Heat pump waste heat treatment system, method, apparatus, and storage medium

Abstract

The application relates to the technical field of heat pump control, and discloses a heat pump waste heat treatment system, method, device and storage medium, which are used for solving the problems that in a traditional scheme, a refrigerant pipeline is complex to lay, the refrigerant in the pipeline is insufficient in heat recovery and utilization, the waste heat utilization rate of a heat pump system is low, and the heat pump system consumes a large amount of energy. The heat pump waste heat treatment method system comprises a waste heat step recovery subsystem, a compressor, a waste heat step utilization subsystem, at least one cooling flow channel and one heating flow channel. The waste heat step recovery subsystem is used for sequentially guiding refrigerant to flow through the at least two pressure reduction and evaporation units to recover the heat of a to-be-cooled fluid in the at least one cooling flow channel. The compressor is used for compressing low-pressure superheated refrigerant after the heat recovery of the to-be-cooled fluid is completed. The waste heat step utilization subsystem is used for sequentially guiding high-pressure superheated refrigerant compressed by the compressor to flow through the at least two condensing units to heat a to-be-heated fluid in the heating flow channel.

Description

Technical Field

[0001] The present application relates to the field of heat pump control technology, and in particular to a heat pump waste heat treatment system, method, device and storage medium. Background Art

[0002] In the field of industrial waste heat recovery and heating applications, the recovery and utilization of waste heat (including sensible heat and latent heat) can save energy, improve the overall efficiency of the system, and reduce operating costs. For example, heat pump control systems are used in industry, commercial buildings and residences. The exhaust fluid (such as exhaust air or water) often contains a large amount of heat. Through heat recovery technology, this part of the waste heat can be collected and used to preheat the incoming fluid, that is, the fluid to be treated (such as fresh air, or water), thereby reducing the energy consumption required to heat the incoming fluid.

[0003] In traditional waste heat recovery solutions, the discharge pipe and the inlet pipe are relatively independent, and the risk of waste heat recovery in the discharge pipe is high. The refrigerant pipe laying is too complicated, and the refrigerant in the refrigerant pipe does not fully recover and utilize the heat. As a result, the cost of traditional waste heat recovery and utilization solutions is too high, the waste heat utilization rate of the heat pump system is low, and the energy consumption of the heat pump system cannot be effectively reduced. Summary of the Invention

[0004] The present application provides a heat pump waste heat treatment system, method, device and storage medium, which are used to solve the problems of complex refrigerant pipeline laying in traditional waste heat recovery solutions, insufficient heat recovery and utilization of refrigerant in the refrigerant pipeline, resulting in low waste heat utilization rate of the heat pump system and inability to effectively reduce the energy consumption of the heat pump system.

[0005] In a first aspect, the present application provides a heat pump waste heat treatment system, comprising: a waste heat cascade recovery subsystem provided with at least two pressure-reducing evaporation units, a compressor, a waste heat cascade utilization subsystem provided with at least two condensing units, at least one cooling channel, and a heating channel; wherein the waste heat cascade recovery subsystem is provided in the at least one cooling channel, and the waste heat cascade utilization subsystem is provided in the heating channel; the waste heat cascade recovery subsystem is used to sequentially flow a refrigerant through the at least two pressure-reducing evaporation units to recover heat from a fluid to be cooled in the at least one cooling channel; the compressor is used to compress the low-pressure superheated refrigerant that has recovered heat from the fluid to be cooled;

[0006] The waste heat cascade utilization subsystem is used to direct the high-pressure superheated refrigerant compressed by the compressor through the at least two condensing units in sequence to heat the fluid to be heated in the heating flow channel, and to guide the refrigerant that has completed the heating of the fluid to be heated to the waste heat cascade recovery subsystem.

[0007] A second aspect of the present application provides a heat pump waste heat treatment method, which is applied to the above-mentioned heat pump waste heat treatment system. The heat pump waste heat treatment method includes: obtaining the actual temperature of the discharged fluid in the heating flow channel; judging whether the actual temperature is equal to the preset target temperature; if so, controlling the heat pump waste heat treatment system to maintain the current operating state; if not, controlling the compressor and / or the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature.

[0008] The third aspect of the present application provides a heat pump waste heat treatment device, which is applied to the above-mentioned heat pump waste heat treatment system. The heat pump waste heat treatment device includes: an acquisition module, which is used to obtain the actual temperature of the discharged fluid in the heating flow channel; a judgment module, which is used to judge whether the actual temperature is equal to the preset target temperature; a maintenance module, which is used to control the heat pump waste heat treatment system to maintain the current operating state if so; and an adjustment module, which is used to control the compressor and / or the waste heat step utilization subsystem to adjust parameters if not, so that the actual temperature is equal to the target temperature.

[0009] A fourth aspect of the present application provides a computer-readable storage medium, wherein the computer-readable storage medium stores instructions, which, when executed on a computer, enable the computer to execute the above-mentioned heat pump waste heat treatment method.

[0010] In the technical solution provided by the present application, the waste heat cascade recovery subsystem uses the refrigerant to flow through the at least two pressure-reducing evaporation units in sequence to recover the heat of the fluid to be cooled in the at least one cooling channel, thereby realizing the gradient recovery of the heat of the refrigerant to be cooled. The refrigerant after heat recovery is compressed by the compressor to provide power for the circulation of the refrigerant pipeline. The waste heat cascade utilization subsystem uses the high-pressure superheated refrigerant compressed by the compressor to flow through the at least two condensing units in sequence to heat the fluid to be heated in the heating channel, thereby realizing the gradient heating of the refrigerant to be heated. The refrigerant circulation loop is constructed through the above-mentioned setting, which reduces the difficulty and cost of laying the refrigerant pipeline, improves the heat recovery rate and utilization rate of the refrigerant, improves the waste heat utilization rate of the heat pump system, and reduces the energy consumption of the heat pump system. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] In order to more clearly illustrate the technical solution of the present application, the following is a brief introduction to the drawings required for use in the embodiments or descriptions of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without any creative work.

[0012] Figure 1 This is a schematic diagram of an embodiment of a heat pump waste heat treatment system in this application;

[0013] Figure 2 This is a schematic diagram of another embodiment of the heat pump waste heat treatment system in this application;

[0014] Figure 3 Schematic diagram of the pressure-enthalpy characteristics of the refrigerant in this application;

[0015] Figure 4 This is a schematic diagram of another embodiment of the heat pump waste heat treatment system in this application;

[0016] Figure 5 This is a schematic diagram of an embodiment of the heat pump waste heat treatment method in this application;

[0017] Figure 6 This is a schematic diagram of another embodiment of the heat pump waste heat treatment method in this application;

[0018] Figure 7 This is a schematic diagram of an embodiment of a heat pump waste heat treatment device in this application;

[0019] Figure 8 This is a schematic diagram of another embodiment of the heat pump waste heat treatment device in this application;

[0020] Figure 9 This is a schematic diagram of an embodiment of the heat pump waste heat treatment equipment in this application.

[0021] Description of Figure Numbers:

[0022] Label name Label name 100 Heat pump waste heat treatment system 113a The first water heat exchange unit 110 Waste heat cascade recovery subsystem 113a1 First water tank 120 compressor 113a2 First water pump 130 Waste heat cascade utilization subsystem 113a3 The first heat exchange mechanism 140 Cooling channels 113b Second water heat exchange unit 150 Heating channel 131 Condensing unit 111 Pressure reduction evaporation unit 131a First condensing unit 111a The first pressure-reducing evaporation unit 131b Second condensing unit 111a1 First throttle valve 132 Auxiliary heating equipment 111a2 First evaporator 133 Refrigerant pipeline regulating valve 111b Second pressure reduction evaporation unit 134 Diversion unit 112 Flash Tank 1341 Flow channel bypass valve 113 Water heat exchange unit 1342 Isolation Agency DETAILED DESCRIPTION

[0023] The present application provides a heat pump waste heat treatment system, method, device and storage medium, which are used to solve the problems of complex refrigerant pipeline laying in traditional waste heat recovery solutions, insufficient heat recovery and utilization of refrigerant in the refrigerant pipeline, resulting in low waste heat utilization rate of the heat pump system and inability to effectively reduce the energy consumption of the heat pump system.

[0024] The following will provide a clear and complete description of the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0025] It should be noted that all directional indications such as up, down, left, right, front, back, etc. in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the various components in a certain specific posture as shown in the accompanying drawings. If the specific posture changes, the directional indication will also change accordingly.

[0026] The terms "first," "second," "third," "fourth," and the like (if any) in the specification and claims of this application and in the accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a particular order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate so that the embodiments described herein can be implemented in an order other than that illustrated or described herein. In addition, the terms "including" or "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product, or apparatus comprising a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0027] See also Figure 1-2 In one embodiment of the heat pump waste heat treatment system 100 of the present application, the waste heat cascade recovery subsystem 110 includes at least two pressure-reducing evaporation units, a compressor 120, a waste heat cascade utilization subsystem 130 includes at least two condensing units, at least one cooling channel 140, and a heating channel 150. The waste heat cascade recovery subsystem 110 is disposed in at least one cooling channel 140, and the waste heat cascade utilization subsystem 130 is disposed in the heating channel 150.

[0028] The waste heat cascade recovery subsystem 110 is used to flow the refrigerant through at least two pressure-reducing evaporation units in sequence (such as 111a and 111b in the figure) to recover the heat of the fluid to be cooled in at least one cooling channel 140;

[0029] The compressor 120 is used to compress the low-pressure superheated refrigerant that has completed heat recovery of the fluid to be cooled;

[0030] The waste heat cascade utilization subsystem 130 is used to direct the high-pressure superheated refrigerant compressed by the compressor 120 through at least two condensing units (such as 131a and 131b in the figure) in sequence to heat the fluid to be heated in the heating channel, and to guide the refrigerant that has completed heating the fluid to be heated to the waste heat cascade recovery subsystem 110.

[0031] This embodiment realizes the gradient recovery of heat by at least two pressure-reducing evaporation units connected in series. If only one cooling channel is included, at least two pressure-reducing evaporation units are sequentially arranged in the cooling channel along the flow direction of the fluid. Any two pressure-reducing evaporation units are at a certain distance from each other, such as Figure 1 If it includes two or more cooling channels, each cooling channel is provided with at least one pressure-reducing evaporation unit, for example, a cooling channel is provided with a pressure-reducing evaporation unit, such as Figure 2 shown.

[0032] For ease of understanding, combined Figure 1The heat recovery and utilization process of the fluid in the heat pump waste heat treatment system is explained, wherein, the heat recovery process: the hollow arrow in the cooling channel 140 is the flow direction of the fluid to be cooled, and the temperature of the fluid to be cooled at the inlet side of the cooling channel 140 is the highest (first temperature). The fluid to be cooled will first pass through the first pressure-reducing evaporation unit 111a for the first waste heat recovery, and the fluid to be cooled will be cooled to the second temperature, and then pass through the second pressure-reducing evaporation unit 111b for the second waste heat recovery, and the fluid to be cooled will be further cooled to the third temperature. The temperatures are sorted from large to small as follows: first temperature, second temperature, and third temperature, wherein the first temperature is the actual temperature of the fluid to be cooled discharged from the heat pump system, such as exhaust gas or wastewater and other discharged fluids, and the specific values ​​of the second temperature and the third temperature are related to the distance between the first pressure-reducing evaporation unit 111a and the second pressure-reducing evaporation unit 111b, the heat exchange capacity of the two pressure-reducing evaporation units, and the characteristics of the refrigerant in the refrigerant pipeline.

[0033] Among them, the heat utilization process: the hollow arrow in the heating channel 150 is the flow direction of the fluid to be heated, and the temperature of the fluid to be heated at the inlet side of the heating channel 150 is the lowest (the fourth temperature). The fluid to be heated will first pass through the second condensing unit 131b for the first heating, and the fluid to be heated will be heated to the fifth temperature, and then pass through the first condensing unit 131a for the second heating, and the fluid to be heated will be further heated to the sixth temperature. The temperatures are sorted from small to large as follows: the fourth temperature, the fifth temperature, and the sixth temperature, wherein the fourth temperature is the actual temperature of the fluid to be heated before treatment, such as fresh air or incoming water waiting to be treated fluid, and the specific values ​​of the fifth temperature and the sixth temperature are related to the distance between the first condensing unit 131a and the second condensing unit 131b, the heat exchange capacity of the two condensing units, and the characteristics of the refrigerant in the refrigerant pipeline.

[0034] Optional, Figure 1 The heat pump waste heat treatment system 100 may further include a flash tank 112 disposed between the first pressure-reducing evaporation unit 111a and the second pressure-reducing evaporation unit 111b. The flash tank 112 flashes and separates the refrigerant remaining from the first pressure-reducing evaporation unit 111a, and directs the gaseous refrigerant to the compressor 120 for air supply and enthalpy increase, while directing the liquid refrigerant to the second pressure-reducing evaporation unit 111b for a second waste heat recovery. This embodiment achieves gas-liquid separation and air supply and enthalpy increase through the flash tank, ensuring that the refrigerant entering the second pressure-reducing evaporation unit is liquid, improving the heat exchange stability of the second pressure-reducing evaporation unit, and enhancing the performance of the compressor.

[0035] It can be understood that the heating flow channel is a flow channel through which the fluid that needs to be heated to the target temperature circulates, wherein the circulating fluid to be heated can be fresh air, that is, air to be heated, or water to be heated, or other fluids for user use; and the cooling flow channel is a flow channel that requires heat recovery, such as an exhaust pipe or a drain pipe, wherein the circulating fluid to be cooled can be exhaust gas, that is, air to be cooled, or wastewater, water to be cooled, or other fluids.

[0036] If there is only one cooling channel, two or more pressure-reducing evaporation units are provided for the cooling channel, wherein the number of pressure-reducing evaporation units can be selected according to actual conditions;

[0037] If there are two cooling channels, each cooling channel is provided with at least one pressure-reducing evaporation unit. The number of pressure-reducing evaporation units in each cooling channel can be selected according to actual conditions. If there are two or more pressure-reducing evaporation units in the same cooling channel, the relative positions of any two adjacent pressure-reducing evaporation units in the cooling channel are calculated based on the refrigerant properties and heat exchange capacity in the refrigerant pipeline to ensure that the relative upstream temperature before passing through the previous pressure-reducing evaporation unit, the relative midstream temperature between the previous pressure-reducing evaporation unit and the next pressure-reducing evaporation unit, and the relative downstream temperature after the next pressure-reducing evaporation unit present an appropriate temperature gradient range to achieve gradient waste heat recovery.

[0038] Similarly, at least two condensing units are provided in the heating flow channel, wherein the number of condensing units can be selected according to actual conditions, and the relative positions of any two adjacent condensing units in the heating flow channel are calculated based on the refrigerant properties and heat exchange capacity in the refrigerant pipeline to ensure that the relative upstream temperature before passing through the previous condensing unit, the relative midstream temperature between the previous condensing unit and the next condensing unit, and the relative downstream temperature after the next condensing unit present an appropriate temperature gradient range to achieve gradient heating.

[0039] In this embodiment, the waste heat cascade recovery subsystem uses the refrigerant to flow through at least two pressure-reducing evaporation units in sequence to recover the heat of the fluid to be cooled in at least one cooling channel, thereby realizing the gradient recovery of the heat of the fluid to be cooled by the refrigerant. The refrigerant that has recovered the heat is compressed by the compressor to provide power for the circulation of the refrigerant pipeline. The waste heat cascade utilization subsystem uses the high-pressure superheated refrigerant compressed by the compressor to flow through at least two condensing units in sequence to heat the fluid to be heated in the heating channel, thereby realizing the gradient heating of the fluid to be heated by the refrigerant. The refrigerant circulation loop is constructed through the above-mentioned settings, which reduces the difficulty and cost of laying the refrigerant pipeline, improves the heat recovery rate and utilization rate of the refrigerant, improves the waste heat utilization rate of the heat pump system, and reduces the energy consumption of the heat pump system.

[0040] In practical applications, there is a need to recover waste heat from multiple independent flow channels with different temperatures. The temperature of the discharged fluid in the heating channel is related to the user's comfort. The recovered heat may exceed the required heat demand of the fluid to be heated, that is, there is too much waste heat; the recovered heat may not meet the required heat demand of the fluid to be heated, that is, there is too little waste heat, etc. In order to meet the above requirements, refer to Figure 2 This embodiment takes two independent cooling channels as an example to provide another embodiment of a heat pump waste heat treatment system:

[0041] The heat pump waste heat treatment system of this embodiment includes two independent cooling channels, wherein the temperature of the first fluid in the first cooling channel 141 is greater than the temperature of the second fluid in the second cooling channel 142;

[0042] The waste heat cascade recovery subsystem 110 includes two pressure-reducing evaporation units 111 and a flash tank 112 , wherein the first pressure-reducing evaporation unit 111 a is used to recover the heat of the first fluid in the first cooling channel 141 ;

[0043] The flash tank 112 is used to separate the refrigerant used to recover the heat of the first fluid into gas and liquid, and to use the gaseous refrigerant to inject heat into the compressor 120;

[0044] The second pressure-reducing evaporation unit 111b recovers the heat of the second fluid in the second cooling channel 142 using the liquid refrigerant separated by the flash tank 112 , and guides the low-pressure superheated refrigerant that recovers the heat of the first fluid and the heat of the second fluid to the compressor 120 .

[0045] Optionally, each pressure-reducing evaporation unit includes a throttle valve and an evaporator connected in series, wherein the throttle valve is used to throttle and reduce the pressure of the refrigerant flowing through it; the evaporator uses the low-pressure refrigerant, after throttling and reducing the pressure of the throttle valve, to recover heat from the fluid to be cooled in at least one cooling channel. Specifically, the first pressure-reducing evaporation unit 111a includes a first throttle valve 111a1 and a first evaporator 111a2, and the second pressure-reducing evaporation unit 111b includes a second throttle valve and a second evaporator. The first evaporator recovers waste heat from the first fluid in the first cooling channel, while the second evaporator recovers waste heat from the second fluid in the second cooling channel.

[0046] Specifically, the refrigerant outlet of the waste heat cascade utilization subsystem 130 is connected to the refrigerant inlet of the first throttle valve 111a1, which is in communication with the refrigerant inlet of the first evaporator 111a2, which is in communication with the refrigerant inlet of the first evaporator 111a2, which is in communication with the refrigerant inlet of the flash tank 112, which is in communication with the refrigerant inlet of the second throttle valve. The refrigerant outlet of the second throttle valve is in communication with the refrigerant inlet of the second evaporator, which is in communication with the refrigerant inlet of the compressor. This embodiment achieves gas-liquid separation and gas replenishment and enthalpy increase through the flash tank, ensuring that the refrigerant entering the second throttle valve is liquid, and avoiding air blockage or intermittent throttling during the throttling process of the second throttle valve, which would cause fluctuations in the refrigerant flow entering the second evaporator for heat exchange and affect heat exchange stability.

[0047] Optionally, the waste heat cascade utilization subsystem 130 includes two condensing units connected in series, wherein the first condensing unit 131a is disposed in a flow channel region close to the outlet side of the heating flow channel, and the second condensing unit 131b is disposed in a flow channel region close to the inlet side of the heating flow channel;

[0048] The refrigerant outlet of the compressor is connected to the refrigerant inlet of the first condensing unit, the refrigerant outlet of the first condensing unit is connected to the refrigerant inlet of the second condensing unit, and the refrigerant outlet of the second condensing unit is connected to the refrigerant inlet of the waste heat cascade utilization subsystem.

[0049] Optionally, the heat pump waste heat treatment system further includes a diversion unit 134, which is disposed in the target flow channel region of the heating flow channel where the waste heat cascade utilization subsystem 130 is installed. The diversion unit is used to divide the target flow channel region into a mutually isolated bypass region and a heating region, and to control the on / off state of the bypass region. The waste heat cascade utilization subsystem is disposed in the heating region. In this embodiment, the diversion unit is used to divert fluid from the target flow channel region of the heating flow channel, thereby adjusting the fluid flow rate in the heating region and the non-heating region (i.e., the bypass region), thereby regulating the temperature of the discharged fluid.

[0050] Optionally, the waste heat cascade utilization subsystem also includes an auxiliary heating device 132, which is disposed in the flow channel region near the outlet of the heating channel. The first condensing unit 131a is disposed in the flow channel region between the auxiliary heating device 132 and the second condensing unit 131b. The auxiliary heating device 132 is used to provide auxiliary heating to the fluid to be heated in the heating channel. In this embodiment, even if the heat recovered by the auxiliary heating device does not meet the required heat requirement of the fluid to be heated, auxiliary heating is performed to raise the temperature of the fluid discharged from the heating channel to a set target temperature.

[0051] Optionally, the diversion unit 134 includes a flow channel bypass valve 1341 and an isolation mechanism 1342, the isolation mechanism 1342 is used to divide the flow channel area into a bypass area and a target heating area isolated from each other, wherein a heating device is provided in the target heating area, such as an auxiliary heating device is provided in the target heating area, and for another example, at least one condensing unit and an auxiliary heating device are provided in the target heating area, Figure 2 An auxiliary heating device 132 and a first condensing unit 131a are installed in the target heating area. The diversion unit 134 allows the heated fluid to bypass the auxiliary heating device 132 and the first condensing unit 131a and flow out from the bypass area only after being heated by the second condensing unit 131b.

[0052] It can be understood that after the flow channel bypass valve 1341 is opened, the wind resistance / water resistance of the target heating area where the first condensing unit 131a and the auxiliary heating device 132 are located is larger than that of the bypass area. Therefore, most of the fluid flows through the bypass valve flow channel, thereby isolating the auxiliary heating device 132 and the first condensing unit 131a, thereby achieving a temperature drop in the fluid discharged from the heating flow channel, and the opening degree of the flow channel bypass valve 1341 is positively correlated with the cooling trend.

[0053] Optionally, the waste heat cascade utilization subsystem 130 includes a refrigerant pipeline regulating valve 133, which is used to regulate the refrigerant flow passing through the second condensing unit 131b.

[0054] Specifically, the refrigerant pipeline regulating valve 133 and the second condensing unit 131b are arranged in parallel between the first condensing unit 131a and the waste heat cascade recovery subsystem. For example, the refrigerant pipeline regulating valve is a fluorine bypass valve, and the condensing unit is a condenser, that is, a condensing heat exchanger. The refrigerant inlet of the fluorine bypass valve is connected to the refrigerant pipeline between the first condenser and the second condenser, and the refrigerant outlet of the fluorine bypass valve is connected to the refrigerant pipeline between the second condenser and the first throttle valve. When the fluorine bypass valve is opened, the refrigerant flow rate flowing through the second condenser decreases, which can reduce the heat exchange capacity of the second condenser, so that the above-mentioned fifth temperature decreases.

[0055] In this embodiment, the waste heat cascade recovery subsystem, the compressor and the waste heat cascade utilization subsystem are connected in series in sequence through a refrigerant pipeline. The refrigerant circulating in the refrigerant pipeline can be a conventional refrigerant or a high-boiling-point refrigerant. Among them, the conventional refrigerant can be a refrigerant code-named R134a, whose main component is tetrafluoroethane; a refrigerant code-named R22, whose main component is difluorochloromethane; a refrigerant code-named R290, whose main component is propane; the above-mentioned high-boiling-point refrigerant can be any high-boiling-point refrigerant with a maximum heating temperature between 80°C and 150°C, for example, The refrigerant code-named R245fa, whose main component is 1,1,1,3,3-pentafluoropropane; the refrigerant code-named R515B, which is a mixture of the refrigerant code-named R1234ze(E) and the refrigerant code-named R227ea; the refrigerant code-named R1234ze(E), whose main component is cis-1,3,3,3-tetrafluoropropene; the refrigerant code-named R1233zd, whose main component is any one of the high-boiling-point refrigerants such as 1-chloro-3,3,3-trifluoropropene refrigerant, or other high-boiling-point refrigerants, are not specifically limited in this embodiment.

[0056] The heat pump waste heat treatment system of the present application utilizes high boiling point refrigerant to improve the COP value of the system as a whole. According to the characteristics of high boiling point refrigerant, the higher the condensation temperature, the more rapidly the two-phase region capacity that can be utilized will be reduced. Figure 3 Schematic diagram of refrigerant pressure-enthalpy characteristics, Figure 3 (a) Figure 1 shows the pressure-enthalpy characteristics of high boiling point refrigerant. Figure 3 Figure (b) shows the pressure-enthalpy characteristics of conventional refrigerants. Based on the pressure-enthalpy characteristics of the two refrigerants, the COP value of the heat pump waste heat treatment system can be effectively improved. Compared with conventional refrigerants, this characteristic makes the COP value of the high-temperature heat pump using high-boiling-point refrigerant lower when the exhaust superheat is lower than that of conventional refrigerants. When there are sufficient waste heat resources, making full use of the heat in the subcooling section can effectively improve the overall COP value of the high-temperature heat pump.

[0057] Through experiments, it was found that by adjusting the equipment position and / or corresponding operating parameters of the heat pump waste heat treatment system, the evaporation temperature of the refrigerant in the second evaporation unit can be controlled to 30°C, the refrigerant temperature entering the compressor through the refrigerant pipeline can be controlled to 35°C, and the condensation temperature of the refrigerant in the first refrigerant unit can be controlled to 90°C. After condensation, the refrigerant temperature at the outlet of the first condensation unit is 85°C, and the condensate further enters the second condensation unit for condensation. The refrigerant temperature at the refrigerant outlet of the second condensation unit (supercooling temperature) is 60°C.

[0058] Under the above control, the conventional refrigerant code-named R134a has a compressor exhaust temperature of 101°C in the heat pump waste heat treatment system of this embodiment, and a theoretical COP value of 5.54, while the high-boiling-point refrigerant code-named R245fa has a compressor exhaust temperature of 90°C in the heat pump waste heat treatment system of this embodiment, and a theoretical COP value of 5.87, while the high-boiling-point refrigerant code-named R1233zd has a compressor exhaust temperature of 94°C in the heat pump waste heat treatment system of this embodiment, and a theoretical COP value of 5.62. The COP of the heat pump waste heat treatment system of this embodiment with high-boiling-point refrigerant is higher than that of the conventional refrigerant.

[0059] Furthermore, in a conventional heat recovery system, if a waste heat treatment circulation loop is constructed using only a compressor-condenser-throttle valve-evaporator, under the same parameter control as above, the theoretical COP value of the high-boiling-point refrigerant code-named R245fa in the conventional system is only 4.70. The heat pump waste heat treatment system of this embodiment increases the theoretical COP value by nearly 25%, while the theoretical COP value of the high-boiling-point refrigerant code-named R1233zd in the conventional system is only 4.09. The heat pump waste heat treatment system of this embodiment increases the theoretical COP value by nearly 37%. Under the same refrigerant, the heat pump waste heat treatment system of this embodiment can effectively improve the COP compared with the conventional system, thereby maximizing the role of the refrigerant.

[0060] by Figure 3 The system pressure-enthalpy characteristic diagram shown in Figure (c) illustrates the refrigerant state change process in this embodiment:

[0061] (1) The refrigerant in the first evaporator absorbs waste heat from the first cooling channel with a higher temperature and evaporates (the refrigerant changes from state E to state F). During this process, the refrigerant dryness increases, and the refrigerant evaporates from a low-dryness gas-liquid mixture state at medium temperature and medium pressure to a high-dryness gas-liquid mixture state;

[0062] The refrigerant dryness refers to the ratio between the mass of the steam part and the total mass when the refrigerant is in the wet saturated steam state in the refrigeration system;

[0063] (2) After the refrigerant in the high-dryness gas-liquid mixed state (F state) enters the flash tank, gas-liquid separation occurs. The gaseous refrigerant enters the compressor enthalpy increase tube (the refrigerant changes from F state to H state) and is replenished to the compressor to do work; the liquid refrigerant is further throttled through the second throttle valve and enters the second evaporator (the refrigerant changes from F state to G state). The liquid refrigerant is throttled to a gas-liquid mixed state with low temperature, low pressure and low dryness;

[0064] (3) The refrigerant in the second evaporator absorbs the residual heat from the second cooling channel with a lower temperature and evaporates (the refrigerant changes from state G to state A). In this process, the refrigerant dryness increases, and the refrigerant evaporates again from a low-dryness gas-liquid mixed state at low temperature and low pressure to a high-dryness gas-liquid mixed state;

[0065] (4) The low-pressure, superheated refrigerant enters the compressor and is compressed. It is mixed with the medium-pressure, medium-temperature gaseous refrigerant to reach the H state, and is finally compressed to the high-pressure, superheated state (B state).

[0066] (5) After the high-pressure superheated refrigerant enters the first condenser, it heats the fluid to be heated. The refrigerant releases heat and condenses from the high-pressure superheated gaseous state to the high-pressure subcooled liquid state (the refrigerant changes from state B to state C). At the same time, the heated fluid is heated and becomes a high-temperature fluid of the required temperature and is sent to the place where it is needed;

[0067] (6) The high-pressure subcooled liquid refrigerant coming out of the first condenser enters the second condenser for further subcooling (the refrigerant changes from state C to state D). The further subcooled liquid refrigerant heats the low-temperature heated fluid, turning the low-temperature fluid into a fluid of intermediate temperature;

[0068] Intermediate temperature refers to the fluid temperature between the low temperature and the required high temperature;

[0069] (7) The further subcooled liquid refrigerant is throttled by the first throttle valve and becomes a medium-temperature, medium-pressure, low-dryness gas-liquid mixed state (the refrigerant changes from state D to state E), and then enters the first evaporator for the next cycle.

[0070] In this embodiment, the condenser is a heating side heat exchanger that mainly performs two-phase heat exchange, including but not limited to a tube-fin heat exchanger, a shell-and-tube heat exchanger, etc.; the evaporator is a heat recovery heat exchanger that performs two-phase heat exchange, including but not limited to a tube-fin heat exchanger, a shell-and-tube heat exchanger, etc. The compressor can be a special compressor suitable for operation with a high-boiling-point refrigerant, and the throttle valve is a valve component that controls the flow rate of the system refrigerant; the flash tank is a container for gas-liquid separation, including but not limited to a gas-liquid separator for gravity separation and filtration separation; the auxiliary heating equipment is arranged at the end of the heating main air duct (waterway) After the last condenser, it is responsible for auxiliary heating when the heat pump capacity is insufficient to achieve the required target temperature; the fluorine bypass valve is arranged in the fluorine side bypass branch between the first condenser and the second condenser, which is used to bypass the second condenser and adjust the refrigerant flow of the second condenser, thereby controlling the heat exchange capacity of the second condenser in the subcooling section; the first cooling flow channel is an independent and higher temperature flow channel that requires heat recovery, such as an exhaust pipe or a drain pipe; the second cooling flow channel is an independent and higher temperature flow channel that requires heat recovery, such as an exhaust pipe or a drain pipe.

[0071] In this embodiment, the waste heat cascade recovery subsystem uses the refrigerant to flow through the first pressure-reducing evaporation unit to perform the first throttling and pressure reduction to recover the waste heat of the first fluid in the first cooling channel for evaporation, and then separate the gas and liquid through the flash tank. The gaseous refrigerant enters the compressor enthalpy increase tube and is replenished to the compressor to do work. The liquid refrigerant is passed through the second pressure-reducing evaporation unit to perform the second throttling and pressure reduction to recover the waste heat of the second fluid in the second cooling channel for evaporation, thereby realizing the gradient recovery of the heat of the cooling fluid by the refrigerant. The refrigerant after heat recovery is compressed by the compressor to provide power for the circulation of the refrigerant pipeline, and the compressed high-pressure superheated refrigerant is first passed through the first condensing unit The medium-temperature fluid is heated to achieve condensation, and then the low-temperature fluid is heated by the second condensing unit to achieve condensation and then returned to the first pressure-reducing evaporation unit, thereby achieving gradient heating of the refrigerant to the fluid to be heated. The refrigerant circulation loop is constructed through the above-mentioned setting, which reduces the difficulty and cost of laying refrigerant pipelines, improves the heat recovery rate and utilization rate of the refrigerant, and improves the waste heat utilization rate of the heat pump system. Auxiliary heating equipment, refrigerant pipeline regulating valves and diversion units are used to adjust the waste heat in the case of insufficient and excessive waste heat, so that the actual temperature of the discharged fluid of the heated fluid meets user needs, improves user comfort and reduces the energy consumption of the heat pump system.

[0072] In actual applications, when there are multiple cooling channels, there may be a long distance between them, or when there is only one cooling channel, the relatively high-temperature channel area and the relatively low-temperature channel area may be far apart. If the refrigerant pipeline is long, the pipeline laying cost is too high, and the required auxiliary pump loss is large, and adjustment is more difficult. To solve the above problems, the waste heat cascade recovery subsystem of this embodiment includes at least one water heat exchange unit, each water heat exchange unit is arranged in the corresponding cooling channel, and the pressure reduction evaporation unit uses a corresponding water heat exchange unit to indirectly recover the heat of the fluid to be cooled, so as to reduce the laying length of the refrigerant pipeline, save laying costs, reduce the high performance requirements of the auxiliary pump required due to the excessively long pipeline, reduce the energy consumption of the auxiliary pump, and achieve accurate adjustment.

[0073] In a feasible embodiment, the heat pump waste heat treatment system includes a cooling flow channel, and the distance between its relatively high temperature flow channel area and relatively low temperature flow channel area is relatively far. It can be understood that the first pressure-reducing evaporation unit and the second pressure-reducing evaporation unit, this embodiment can adopt a mixed scheme of indirect waste heat recovery and direct waste heat recovery. For example, the waste heat cascade recovery subsystem 110 includes a water heat exchange unit 113, and the water heat exchange unit 113 can exchange heat with the first pressure-reducing evaporation unit 111a, that is, the first pressure-reducing evaporation unit 111a indirectly recovers waste heat from the inlet side of the cooling flow channel 140 (that is, the relatively high temperature flow channel area) through the water heat exchange unit 113, and the second pressure-reducing evaporation unit 111b directly recovers waste heat from the outlet side of the cooling flow channel 140 (that is, the relatively low temperature flow channel area); it can be understood that the direct waste heat recovery of the relatively high temperature flow channel area and the indirect waste heat recovery of the relatively low temperature flow channel area can be performed with reference to the above, and this embodiment does not make specific restrictions.

[0074] In a feasible embodiment, the heat pump waste heat treatment system may also include two or more relatively independent cooling channels that are far apart. Taking the first cooling channel and the second cooling channel as an example, this embodiment may adopt a mixed scheme of indirect waste heat recovery and direct waste heat recovery. The waste heat cascade recovery subsystem 110 includes a water heat exchange unit 113. The water heat exchange unit 113 may perform heat exchange with the first pressure-reducing evaporation unit 111a, that is, the first pressure-reducing evaporation unit 111a performs indirect waste heat recovery on the first cooling channel 141 through the water heat exchange unit 113, while the second pressure-reducing evaporation unit 111b performs direct waste heat recovery on the second cooling channel 142. It can be understood that the direct waste heat recovery for the first cooling channel and the indirect waste heat recovery for the second cooling channel can be performed with reference to the above, and this embodiment does not impose specific restrictions.

[0075] In a feasible embodiment, taking two cooling channels that are far apart, independent of each other and have different fluid temperatures as an example, refer to Figure 4 This embodiment can adopt an indirect waste heat recovery solution. The waste heat cascade recovery subsystem also includes a first water channel heat exchange unit 113a and a second water channel heat exchange unit 113b. The first water channel heat exchange unit 113a is arranged in the first cooling channel 141, and the second water channel heat exchange unit 113b is arranged in the second cooling channel 142.

[0076] The first water path heat exchange unit 113a is used to recover the heat of the first fluid in the first cooling channel 141. The first pressure-reducing evaporation unit 111a uses the first water path heat exchange unit 113a to indirectly recover the heat of the fluid to be cooled. The refrigerant outlet of the first pressure-reducing evaporation unit 111a is connected to the refrigerant inlet of the flash tank 112. The liquid refrigerant outlet of the flash tank 112 is connected to the refrigerant inlet of the second pressure-reducing evaporation unit 111b. The second pressure-reducing evaporation unit 111b uses the second water path heat exchange unit 113b to indirectly recover the heat of the fluid to be cooled.

[0077] Among them, the first water tank is a water tank for storing higher temperature cooling water in the first cooling water circuit, the second water tank is a water tank for storing higher temperature cooling water in the second cooling water circuit, the first water pump is a water pump for driving higher temperature cooling water in the first cooling water circuit, and the second water pump is a water pump for driving higher temperature cooling water in the second cooling water circuit.

[0078] In this embodiment, the waste heat cascade recovery subsystem uses the refrigerant flowing through at least two step-down evaporation units in sequence to exchange heat with the heat recovered by the corresponding water heat exchange units, thereby realizing indirect waste heat recovery and indirect gradient recovery of the heat of the refrigerant to be cooled. The refrigerant that has recovered the heat is compressed by the compressor to provide power for the circulation of the refrigerant pipeline. The waste heat cascade utilization subsystem uses the high-pressure superheated refrigerant compressed by the compressor to flow through at least two condensing units in sequence to heat the fluid to be heated in the heating flow channel, thereby realizing gradient heating of the refrigerant to be heated. The refrigerant circulation loop is constructed through the above-mentioned settings, which reduces the difficulty and cost of laying the refrigerant pipeline, improves the heat recovery rate and utilization rate of the refrigerant, improves the waste heat utilization rate of the heat pump system, and reduces the energy consumption of the heat pump system.

[0079] For ease of understanding, the specific process of this application is described below. Figure 5 , an embodiment of the heat pump waste heat treatment method in the present application includes:

[0080] 501. Obtain the actual temperature of the discharged fluid in the heating flow channel.

[0081] It is understood that the execution subject of this application can be a heat pump waste heat treatment device, or a heat pump waste heat treatment system, a terminal or a server, and the specific details are not limited here. This embodiment is described by taking the heat pump waste heat treatment system as the execution subject as an example.

[0082] The heat pump waste heat treatment system collects the actual temperature of the exhaust fluid through a temperature sensor installed in the heating flow channel. The actual temperature of the exhaust fluid may be the actual water temperature or the actual wind temperature.

[0083] 502. Determine whether the actual temperature is equal to the preset target temperature.

[0084] In this embodiment, the target temperature is the target outlet temperature or target exhaust temperature of the fluid discharged from the heating channel. The target temperature can be a fixed value set by the user, or it can be adaptively adjusted according to the corresponding target temperature adjustment logic, for example, adjusting the target temperature according to the ambient temperature.

[0085] Specifically, the actual temperature may be greater than the target temperature, that is, the heat utilized in the waste heat cascade utilization subsystem is greater than the user demand; the actual temperature may be lower than the target temperature, that is, the heat utilized in the waste heat cascade utilization subsystem does not meet the user demand, and the actual temperature is equal to the target temperature, that is, the heat available in the waste heat cascade utilization subsystem just meets the user demand.

[0086] 503. If yes, control the heat pump waste heat treatment system to maintain the current operating state.

[0087] When the actual temperature is equal to the preset target temperature, the current operating state of the heat pump waste heat treatment system is maintained, that is, the current operating parameters of each device in the heat pump waste heat treatment system are maintained, for example, including the compressor frequency, throttle valve opening, heat exchanger operating power (including evaporator and heat exchanger), flash tank operating power, water pump operating power, auxiliary heating equipment operating power, flow channel bypass valve opening, refrigerant pipeline regulating valve opening, etc.

[0088] 504. If not, control the compressor and / or the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature.

[0089] Specifically, when the actual temperature is not equal to the preset target temperature, the operating parameters of each device in the heat pump waste heat treatment system are adjusted to make the actual temperature equal to the target temperature.

[0090] Optionally, if the compressor is a fixed-frequency compressor, the operating parameters of the waste heat staged utilization subsystem are adjusted.

[0091] Optionally, if the compressor is a variable frequency compressor, the operating parameters of the variable frequency compressor and the waste heat staged utilization subsystem are adjusted.

[0092] Optionally, if the compressor is a variable frequency compressor, the operating parameters of the variable frequency compressor are adjusted first; when the actual temperature is still not equal to the target temperature after adjustment and exceeds the adjustment range of the variable frequency compressor, the operating parameters of the waste heat cascade utilization subsystem are adjusted.

[0093] Optionally, if the compressor is a variable frequency compressor, the operating parameters of the waste heat cascade utilization subsystem are adjusted first; when the actual temperature is still not equal to the target temperature after adjustment and exceeds the adjustment range of the waste heat cascade utilization subsystem, the operating parameters of the variable frequency compressor are adjusted again.

[0094] In this embodiment, the operating parameters of each device in the heat pump waste heat treatment system are adjusted by adjusting the actual temperature and target temperature of the fluid discharged in the heating flow channel, thereby avoiding overheating or insufficient heating, realizing precise control of the heat pump waste heat treatment system, and improving the accuracy and efficiency of thermal energy utilization. The dynamic adjustment strategy based on temperature feedback reduces unnecessary energy consumption and achieves the optimal match between energy consumption and demand, thereby improving the energy efficiency ratio of the entire heat pump waste heat treatment system, avoiding frequent start and stop, extending equipment life, reducing maintenance costs, enhancing the system's degree of automation, reducing the need for manual intervention, and improving the convenience and response speed of operation, so that the system can adapt to more complex and changeable working conditions, improving the recovery rate and utilization rate of heat by the refrigerant, improving the waste heat utilization rate of the heat pump system, and reducing the energy consumption of the heat pump system.

[0095] See also Figure 6 Another embodiment of the heat pump waste heat treatment method in the present application includes:

[0096] 601. Obtain the actual temperature of the discharged fluid in the heating channel.

[0097] 602. Determine whether the actual temperature is equal to the preset target temperature.

[0098] 603. If yes, control the heat pump waste heat treatment system to maintain the current operating state.

[0099] Steps 601-603 may be performed with reference to steps 501-503 and will not be repeated here.

[0100] 604. If the actual temperature is not equal to the target temperature, determine the target frequency adjustment amount of the variable frequency compressor according to the target temperature difference, where the target temperature difference is the temperature difference between the actual temperature and the target temperature.

[0101] The compressor in the heat pump waste heat treatment system can be a variable frequency compressor. When the actual temperature is not equal to the target temperature, the target temperature difference between the actual temperature and the target temperature is determined; and the target frequency adjustment amount of the variable frequency compressor is determined according to the target temperature difference.

[0102] The target temperature difference may be greater than zero, that is, the actual temperature is greater than the target temperature; the target temperature difference may be less than zero, that is, the actual temperature is less than the target temperature.

[0103] If the target temperature difference is greater than zero, the compressor frequency is reduced to reduce the heat exchanger capacity and lower the outlet air temperature; if the target temperature difference is less than zero, the compressor frequency is increased to increase the heat exchanger capacity and increase the outlet air temperature.

[0104] 605. Determine whether the frequency adjustment amount is greater than the compressor adjustment range.

[0105] Specifically, the adjusted target operating frequency is determined based on the current operating frequency of the compressor and the frequency adjustment amount; if the target operating frequency is greater than the maximum safe operating frequency of the compressor, or the target operating frequency is less than the minimum safe operating frequency of the compressor, it is determined that the compressor adjustment range is exceeded; otherwise, the compressor adjustment range is not exceeded.

[0106] Optionally, a determination is made as to whether the frequency adjustment amount is greater than a preset adjustment amount threshold; if so, it is determined that the compressor adjustment range is exceeded; otherwise, the compressor adjustment range is not exceeded. In this embodiment, if the frequency adjustment amount is greater than the preset adjustment amount threshold, the frequency adjustment may be too large, resulting in system instability. To avoid adjusting the compressor too quickly and improve system stability, step 606 may be directly executed. Alternatively, the actual frequency of the variable frequency compressor may be adjusted according to the adjustment amount threshold, and the adjusted first frequency may be maintained for a preset first time period, and then the first frequency may be continuously adjusted according to the adjustment amount difference so that the actual temperature is equal to the target temperature. The adjustment amount difference is the difference between the frequency adjustment amount and the adjustment amount threshold.

[0107] In this embodiment, the adjustment range of the compressor may be one or more of the maximum safe operating frequency of the compressor, the minimum safe operating frequency of the compressor, and an adjustment threshold, for example, determining whether the frequency adjustment is greater than a preset adjustment threshold; if not, determining the adjusted target operating frequency based on the current operating frequency of the compressor and the frequency adjustment;

[0108] If the target operating frequency is greater than the current operating frequency, that is, the frequency adjustment amount is greater than zero, then it is determined whether the target operating frequency is greater than the maximum safe operating frequency of the compressor; if not, the compressor adjustment range is not exceeded;

[0109] If the target operating frequency is less than the current operating frequency, that is, the frequency adjustment amount is less than zero, then it is determined whether the target operating frequency is less than the minimum safe operating frequency of the compressor; if not, the compressor adjustment range is not exceeded;

[0110] If the frequency adjustment amount is greater than the preset adjustment amount threshold, or the target operating frequency is greater than the maximum safe operating frequency of the compressor, or the target operating frequency is less than the minimum safe operating frequency of the compressor, it is determined that the compressor adjustment range is exceeded.

[0111] 606. If so, control the actual frequency adjustment amount of the variable frequency compressor to be less than or equal to the adjustment amount threshold, and control the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature.

[0112] In this embodiment, when the variable frequency compressor cannot meet the adjustment requirements, the compressor frequency is adjusted preferentially within the compressor adjustment range. It is determined that the fluid temperature (actual temperature) of the fluid discharged from the heating flow channel after adjustment is still not equal to the target temperature. Then, the waste heat step is controlled to utilize the subsystem to adjust the parameters so that the actual temperature is equal to the target temperature.

[0113] Optionally, controlling the waste heat cascade utilization subsystem to adjust parameters includes: if the actual temperature is greater than the target temperature, controlling the auxiliary heating equipment to reduce the operating power to lower the actual temperature; if the actual temperature is lower than the target temperature, controlling the auxiliary heating equipment to increase the operating power to increase the actual temperature.

[0114] Optionally, controlling the waste heat step utilization subsystem to perform parameter adjustment includes: if the actual temperature is greater than the target temperature, increasing the opening of the flow channel bypass valve to reduce the actual temperature; if the actual temperature is less than the target temperature, reducing the opening of the flow channel bypass valve to increase the actual temperature to equal the target temperature.

[0115] Optionally, controlling the waste heat step utilization subsystem to perform parameter adjustment includes: if the actual temperature is greater than the target temperature, controlling the auxiliary heating equipment to reduce the operating power until the auxiliary heating equipment is shut down, and then increasing the opening of the flow channel bypass valve to reduce the actual temperature to equal the target temperature; if the actual temperature is lower than the target temperature, reducing the opening of the flow channel bypass valve until the flow channel bypass valve is closed, and then controlling the auxiliary heating equipment to increase the operating power to increase the actual temperature to equal the target temperature.

[0116] 607. If not, adjust the operating frequency of the variable frequency compressor according to the frequency adjustment amount so that the actual temperature is equal to the target temperature.

[0117] When the variable frequency compressor can meet the regulation demand, the compressor frequency is adjusted according to the calculated frequency adjustment amount so that the actual temperature is equal to the target temperature.

[0118] Specifically, the actual temperature may be greater than the target temperature, and the frequency adjustment amount is negative adjustment, that is, reducing the compressor frequency to achieve the purpose of reducing the heat exchange capacity of the condenser and lowering the discharge fluid temperature; the actual temperature may be lower than the target temperature, and the frequency adjustment amount is positive adjustment, that is, increasing the compressor frequency to achieve the purpose of increasing the heat exchange capacity of the condenser and increasing the discharge fluid temperature.

[0119] In this embodiment, by adjusting the actual temperature and target temperature of the discharged fluid in the heating flow channel, the compressor operating frequency is preferentially controlled within the compressor adjustment range. When the compressor adjustment range is exceeded, the operating parameters of the waste heat cascade utilization subsystem are adjusted, and the operating parameters of each device in the heat pump waste heat treatment system are adjusted to avoid overheating or insufficient heating, thereby achieving precise control of the heat pump waste heat treatment system and improving the accuracy and efficiency of thermal energy utilization. The dynamic adjustment strategy based on temperature feedback reduces unnecessary energy consumption and achieves the optimal match between energy consumption and demand, thereby improving the energy efficiency ratio of the entire heat pump waste heat treatment system, avoiding frequent start-stop, extending equipment life, reducing maintenance costs, enhancing the system's degree of automation, reducing the need for manual intervention, and improving the convenience and response speed of operation, so that the system can adapt to more complex and changeable working conditions, improving the heat recovery rate and utilization rate of the refrigerant, improving the waste heat utilization rate of the heat pump system, and reducing the energy consumption of the heat pump system.

[0120] The above describes the heat pump waste heat treatment method in this application. The following describes the heat pump waste heat treatment device in this application. Figure 7 , an embodiment of the heat pump waste heat treatment device in this application includes:

[0121] An acquisition module 701 is used to acquire the actual temperature of the fluid discharged from the heating channel;

[0122] A determination module 702 is used to determine whether the actual temperature is equal to a preset target temperature;

[0123] Maintaining module 703, for controlling the heat pump waste heat treatment system to maintain the current operating state if yes;

[0124] The adjustment module 704 is configured to, if not, control the compressor and / or the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature.

[0125] In this embodiment, the operating parameters of each device in the heat pump waste heat treatment system are adjusted by adjusting the actual temperature and target temperature of the fluid discharged in the heating flow channel, thereby avoiding overheating or insufficient heating, realizing precise control of the heat pump waste heat treatment system, and improving the accuracy and efficiency of thermal energy utilization. The dynamic adjustment strategy based on temperature feedback reduces unnecessary energy consumption and achieves the optimal match between energy consumption and demand, thereby improving the energy efficiency ratio of the entire heat pump waste heat treatment system, avoiding frequent start and stop, extending equipment life, reducing maintenance costs, enhancing the system's degree of automation, reducing the need for manual intervention, and improving the convenience and response speed of operation, so that the system can adapt to more complex and changeable working conditions, improving the recovery rate and utilization rate of heat by the refrigerant, improving the waste heat utilization rate of the heat pump system, and reducing the energy consumption of the heat pump system.

[0126] See also Figure 8 Another embodiment of the heat pump waste heat treatment device in the present application includes:

[0127] An acquisition module 701 is used to acquire the actual temperature of the fluid discharged from the heating channel;

[0128] A determination module 702 is used to determine whether the actual temperature is equal to a preset target temperature;

[0129] Maintaining module 703, for controlling the heat pump waste heat treatment system to maintain the current operating state if yes;

[0130] The adjustment module 704 is configured to, if not, control the compressor and / or the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature.

[0131] Optionally, the adjustment module 704 includes:

[0132] A determination submodule 7041 is configured to determine a target frequency adjustment amount for the variable frequency compressor based on a target temperature difference if the actual temperature is not equal to the target temperature, where the target temperature difference is the temperature difference between the actual temperature and the target temperature;

[0133] The judging submodule 7042 is used to judge whether the frequency adjustment amount is greater than a preset adjustment amount threshold;

[0134] The first adjustment submodule 7043 is configured to control the actual frequency adjustment amount of the variable frequency compressor to be less than or equal to the adjustment amount threshold, and control the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature;

[0135] The second regulating submodule 7044 is configured to, if not, regulate the operating frequency of the variable frequency compressor according to the frequency adjustment amount so that the actual temperature is equal to the target temperature.

[0136] Optionally, the first regulating submodule 7043 includes an auxiliary heating unit, which is specifically configured to: if the actual temperature is greater than the target temperature, control the auxiliary heating device to reduce operating power so as to reduce the actual temperature;

[0137] If the actual temperature is lower than the target temperature, the auxiliary heating device is controlled to increase the operating power so as to increase the actual temperature.

[0138] Optionally, the first regulating submodule 7043 includes a valve regulating unit, which is specifically used to: if the actual temperature is greater than the target temperature, increase the opening of the flow channel bypass valve to reduce the actual temperature; if the actual temperature is lower than the target temperature, reduce the opening of the flow channel bypass valve to increase the actual temperature.

[0139] In this embodiment, by adjusting the actual temperature and target temperature of the discharged fluid in the heating flow channel, the compressor operating frequency is preferentially controlled within the compressor adjustment range. When it exceeds the compressor adjustment range, the operating parameters of the waste heat cascade utilization subsystem are adjusted, and the operating parameters of each device in the heat pump waste heat treatment system are adjusted to avoid overheating or insufficient heating, thereby achieving precise control of the heat pump waste heat treatment system and improving the accuracy and efficiency of thermal energy utilization. The dynamic adjustment strategy based on temperature feedback reduces unnecessary energy consumption and achieves the optimal match between energy consumption and demand, thereby improving the energy efficiency ratio of the entire heat pump waste heat treatment system, avoiding frequent start-stop, extending equipment life, reducing maintenance costs, enhancing the system's degree of automation, reducing the need for manual intervention, and improving the convenience and response speed of operation, so that the system can adapt to more complex and changeable working conditions, improving the heat recovery rate and utilization rate of the refrigerant, improving the waste heat utilization rate of the heat pump system, and reducing the energy consumption of the heat pump system.

[0140] above Figure 7 and Figure 8 The heat pump waste heat treatment device in this application is described in detail from the perspective of modular functional entities, and the heat pump waste heat treatment equipment in this application is described in detail from the perspective of hardware processing.

[0141] See also Figure 9 As shown, the heat pump waste heat treatment device includes a processor 900 and a memory 901. The memory 901 stores machine executable instructions that can be executed by the processor 900. The processor 900 executes the machine executable instructions to implement the above-mentioned heat pump waste heat treatment method.

[0142] Furthermore, Figure 9 The heat pump waste heat treatment device shown further includes a bus 902 and a communication interface 903 , and the processor 900 , the communication interface 903 and the memory 901 are connected via the bus 902 .

[0143] Among them, the memory 901 may include a high-speed random access memory (RAM), and may also include a non-volatile memory (non-volatile memory), for example, at least one disk storage. The communication connection between the system network element and at least one other network element is realized through at least one communication interface 903 (which can be wired or wireless), and the Internet, wide area network, local area network, metropolitan area network, etc. can be used. The bus 902 can be an ISA bus, a PCI bus, or an EISA bus, etc. The bus can be divided into an address bus, a data bus, a control bus, etc. For ease of representation, Figure 9 Only one bidirectional arrow is used in the diagram, but this does not mean that there is only one bus or one type of bus.

[0144] The processor 900 may be an integrated circuit chip with signal processing capabilities. During implementation, each step of the above method can be completed by hardware integrated logic circuits or software instructions in the processor 900. The above processor 900 may be a general-purpose processor, including a central processing unit (CPU), a network processor (NP), etc.; it may also be a digital signal processor (DSP), an application-specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, or discrete hardware components. It can implement or execute the various methods, steps, and logic block diagrams disclosed in the embodiments of the present disclosure. The general-purpose processor may be a microprocessor or any conventional processor. The steps of the method disclosed in conjunction with the embodiments of the present disclosure can be directly implemented and executed by a hardware decoding processor, or by a combination of hardware and software modules in the decoding processor. The software module can be located in a storage medium mature in the art, such as random access memory, flash memory, read-only memory, programmable read-only memory, electrically erasable programmable memory, registers, etc. The storage medium is located in the memory 901 , and the processor 900 reads the information in the memory 901 and completes the method steps of the aforementioned embodiment in combination with its hardware.

[0145] The present application also provides a computer-readable storage medium, which may be a non-volatile computer-readable storage medium or a volatile computer-readable storage medium. The computer-readable storage medium stores instructions that, when executed on a computer, cause the computer to execute the steps of the heat pump waste heat treatment method.

[0146] Those skilled in the art will clearly understand that, for the convenience and brevity of description, the specific working processes of the systems, devices and units described above can refer to the corresponding processes in the aforementioned method embodiments and will not be repeated here.

[0147] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present application, or the part that contributes to the prior art, or all or part of the technical solution can be embodied in the form of a software product, which is stored in a storage medium and includes several instructions for enabling a computer device (which can be a personal computer, server, or network device, etc.) to execute all or part of the steps of the various embodiments of the present application. The aforementioned storage medium includes various media that can store program codes, such as a USB flash drive, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a magnetic disk or an optical disk.

[0148] As described above, the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the above embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A heat pump waste heat treatment system, characterized in that: include: A waste heat cascade recovery subsystem with at least two pressure-reducing evaporation units, a compressor, a waste heat cascade utilization subsystem with at least two condensing units, at least one cooling flow channel, and one heating flow channel; wherein the waste heat cascade recovery subsystem is provided in the at least one cooling flow channel, and the waste heat cascade utilization subsystem is provided in the heating flow channel; The waste heat cascade recovery subsystem is used to flow the refrigerant through the at least two pressure-reducing evaporation units in sequence to recover the heat of the fluid to be cooled in the at least one cooling channel; The compressor is used to compress the low-pressure superheated refrigerant that completes the heat recovery of the fluid to be cooled; The waste heat cascade utilization subsystem is used to pass the high-pressure superheated refrigerant compressed by the compressor through the at least two condensing units in sequence to heat the fluid to be heated in the heating flow channel, and guide the refrigerant that has completed heating the fluid to be heated to the waste heat cascade recovery subsystem; The waste heat cascade utilization subsystem includes two condensing units connected in series, wherein the first condensing unit is arranged in the flow channel area close to the outlet side of the heating flow channel, and the second condensing unit is arranged in the flow channel area close to the inlet side of the heating flow channel; The refrigerant outlet of the compressor is connected to the refrigerant inlet of the first condensing unit, the refrigerant outlet of the first condensing unit is connected to the refrigerant inlet of the second condensing unit, and the refrigerant outlet of the second condensing unit is connected to the refrigerant inlet of the waste heat cascade utilization subsystem; The heat pump waste heat treatment system further includes a diversion unit, which is arranged in the target flow channel area where the waste heat cascade utilization subsystem is installed in the heating flow channel; The diversion unit is used to divide the target flow channel area into a bypass area and a heating area that are isolated from each other, and to control the on / off state of the bypass area. The waste heat step utilization subsystem is arranged in the heating area. The heat pump waste heat treatment system comprises two independent cooling channels, wherein the temperature of the first fluid in the first cooling channel is greater than the temperature of the second fluid in the second cooling channel; The waste heat cascade recovery subsystem includes two pressure-reducing evaporation units and a flash tank, wherein the first pressure-reducing evaporation unit is used to recover the heat of the first fluid in the first cooling channel; The flash tank is used to perform gas-liquid separation on the refrigerant used to recover the heat of the first fluid, and to use the gaseous refrigerant to inject heat into the compressor; The second pressure-reducing evaporation unit recovers the heat of the second fluid in the second cooling channel using the liquid refrigerant separated by the flash tank, and guides the low-pressure superheated refrigerant that recovers the heat of the first fluid and the heat of the second fluid to the compressor.

2. The heat pump waste heat treatment system according to claim 1, characterized in that: The waste heat cascade utilization subsystem further includes an auxiliary heating device, which is arranged in a flow channel region near the outlet side of the heating flow channel, and the first condensing unit is arranged in a flow channel region between the auxiliary heating device and the second condensing unit; The auxiliary heating device is used to perform auxiliary heating on the fluid to be heated in the heating channel.

3. The heat pump waste heat treatment system according to claim 1, characterized in that: The waste heat cascade utilization subsystem includes a refrigerant pipeline regulating valve; The refrigerant pipeline regulating valve is used to regulate the refrigerant flow passing through the second condensing unit.

4. The heat pump waste heat treatment system according to claim 1, characterized in that: Each pressure-reducing evaporation unit includes a throttle valve and an evaporator connected in series, wherein the throttle valve is used to throttle and reduce the pressure of the refrigerant flowing through; The evaporator utilizes the low-pressure refrigerant throttled and depressurized by the throttle valve to recover heat of the fluid to be cooled in the at least one cooling channel.

5. The heat pump waste heat treatment system according to claim 1 or 4, characterized in that: The waste heat cascade recovery subsystem further includes at least two water heat exchange units, and the at least two water heat exchange units are arranged in the at least one cooling channel; The at least two water channel heat exchange units are used to recover the heat of the fluid to be cooled in the at least one cooling channel; Each pressure-reducing evaporation unit utilizes a corresponding water-circuit heat exchange unit to indirectly recover the heat of the fluid to be cooled.

6. The heat pump waste heat treatment system according to claim 1, characterized in that: The refrigerant pipeline connecting the waste heat cascade recovery subsystem, the compressor, and the waste heat cascade utilization subsystem is circulated with a high-boiling-point refrigerant, and the maximum heating temperature of the high-boiling-point refrigerant reaches 80°C to 150°C.

7. A heat pump waste heat treatment method, characterized in that: Applicable to the heat pump waste heat treatment system according to any one of claims 1 to 6, the heat pump waste heat treatment method comprising: Acquiring the actual temperature of the fluid discharged from the heating flow channel; Determine whether the actual temperature is equal to the preset target temperature; If so, controlling the heat pump waste heat treatment system to maintain the current operating state; If not, the compressor and / or the waste heat step utilization subsystem are controlled to adjust parameters so that the actual temperature is equal to the target temperature.

8. The heat pump waste heat treatment method according to claim 7, characterized in that: The compressor is a variable frequency compressor; If not, controlling the compressor and / or the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature includes: If the actual temperature is not equal to the target temperature, determining the target frequency adjustment amount of the variable frequency compressor according to a target temperature difference, wherein the target temperature difference is the temperature difference between the actual temperature and the target temperature; Determining whether the frequency adjustment amount is greater than a preset adjustment amount threshold; If so, controlling the actual frequency adjustment amount of the variable frequency compressor to be less than or equal to the adjustment amount threshold, and controlling the waste heat step utilization subsystem to adjust parameters so that the actual temperature is equal to the target temperature; If not, the operating frequency of the variable frequency compressor is adjusted according to the frequency adjustment amount so that the actual temperature is equal to the target temperature.

9. The heat pump waste heat treatment method according to claim 8, characterized in that: The waste heat cascade utilization subsystem includes auxiliary heating equipment; The controlling the waste heat step utilization subsystem to perform parameter adjustment includes: If the actual temperature is greater than the target temperature, controlling the auxiliary heating device to reduce operating power so as to reduce the actual temperature; If the actual temperature is lower than the target temperature, the auxiliary heating device is controlled to increase operating power to increase the actual temperature.

10. The heat pump waste heat treatment method according to claim 8 or 9, characterized in that: The heat pump waste heat treatment system further includes a flow diversion unit provided with a flow channel bypass valve; The controlling the waste heat step utilization subsystem to perform parameter adjustment includes: If the actual temperature is greater than the target temperature, increasing the opening of the flow channel bypass valve to reduce the actual temperature; If the actual temperature is lower than the target temperature, the opening of the flow path bypass valve is reduced to increase the actual temperature.

11. A heat pump waste heat treatment device, characterized in that: Applicable to any one of claims 1 to 6 of the heat pump waste heat treatment system, the heat pump waste heat treatment device comprising: an acquisition module, configured to acquire the actual temperature of the fluid discharged from the heating flow channel; A judgment module is used to judge whether the actual temperature is equal to the preset target temperature; a maintaining module, configured to control the heat pump waste heat treatment system to maintain a current operating state if yes; The adjustment module is used to control the compressor and / or the waste heat step utilization subsystem to adjust parameters if the actual temperature is not equal to the target temperature.

12. A computer-readable storage medium having instructions stored thereon, characterized in that: When the instruction is read and executed, the heat pump waste heat treatment method according to any one of claims 7 to 10 is executed.

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