Double high-temperature heat pump system of regenerative reverse rankine cycle

Abstract

This invention provides a regenerative reverse Rankine cycle dual high-temperature heat pump system. The heat pump system includes: a first heat exchanger, a first compressor, a first regenerator, a second heat exchanger, and a first expansion valve. The first heat exchanger is connected to the first compressor via the first regenerator. The second heat exchanger is connected to the first compressor. The first expansion valve is connected to the first heat exchanger, and the second heat exchanger is connected to the first expansion valve via the first regenerator. By setting up the first regenerator, heat exchange is performed between the working fluid before throttling and before compression, thereby increasing the subcooling before throttling and significantly reducing throttling losses. At the same time, increasing the superheat at the outlet of the first heat exchanger avoids the damage to the compressor caused by wet compression due to ultra-high temperature dry working fluid, which helps to ensure the service life and high reliability of system components.

Description

Technical Field

[0001] This invention relates to the field of ultra-high temperature heat pump technology, and in particular to a regenerative reverse Rankine cycle dual high temperature heat pump system. Background Technology

[0002] A heat pump is a technology that transfers a low-temperature heat source to a high-temperature heat source through a working fluid cycle. Currently, the reverse Rankine cycle is one of the more commonly used heat pump cycles. Its principle is that the compressor compresses the steam generated in the evaporator to a high temperature, then the high-temperature working fluid releases heat in the condenser, and then enters the expansion valve (expander) for throttling / expansion before returning to the evaporator to complete one working cycle.

[0003] However, existing vapor compression heat pump technology generally operates below 200°C, making it difficult to apply to higher temperature ranges. Using a special type of ultra-high temperature working fluid (such as heat transfer oil operating at 300°C to 400°C) could potentially achieve heat pumping at temperatures above 200°C. However, these working fluids often have vastly different properties from low-temperature and ambient-temperature working fluids. They are generally dry working fluids, and during isentropic compression, they typically enter the gas-liquid two-phase region, leading to liquid slugging and even severe damage to the rigid body and blades, causing compressor failure. Summary of the Invention

[0004] This invention provides a regenerative reverse Rankine cycle dual high-temperature heat pump system, which differs from common vapor compression cycles. This cycle uses a regenerator to achieve the regeneration function, which can greatly reduce throttling losses and solve the problems of compressor liquid slugging or blade damage. It can effectively improve the superheat of the compressor inlet, avoid mechanical damage caused by wet compression, and ensure the service life and reliability of system components.

[0005] This invention provides a regenerative reverse Rankine cycle dual high-temperature heat pump system, comprising: First heat exchanger and first compressor; The first regenerator, the first heat exchanger is connected to the first compressor through the first regenerator; The second heat exchanger is connected to the first compressor; The first expansion valve is connected to the first heat exchanger, and the second heat exchanger is connected to the first expansion valve through the first regenerator.

[0006] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the first regenerator includes a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is connected to the first heat exchanger, the first outlet is connected to the first compressor, the second inlet is connected to the second heat exchanger, and the second outlet is connected to the first expansion valve.

[0007] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the first heat exchanger is used to connect to a first heat source, the second heat exchanger is used to connect to a second heat source, and the temperature of the second heat source is greater than the temperature of the first heat source.

[0008] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system further includes: Third heat exchanger; The second compressor is connected to the third heat exchanger; The second regenerator, the second heat exchanger is connected to the second compressor through the second regenerator; The second expansion valve is connected to the second heat exchanger, and the third heat exchanger is connected to the second expansion valve through the second regenerator.

[0009] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the first heat exchanger is used to connect to a first heat source, and the third heat exchanger is used to connect to a second heat source, wherein the temperature of the second heat source is greater than the temperature of the first heat source.

[0010] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein when at least one of the first heat source and the second heat source is a variable temperature heat source, the system working fluid of the heat pump system includes at least two fluid working fluids, and the at least two fluid working fluids do not azeotropically combine.

[0011] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the temperature of the first heat source is T1, and 200℃≤T1≤350℃.

[0012] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the temperature of the second heat source is T2, and 350℃≤T2≤600℃.

[0013] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the working fluid of the heat pump system is a dry fluid.

[0014] According to the present invention, a regenerative reverse Rankine cycle dual high-temperature heat pump system is provided, wherein the working fluid of the system includes at least one selected from Dowthern A, undecane, dodecane, hexadecane, dodecene, propylcyclohexane, chlorobenzene, D4, D5, D6, diethanolamine, decane, ethylbenzene, ethylene glycol, MD2M, MD3M, MD4M, monoethanolamine, methyl linoleate, methyl linolenic acid, methyl oleate, methyl palmitate, methyl stearate, m-xylene, nonane, o-xylene, p-xylene, and toluene.

[0015] The regenerative reverse Rankine cycle dual high-temperature heat pump system provided by this invention achieves the regenerative function by setting a first regenerator, which exchanges heat between the working fluid before throttling and the working fluid before compression to increase the subcooling before throttling, thereby significantly reducing throttling losses. At the same time, increasing the superheat at the outlet of the first heat exchanger can avoid the use of ultra-high temperature dry working fluid to produce wet compression, which would cause compressor damage and help ensure the service life and high reliability of system components. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 This is one of the structural schematic diagrams of the heat pump system provided by the present invention.

[0018] Figure 2 This is the second schematic diagram of the heat pump system provided by the present invention.

[0019] Figure 3 This is the temperature entropy diagram of the constant temperature heat source of the heat pump system provided by the present invention.

[0020] Figure 4 This is a temperature entropy diagram of the variable temperature heat source (with temperature glide) of the heat pump system provided by the present invention.

[0021] Figure 5 This is a schematic diagram of the structure of a heat pump in related technologies.

[0022] Figure 6 This is a temperature entropy diagram of the heat pump working fluid in related technologies.

[0023] Figure label: 1: Heat pump system; 10: First heat exchanger; 20: First compressor; 30: First regenerator; 32: First inlet; 34: Second inlet; 36: First outlet; 38: Second outlet; 40: Second heat exchanger; 50: First expansion valve; 60: Third heat exchanger; 70: Second compressor; 80: Second regenerator; 90: Second expansion valve; 100: First heat source; 200: Second heat source; 10': Evaporator; 20': Compressor; 30': Condenser; 40': Expansion valve; 50': High-temperature heat source; 60': Low-temperature heat source. Detailed Implementation

[0024] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0025] The following is combined Figures 1 to 4 The present invention describes a regenerative reverse Rankine cycle dual high-temperature heat pump system.

[0026] like Figure 1 As shown, this embodiment provides a regenerative reverse Rankine cycle dual high-temperature heat pump system 1. The heat pump system 1 includes a first heat exchanger 10, a first compressor 20, a first regenerator 30, a second heat exchanger 40, and a first expansion valve 50. The first heat exchanger 10 is connected to the first compressor 20 via the first regenerator 30. The second heat exchanger 40 is connected to the first compressor 20. The first expansion valve 50 is connected to the first heat exchanger 10, and the second heat exchanger 40 is connected to the first expansion valve 50 via the first regenerator 30.

[0027] The regenerative reverse Rankine cycle dual high-temperature heat pump system 1 of this embodiment includes a first heat exchanger 10, a first compressor 20, a first regenerator 30, a second heat exchanger 40, and a first expansion valve 50. Specifically, the low-temperature working fluid flowing out of the first heat exchanger 10 flows into the first regenerator 30 before entering the first compressor 20, where it exchanges heat with the high-temperature working fluid flowing out of the second heat exchanger 40 before entering the first expansion valve 50. The low-temperature working fluid heats up to become superheated steam, which is then compressed by the first compressor 20 and enters the second heat exchanger 40 to release heat. The high-temperature working fluid flowing out of the second heat exchanger 40 flows into the first regenerator 30 before entering the first expansion valve 50, where it exchanges heat with the low-temperature working fluid flowing out of the first heat exchanger 10 to become subcooled liquid. It is then throttled and expanded by the first expansion valve 50 to cool and depressurize, and finally enters the first heat exchanger 10 to complete the cycle.

[0028] By setting up the first regenerator 30 to achieve the regeneration function, heat is exchanged between the working fluid before throttling and the working fluid before compression, so as to increase the subcooling before throttling and significantly reduce throttling losses. At the same time, increasing the superheat at the outlet of the first heat exchanger can avoid the use of ultra-high temperature dry working fluid to produce wet compression, which would cause compressor damage and help ensure the service life and high reliability of system components.

[0029] Optionally, the first heat exchanger 10 is an evaporator, and the second heat exchanger 40 is a condenser.

[0030] In some embodiments, such as Figure 1As shown, the first regenerator 30 includes a first inlet 32, a second inlet 34, a first outlet 36, and a second outlet 38. The first inlet 32 ​​is connected to the first heat exchanger 10, and the first outlet 36 is connected to the first compressor 20. The second inlet 34 is connected to the second heat exchanger 40, and the second outlet 38 is connected to the first expansion valve 50.

[0031] In this embodiment, specifically, the low-temperature working fluid flowing out of the first heat exchanger 10 flows into the first regenerator 30 through the first inlet 32 ​​before entering the first compressor 20. There, it exchanges heat with the high-temperature working fluid flowing out of the second heat exchanger 40 before entering the first expansion valve 50. The low-temperature working fluid heats up to become superheated steam, which flows out from the first outlet 36, is compressed by the first compressor 20, and then enters the second heat exchanger 40 to release heat. The high-temperature working fluid flowing out of the second heat exchanger 40 flows into the first regenerator 30 through the second inlet 34 before entering the first expansion valve 50. There, it exchanges heat with the low-temperature working fluid flowing out of the first heat exchanger 10 and becomes subcooled liquid. The subcooled liquid flows out from the second outlet 38, is then throttled and expanded by the first expansion valve 50 to reduce its temperature and pressure, and finally enters the first heat exchanger 10 to complete the cycle.

[0032] Unlike common vapor compression cycles, this cycle uses a regenerator to achieve reheating, which can greatly reduce throttling losses and solve the problems of compressor liquid slugging or blade damage. It can effectively improve the superheat of the compressor inlet, avoid mechanical damage caused by wet compression, and ensure the service life and reliability of system components.

[0033] In some embodiments, such as Figure 1 As shown, the first heat exchanger 10 is connected to the first heat source 100, and the second heat exchanger 40 is connected to the second heat source 200. The temperature of the second heat source 200 is higher than the temperature of the first heat source 100.

[0034] In other words, the first heat source 100 is a low-temperature heat source, and the second heat source 200 is a high-temperature heat source. At this time, the heat pump system 1 is a primary circulation unit, which can raise the medium- and high-temperature heat source (first heat source 100) generated by nuclear energy to the higher-temperature heat source (second heat source 200) required by heavy industries such as petrochemicals and metallurgy through the heat pump system 1, so as to realize the effective utilization of nuclear energy heat generation.

[0035] The superheated steam is compressed by the first compressor 20 and then enters the second heat exchanger 40, where it releases heat to the second heat source 200.

[0036] In some embodiments, such as Figure 2As shown, the heat pump system 1 also includes a third heat exchanger 60, a second compressor 70, a second regenerator 80, and a second expansion valve 90. The second compressor 70 is connected to the third heat exchanger 60. The second heat exchanger 40 is connected to the second compressor 70 via the second regenerator 80. The second expansion valve 90 is connected to the second heat exchanger 40. The third heat exchanger 60 is connected to the second expansion valve 90 via the second regenerator 80.

[0037] In this embodiment, another implementation method is defined. In scenarios with a large temperature range, two-stage cascading can be performed. In this case, the second heat exchanger 40 can be the evaporator of the next stage circulation unit, performing stepped heating so that the low-temperature heat source is gradually raised to the higher temperature heat source required by heavy industries such as petrochemicals and metallurgy.

[0038] The second heat exchanger 40 is an evaporative-condensing heat exchanger.

[0039] Optionally, the above-mentioned regenerators (first regenerator 30 and second regenerator 80) are both counter-flow heat exchange structures to reheat the working fluid before throttling and before compression, thereby reducing throttling losses and increasing the superheat at the compressor inlet.

[0040] In some embodiments, such as Figure 2 As shown, the first heat exchanger 10 is used to connect to the first heat source 100, and the third heat exchanger 60 is used to connect to the second heat source 200. The temperature of the second heat source 200 is greater than the temperature of the first heat source 100.

[0041] In this embodiment, the first heat source 100 is a low-temperature heat source, and the second heat source 200 is a high-temperature heat source. At this time, the heat pump system 1 is a two-stage cascade cycle unit, which can raise the medium-high temperature heat source (first heat source 100) generated by nuclear energy to the higher temperature heat source (second heat source 200) required by heavy industries such as petrochemicals and metallurgy, thereby realizing the effective utilization of nuclear energy heat generation.

[0042] In this process, superheated steam is compressed by the first compressor 20 and then enters the second heat exchanger 40, which functions as the evaporator of the secondary circulation unit. The working fluid flowing out of the second heat exchanger 40 enters the second regenerator 80 and exchanges heat with the high-temperature medium flowing out of the third heat exchanger 60, becoming superheated steam. After being compressed by the second compressor 70, it enters the third heat exchanger 60, where it releases heat to the second heat source 200. The high-temperature working fluid flowing out of the third heat exchanger 60 enters the second regenerator 80 before flowing into the second expansion valve 90, where it exchanges heat with the working fluid flowing out of the second heat exchanger 40, becoming subcooled liquid. It then undergoes throttling expansion and cooling / pressure reduction by the second expansion valve 90 before finally entering the second heat exchanger 40 to complete the cycle.

[0043] In some embodiments, when at least one of the first heat source 100 and the second heat source 200 is a variable temperature heat source, the system working fluid of the heat pump system 1 includes at least two fluid working fluids, and the at least two fluid working fluids do not azeotropically combine.

[0044] In this embodiment, it can be understood that the heat source temperatures of the first heat source 100 and the second heat source 200 are often not constant-temperature heat sources. The temperature difference change of the system working fluid during the heat absorption and release process on the high-temperature heat source and the low-temperature heat source side is an important source of irreversible loss.

[0045] Since the system working fluid includes at least two fluid working fluids, and at least two fluid working fluids do not azeotropically, that is, the system working fluid is a mixed working fluid, there is a temperature glide phenomenon during the phase change process of the mixed working fluid, that is, the working fluid produces temperature changes when it evaporates or condenses. This can effectively reduce the temperature difference between the system working fluid and the variable temperature heat source during the heat transfer process, that is, reduce the average heat transfer temperature difference, and thus reduce the irreversible heat transfer loss of the heat source.

[0046] In some embodiments, the temperature of the first heat source 100 is T1, wherein 200℃≤T1≤350℃.

[0047] In some embodiments, the temperature of the second heat source 200 is T2, wherein 350℃≤T2≤600℃.

[0048] In this embodiment, since the continuous expansion of wind power and photovoltaic power has compressed the space for nuclear power generation, supplying high-temperature heat sources required by industrial scenarios with nuclear heat is a new way to utilize nuclear energy.

[0049] Understandably, compared to the second heat source 200, the first heat source 100 is a low-temperature heat source. Since the temperature of the first heat source 100 is between 200℃ and 350℃, it is a medium-to-high temperature heat source. The temperature of the second heat source 200 is between 350℃ and 600℃. For example, in nuclear energy heat generation, the medium-to-high temperature heat source (200℃~350℃) generated by nuclear energy can be raised through this heat pump system 1 to the higher temperatures (350℃~600℃) required in heavy industries such as petrochemicals and metallurgy, thus achieving effective utilization of nuclear energy heat generation.

[0050] In the process of high-temperature pumping heat, the use of a counter-flow heat exchanger to achieve the heat recovery function can greatly reduce throttling losses and solve the problems of compressor liquid slugging or blade damage.

[0051] In some embodiments, the working fluid of the heat pump system 1 is a dry fluid.

[0052] In this embodiment, since the system uses a dry fluid as the working fluid, the problem of excessively high compressor outlet temperature caused by reheating and recompression, which leads to a decrease in system efficiency, can be reduced. While increasing the steam superheat at the outlet of the first heat exchanger 10 and reducing the risk of liquid slugging in the compressor, it is also beneficial to improve system efficiency.

[0053] It is worth noting that the slope of the saturated vapor line on the temperature-entropy diagram is positive for the dry working fluid.

[0054] In some embodiments, the system working fluid includes at least one selected from Dowthern A, undecane, dodecane, hexadecane, dodecene, propylcyclohexane, chlorobenzene, D4, D5, D6, diethanolamine, decane, ethylbenzene, ethylene glycol, MD2M, MD3M, MD4M, monoethanolamine, methyl linoleate, methyl linolenic acid, methyl oleate, methyl palmitate, methyl stearate, m-xylene, nonane, o-xylene, p-xylene, and toluene.

[0055] In other words, the system working fluids that can be used include, but are not limited to, Dowthern A, undecane, dodecane, hexadecane, dodecene, propylcyclohexane, chlorobenzene, D4, D5, D6, diethanolamine, decane, ethylbenzene, ethylene glycol, MD2M, MD3M, MD4M, monoethanolamine, methyl linoleate, methyl linolenic acid, methyl oleate, methyl palmitate, methyl stearate, m-xylene, nonane, o-xylene, p-xylene, toluene, and mixtures thereof.

[0056] Among them, D4, D5, and D6 are octamethylcyclotetrasiloxane, decamethylcyclopentasiloxane, and dodecylcyclohexasiloxane, respectively.

[0057] MD2M, MD3M, and MD4M are hexamethyldisiloxane, octamethyltrisiloxane, and decamethyltetrasiloxane, respectively.

[0058] In one specific embodiment, compared to the traditional heat pump system structure, such as Figure 5 As shown, the system includes an evaporator 10', a compressor 20', a condenser 30', and an expansion valve 40'. The evaporator 10' is connected to a low-temperature heat source 60', and the condenser 30' is connected to a high-temperature heat source 50'. The working fluid temperature-entropy diagram is shown below. Figure 6 As shown, specifically, 6-1-2 is the process of the working fluid evaporating and absorbing heat in the evaporator 10', 2-3 is the process of the working fluid being compressed and heated in the compressor 20', and 3-4-5 is the process of the working fluid being compressed and then condensed and releasing heat in the condenser 30'.

[0059] Conventional vapor compression heat pumps operate at temperatures below 200°C on the high-temperature heat source side, using a wet working fluid. The evaporator outlet exhibits slight superheat, and the compressor compression process does not enter the two-phase region, thus avoiding liquid slugging or blade damage issues. However, ultra-high temperature heat pumps operating in the 300°C–500°C range typically use a dry working fluid. If a simple reverse Rankine cycle, typical of conventional vapor compression heat pumps, is employed, two critical problems arise: firstly, significant throttling losses; and secondly, the compression process enters the two-phase region, leading to severe issues such as liquid slugging or blade damage.

[0060] Based on this, the present invention proposes a heat pump system 1, which belongs to ultra-high temperature heat pump technology, capable of efficiently raising the temperature of a medium-high temperature heat source of 200℃~350℃ to the high temperature range (350℃~600℃) usable in industrial scenarios such as petrochemicals and metallurgy. A regenerator (first regenerator 30) is added to the heat pump cycle, allowing heat exchange between the working fluid before throttling and before compression. This ensures that the working fluid has a certain degree of subcooling before throttling, reducing throttling losses, and also ensures that the working fluid has a certain degree of superheat before compression, preventing liquid from mixing in during compression.

[0061] The system structure proposed in this invention can reduce throttling losses and heat transfer temperature difference on the heat source side, while also increasing the steam superheat at the outlet of the evaporator (first heat exchanger 10), reducing the risk of compressor liquid slugging, improving system efficiency, extending the service life of system components, greatly improving system efficiency, and ensuring reliable system operation.

[0062] Example 1: When the heat source is a constant-temperature heat source, in order to control the heat transfer temperature difference, a pure working fluid is used (the temperature of the evaporation and condensation processes remains constant). The system temperature-entropy diagram is as follows: Figure 3 As shown. Specifically, 1-2 is the process of the working fluid absorbing heat and increasing temperature at isobaric pressure in the regenerator (first regenerator 30) after exiting the evaporator (first heat exchanger 10); 2-3 is the process of the working fluid being compressed and increasing temperature in the compressor (first compressor 20) after exiting the regenerator; 3-4-5 is the process of the compressed working fluid condensing and releasing heat in the condenser (second heat exchanger 40). At this time, the thermodynamic process of the high-temperature heat source medium is ab. 5-6 is the process of the working fluid releasing heat in the regenerator after exiting the condenser; 6-7 is the process of the working fluid expanding by throttling in the throttling valve (first expansion valve 50); 7-1 is the process of the working fluid evaporating and absorbing heat in the evaporator. At this time, the thermodynamic process of the low-temperature heat source medium is cd.

[0063] Example 2: When the heat source is a variable-temperature heat source, in order to control the heat transfer temperature difference, a mixture of two or more working fluids can be used (the temperature will change during evaporation and condensation). The system temperature-entropy diagram is as follows: Figure 4As shown. Specifically, 1-2 is the process of the working fluid absorbing heat and increasing temperature at isobaric pressure in the regenerator (first regenerator 30) after exiting the evaporator (first heat exchanger 10); 2-3 is the process of the working fluid being compressed and increasing temperature in the compressor (first compressor 20) after exiting the regenerator; 3-4-5 is the process of the compressed working fluid condensing and releasing heat in the condenser (second heat exchanger 40). At this time, the thermodynamic process of the high-temperature heat source medium is ab. 5-6 is the process of the working fluid releasing heat in the regenerator after exiting the condenser; 6-7 is the process of the working fluid expanding by throttling in the throttling valve (first expansion valve 50); 7-1 is the process of the working fluid evaporating and absorbing heat in the evaporator. At this time, the thermodynamic process of the low-temperature heat source medium is cd.

[0064] in, Figure 3 , Figure 4 and Figure 6 In the diagram, the thick dashed line represents the heat source on the high-temperature side, and the thin dashed line represents the heat source on the low-temperature side.

[0065] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A regenerative reverse Rankine cycle dual high-temperature heat pump system, characterized in that, include: First heat exchanger and first compressor; The first regenerator, the first heat exchanger is connected to the first compressor through the first regenerator; The second heat exchanger is connected to the first compressor; The first expansion valve is connected to the first heat exchanger, and the second heat exchanger is connected to the first expansion valve through the first regenerator.

2. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 1, characterized in that, The first regenerator includes a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is connected to the first heat exchanger, the first outlet is connected to the first compressor, the second inlet is connected to the second heat exchanger, and the second outlet is connected to the first expansion valve.

3. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 1, characterized in that, The first heat exchanger is used to connect to a first heat source, and the second heat exchanger is used to connect to a second heat source, wherein the temperature of the second heat source is greater than the temperature of the first heat source.

4. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 1, characterized in that, The heat pump system also includes: Third heat exchanger; The second compressor is connected to the third heat exchanger; The second regenerator, the second heat exchanger is connected to the second compressor through the second regenerator; The second expansion valve is connected to the second heat exchanger, and the third heat exchanger is connected to the second expansion valve through the second regenerator.

5. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 4, characterized in that, The first heat exchanger is used to connect to a first heat source, and the third heat exchanger is used to connect to a second heat source, the temperature of the second heat source being greater than the temperature of the first heat source.

6. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 3 or 5, characterized in that, When at least one of the first heat source and the second heat source is a variable temperature heat source, the working fluid of the heat pump system includes at least two fluid working fluids, and the at least two fluid working fluids do not azeotropically combine.

7. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 3 or 5, characterized in that, The temperature of the first heat source is T1, where 200℃≤T1≤350℃.

8. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 3 or 5, characterized in that, The temperature of the second heat source is T2, where 350℃≤T2≤600℃.

9. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to any one of claims 1 to 5, characterized in that, The working fluid of the heat pump system is a dry fluid.

10. The regenerative reverse Rankine cycle dual high-temperature heat pump system according to claim 9, characterized in that, The system working fluid includes at least one of DowthernA, undecane, dodecane, hexadecane, dodecene, propylcyclohexane, chlorobenzene, D4, D5, D6, diethanolamine, decane, ethylbenzene, ethylene glycol, MD2M, MD3M, MD4M, monoethanolamine, methyl linoleate, methyl linolenic acid, methyl oleate, methyl palmitate, methyl stearate, m-xylene, nonane, o-xylene, p-xylene, and toluene.

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