storage unit 38, the first stop valve 80 in the closed configuration and the first bypass discharge valve 78 in the open configuration directs the refrigerant around the first thermal storage unit 38 and re-enters the first thermal storage unit 38 in the second line 48 as part of the second fluid path 36. Because the evaporator 22 was bypassed, heat was not absorbed into the refrigerant. Therefore, the refrigerant is cooler than the phase change material 44 of the first thermal storage unit 38. Heat is transferred from the phase change material 44 to the refrigerant causing therefrigerant to phase change at least partially to a gas. The refrigerant in the combination of liquid phase and gas phase enters second compressor 70, where the refrigerant is wet compressed and continues the operation as described above. The discharge operation will continue until the heat stored in the first thermal storage unit 38 is depleted or reaches a predetermined level.

[0066] When the second thermal storage unit 50 is fully charged, the second stop valve 84 moves from the open configuration to the closed configuration, inhibiting flow of the refrigerant to the second expansion valve 64. The second bypass discharge valve 82 moves from the closed configuration that directs the refrigerant through the evaporator 22 to receive the heat from the heat source to the open configuration that redirects the refrigerant between the first fluid path 34 and the second fluid path 36 bypassing the evaporator 22 to discharge the heat stored in the second thermal storage unit 50 into the refrigerant before entering the compressor.

[0067] Accordingly, the operation of discharging the second thermal storage unit 50 is the same as the general charging operation described above, but for the following differences. With reference to FIG. 3C, the refrigerant flowing from the third expansion valve 66 in the first fluid path 34 passes through the first line 58 of the second thermal storage unit 50. Upon exiting the second thermal storage unit 50, the second stop valve 84 in the closed configuration and the second bypass discharge valve 82 in the open configuration directs the refrigerant around the second thermal storage unit 50 and re-enters the second thermal storage unit 50 in the second line 60 as part of the second fluid path 36. Because the evaporator 22 was bypassed, heat was not absorbed into the refrigerant. Therefore, the refrigerant is cooler than the phase change material 56 of the second thermal storage unit 50. Heat is transferred from the phase change material 56 the refrigerant causing the refrigerant to phase change at least partially to a gas. The refrigerant in the combination of liquid phase and gas phase enters third compressor 72, where the refrigerant is wet compressed and continues the operation as described above. The discharge operation will continue until the heat stored in the second thermal storage unit 50 is depleted or reaches a predetermined level.

[0068] Although the industrial heat pump 20 described above includes to two thermal storage units, it is contemplated that the industrial heat pump 20 may be configured for use with a single thermal storage unit or multiple thermal storage units in excess of two. Further, in other embodiments the thermal storage unit(s) may be substituted with similar components heat exchange and storage components.

[0069] A method of operating the industrial heat pump 20 will now be described with reference to the description of the industrial heat pump 20 shown in FIGS. 1 and 3A-3B, and theoperation of the industrial heat pump 20 describe above. The method includes transporting the refrigerant through the first fluid path 34 from the output port 32 of the condenser 28, phase changing at least a portion of the refrigerant flowing from the condenser 28 to the evaporator 22 through the first expansion valve 62 from a liquid to a gas, and receiving the refrigerant into the input port 24 of the evaporator 22 from the first fluid path 34. The method further includes transferring the heat into the refrigerant from the heat source with the evaporator 22, expelling the refrigerant through the output port 26 of the evaporator 22 into the second fluid path 36, and receiving and storing heat from the refrigerant in the first thermal storage unit 38.

[0070] The method further includes phase changing at least a portion of the refrigerant from a gas to liquid, wet compressing the refrigerant through the second compressor 70, and phase changing the refrigerant to a gas. The method further includes receiving the refrigerant into the input port 30 of the condenser 28 from the second fluid path 36, transferring the heat out of the refrigerant to the heat sink with the condenser 28, and expelling the refrigerant through the output port 32 of the condenser 28 into the first fluid path 34.

[0071] The method may further include compressing the refrigerant through the first compressor 68 after expelling the refrigerant through the output port 26 of the evaporator 22 into the second fluid path 36. The method may further include moving the first regulator valve 74 between the open configuration and the closed configuration to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the second compressor 70.

[0072] As described above, the first thermal storage unit 38 includes the first line 46 defining a portion of the first fluid path 34 and the second line 48 defining a portion of the second fluid path 36. Therefore, receiving and storing heat from the refrigerant in the first thermal storage unit 38 may be further defined as receiving and storing heat from the refrigerant in the second line 48 in the first thermal storage unit 38. The method may further include receiving and storing heat from the refrigerant in the first line 46 in the first thermal storage unit 38 after transporting the refrigerant through the first fluid path 34 from the output port 32 of the condenser 28.

[0073] The method may further include phase changing at least a portion of the refrigerant flowing from the condenser 28 to the first thermal storage unit 38 through the second expansion valve 64 from a liquid to a gas. In one example, phase changing at least a portion of the refrigerant flowing from the condenser 28 to the first thermal storage unit 38 through the second expansion valve 64 from a liquid to a gas occurs prior to receiving and storing heat from the refrigerant in the first line 46 in the first thermal storage unit 38.

[0074] The method may further include moving the first bypass discharge valve 78 from the closed configuration to the open configuration to discharge the heat stored in the first thermal storage unit 38 into the refrigerant before entering the second compressor 70. The method may further include, and moving the first bypass charge valve 86 from the closed configuration to the open configuration to increase the transfer of heat from the refrigerant into the first thermal storage unit 38.

[0075] The method may further include receiving and storing heat from the refrigerant in the second thermal storage unit 50 and phase changing at least a portion of the refrigerant from a gas to liquid. The method may further include wet compressing the refrigerant through the third compressor 72 and phase changing the refrigerant to a gas.

[0076] The industrial heat pump 20 described herein offers several advantages over other industrial heat pumps. The use of multiple wet compression stages in the industrial heat pump 20 allows for improved energy efficiency. In particular, by wet compressing the refrigerant in stages, the system can achieve higher compression ratios, resulting in higher coefficient of performance and improved performance. Furthermore, the integration of the thermal storage unit(s) allow for the storage of latent heat, enabling energy recovery and later use. Additionally, the industrial heat pump 20 expands the temperature range beyond the typical 90°C-150°C range of most industrial heat pumps by wet compressing the refrigerant. By reaching temperatures of 200°C or higher, the system enables a wider range of industrial processes to benefit from the use of industrial heat pumps. This expansion opens up new possibilities for energy-efficient heating in various industrial applications. Moreover, the storage and discharge of the heat in the thermal storage unit(s) provides for better management of energy consumption and peak demand. For example, one or more of the compressors are shut-off during the discharging operation as they are not utilized. By adjusting the system operation based on demand requirements, the industrial heat pump 20 can optimize energy usage and reduce the strain on the electrical grid during peak periods. Furthermore, the industrial heat pump 20 includes features for efficient utilization of low-grade waste heat. By capturing and utilizing waste heat at various intermediate temperature levels, the system enhances energy efficiency and reduces overall energy consumption.

[0077] It is noted that the terms "substantially" and "about" may be utilized herein to represent the inherent degree of uncertainty that may be attributed to any quantitative comparison, value, measurement, or other representation. These terms are also utilized herein to represent the degree by which a quantitative representation may vary from a stated reference without resulting in a change in the basic function of the subject matter at issue.

[0078] While particular embodiments have been illustrated and described herein, it should be understood that various other changes and modifications may be made without departing from the spirit and scope of the claimed subject matter. Moreover, although various aspects of the claimed subject matter have been described herein, such aspects need not be utilized in combination. It is therefore intended that the appended claims cover all such changes and modifications that are within the scope of the claimed subject matter.

Claims

1. An industrial heat pump for transporting heat with a refrigerant, the industrial heat pump comprising: an evaporator having an input port for receiving the refrigerant and an output port for expelling the refrigerant, wherein the evaporator is configured to transfer the heat into the refrigerant from a heat source; a condenser having an input port for receiving the refrigerant and an output port for expelling the refrigerant, wherein the condenser is configured to transfer the heat out of the refrigerant to a heat sink; a first fluid path extending between the output port of the condenser and the input port of the evaporator; a second fluid path extending between the output port of the evaporator and the input port of the condenser; an expansion valve defining a portion of the first fluid path between the evaporator and the condenser that causes at least a portion of the refrigerant flowing from the condenser to the evaporator to phase change from a liquid to a gas; a thermal storage unit defining a portion of the second fluid path, wherein the thermal storage unit is configured to receive and store heat from the refrigerant in the second fluid path; and a compressor defining a portion of the second fluid path between the thermal storage unit and the condenser, wherein the heat received by the thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the compressor where the refrigerant phase changes to a gas.

2. The industrial heat pump of claim 1, further comprising a first compressor defining a portion of the second fluid path between the evaporator and the thermal storage unit, wherein the compressor is a second compressor.

3. The industrial heat pump of claim 2, further comprising a regulator valve connected to the second fluid path between the first compressor and the second compressor, bypassing the thermal storage unit, wherein the regulator valve is movable between a closed configuration that directs all of the refrigerant from the first compressor through the thermal storage unit, and an open configuration that directs at least a portion of the refrigerant as a gas from the first compressor tothe second compressor to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the second compressor.

4. The industrial heat pump of claim 1, wherein the thermal storage unit comprises a first line defining a portion of the first fluid path and a second line defining a portion of the second fluid path, wherein the thermal storage unit is configured to receive and store heat from the refrigerant in the first fluid path and the second fluid path.

5. The industrial heat pump of claim 4, wherein the expansion valve is a first expansion valve defining a portion of the first fluid path between the evaporator and the thermal storage unit, and the industrial heat pump further comprises a second expansion valve defining a portion of the first fluid path between the thermal storage unit and the condenser, wherein each of the first expansion valve and the second expansion valve causes at least a portion of the refrigerant to phase change from a liquid to a gas before the refrigerant enters the thermal storage unit and the evaporator, respectively.

6. The industrial heat pump of claim 4, further comprising a bypass discharge valve fluidically coupled to both the first fluid path between the thermal storage unit and the evaporator and the second fluid path between the thermal storage unit and the evaporator, wherein the bypass discharge valve is movable between a closed configuration that directs the refrigerant through the evaporator to receive the heat from the heat source, and an open configuration that redirects at least a portion of the refrigerant between the first fluid path and the second fluid path bypassing the evaporator to discharge the heat stored in the thermal storage unit into the refrigerant before entering the compressor.

7. The industrial heat pump of claim 4, wherein the thermal storage unit comprises a housing defining an interior for holding a phase change material, wherein the first line and the second line are disposed within the interior and contact the phase change material to cause heat transfer between the refrigerant and the phase change material.

8. The industrial heat pump of claim 7, wherein both of the first line and the second line are coiled within the interior of the housing.

9. The industrial heat pump of claim 7, further comprising a bypass charge valve fluidically coupled to each of the first line and the second line of the thermal storage unit and movable between a closed configuration that separates the first line and the second line to direct all of the refrigerant through the condenser, and an open configuration that connects the first line and the second line to reduce flow of the refrigerant to the condenser and increase the transfer of heat from the refrigerant into the phase change material for storage in the thermal storage unit.

10. The industrial heat pump of claim 2, further comprising: a second thermal storage unit defining a portion of the second fluid path between the second compressor and the condenser, wherein the second thermal storage unit is configured to receive and store heat from the refrigerant in the second fluid path; and a third compressor defining a portion of the second fluid path between the second thermal storage unit and the condenser, wherein the heat received by the second thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the third compressor and a phase change of the refrigerant to a gas.

11. An industrial heat pump for transporting heat with a refrigerant, the industrial heat pump comprising: an evaporator having an input port for receiving the refrigerant and an output port for expelling the refrigerant, wherein the evaporator is configured to transfer the heat into the refrigerant from a heat source; a condenser having an input port for receiving the refrigerant and an output port for expelling the refrigerant, wherein the condenser is configured to transfer the heat out of the refrigerant to a heat sink; a first fluid path extending between the output port of the condenser and the input port of the evaporator; a second fluid path extending between the output port of the evaporator and the input port of the condenser; a first thermal storage unit defining a portion of the first fluid path and a portion of the second fluid path, wherein the first thermal storage unit is configured to receive and store heat from the refrigerant in the first fluid path and from the refrigerant in the second fluid path;a second thermal storage unit defining a portion of the first fluid path between the first thermal storage unit and the condenser and a portion of the second fluid path between the first thermal storage unit and the condenser, wherein the second thermal storage unit is configured to receive and store heat from the refrigerant in the first fluid path and from the refrigerant in the second fluid path; a first expansion valve defining a portion of the first fluid path between the evaporator and the first thermal storage unit that causes at least a portion of the refrigerant flowing from the first thermal storage unit to the evaporator to phase change from a liquid to a gas; a second expansion valve defining a portion of the first fluid path between the first thermal storage unit and the second thermal storage unit that causes at least a portion of the refrigerant flowing from the second thermal storage unit to the first thermal storage unit to phase change from a liquid to a gas; a third expansion valve defining a portion of the first fluid path between the second thermal storage unit and the condenser that causes at least a portion of the refrigerant flowing from the condenser to the second thermal storage unit to phase change from a liquid to a gas; a first compressor defining a portion of the second fluid path between the evaporator and the first thermal storage unit; a second compressor defining a portion of the second fluid path between the first thermal storage unit and the second thermal storage unit, wherein the heat received by the first thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the second compressor where the refrigerant phase changes to a gas; and a third compressor defining a portion of the second fluid path between the second thermal storage unit and the condenser, wherein the heat received by the second thermal storage unit causes a portion of the refrigerant to phase change from a gas to a liquid allowing for wet compression of the refrigerant through the third compressor where the refrigerant phase changes to a gas.

12. The industrial heat pump of claim 11, further comprising a first regulator valve connected to the second fluid path between the first compressor and the second compressor, bypassing the first thermal storage unit, wherein the first regulator valve is movable between a closed configuration that directs all of the refrigerant from the first compressor through the first thermal storage unit, and an open configuration that directs at least a portion of the refrigerant as a gasfrom the first compressor to the second compressor to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the second compressor.

13. The industrial heat pump of claim 12, further comprising a second regulator valve connected to the second fluid path between the second compressor and the third compressor, bypassing the second thermal storage unit, wherein the second regulator valve is movable between a closed configuration that directs all of the refrigerant from the second compressor through the second thermal storage unit, and an open configuration that directs at least a portion of the refrigerant as a gas from the second compressor to the third compressor to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the third compressor.

14. The industrial heat pump of claim 11, further comprising a first bypass discharge valve fluidically coupled to both the first fluid path between the first thermal storage unit and the evaporator and the second fluid path between the first thermal storage unit and the evaporator, wherein the first bypass discharge valve is movable between a closed configuration that directs the refrigerant through the evaporator to receive the heat from the heat source, and an open configuration that redirects at least a portion of the refrigerant between the first fluid path and the second fluid path bypassing the evaporator to discharge the heat stored in the first thermal storage unit into the refrigerant before entering the compressor.

15. A method of operating an industrial heat pump comprising an evaporator having an input port and an output port, a condenser having an input port and an output port, a first fluid path extending between the output port of the condenser and the input port of the evaporator, a second fluid path extending between the output port of the evaporator and the input port of the condenser, an expansion valve defining a portion of the first fluid path between the evaporator and the condenser, a thermal storage unit defining a portion of the second fluid path, and a compressor defining a portion of the second fluid path between the thermal storage unit and the condenser, the method comprising: transporting the refrigerant through the first fluid path from the output port of the condenser; phase changing at least a portion of the refrigerant flowing from the condenser to the evaporator through the expansion valve from a liquid to a gas; receiving the refrigerant into the input port of the evaporator from the first fluid path;transferring the heat into the refrigerant from a heat source with the evaporator; expelling the refrigerant through the output port of the evaporator into the second fluid path; receiving and storing heat from the refrigerant in the thermal storage unit; phase changing at least a portion of the refrigerant from a gas to liquid; wet compressing the refrigerant through the compressor; phase changing the refrigerant to a gas; receiving the refrigerant into the input port of the condenser from the second fluid path; transferring the heat out of the refrigerant to a heat sink with the condenser; and expelling the refrigerant through the output port of the condenser into the first fluid path.

16. The method of claim 15, wherein the industrial heat pump further comprises a first compressor defining a portion of the second fluid path between the evaporator and the thermal storage unit and wherein the compressor is further defined as a second compressor, the method further comprising: compressing the refrigerant with the first compressor after expelling the refrigerant through the output port of the evaporator into the second fluid path.

17. The method of claim 16, wherein the industrial heat pump further comprises a regulator valve connected to the second fluid path between the first compressor and the second compressor bypassing the thermal storage unit, wherein the regulator valve is movable between a closed configuration that directs all of the refrigerant from the first compressor through the thermal storage unit and an open configuration that directs at least a portion of the refrigerant as a gas from the first compressor to the second compressor, the method further comprising: moving the regulator valve between the open configuration and the closed configuration to regulate the proportion of gaseous refrigerant to liquid refrigerant that enters the second compressor.

18. The method of claim 15, wherein the thermal storage unit comprises a first line defining a portion of the first fluid path and a second line defining a portion of the second fluid path, wherein receiving and storing heat from the refrigerant in the thermal storage unit comprises receiving and storing heat from the refrigerant in the second line in the thermal storage unit; the method further comprising:receiving and storing heat from the refrigerant in the first line with the thermal storage unit after transporting the refrigerant through the first fluid path from the output port of the condenser.

19. The method of claim 18, wherein the expansion valve is further defined as a first expansion valve defining a portion of the first fluid path between the evaporator and the thermal storage unit, and the industrial heat pump further comprises a second expansion valve defining a portion of the first fluid path between the thermal storage unit and the condenser, wherein phase changing at least a portion of the refrigerant flowing from the condenser to the evaporator through the expansion valve from a liquid to a gas comprises phase changing at least a portion of the refrigerant flowing from the thermal storage unit to the evaporator through the first expansion valve from a liquid to a gas; the method further comprising: phase changing at least a portion of the refrigerant flowing from the condenser to the thermal storage unit through the second expansion valve from a liquid to a gas.

20. The method of claim 19, wherein phase changing at least a portion of the refrigerant flowing from the condenser to the thermal storage unit through the second expansion valve from a liquid to a gas occurs prior to receiving and storing heat from the refrigerant in the first line in the thermal storage unit.

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