Heat pump thermal management system for dual-purpose heat exchanger

Abstract

The present invention relates to the technical field of thermal management systems, and in particular, to a heat exchanger dual-purpose thermal management system. A heat pump thermal management system with a dual-purpose heat exchanger includes: a first control valve is provided at the inflow end of the communication loop close to the power source assembly; a first communication pipeline is connected between the communication loop and the inflow end of the power source assembly, and a second control valve is provided on the first communication pipeline; a second communication pipeline is connected between the outflow end of the power source assembly and the second heat exchanger; a series pipeline is connected between the first heat exchanger and the second heat exchanger, and a third control valve is provided on the series pipeline; a first branch pipeline is connected between the second communication pipeline and the side of the communication loop close to the inflow end of the power source assembly, and a fourth control valve is provided on the first branch pipeline; the outflow end of the power source assembly can be connected to the communication loop or the second communication pipeline through a commutation control member.

Description

Technical Field

[0001] The present invention relates to the technical field of thermal management systems, and more particularly to a heat pump thermal management system with a dual-purpose heat exchanger. Background Art

[0002] The heat pump air conditioning system is an important part of new energy vehicles, and its performance greatly affects the driving range of new energy vehicles and the comfort of passengers. The general air conditioning box assembly of the existing direct heat pump air conditioning system is a two-core structure, that is, an indoor evaporator and an indoor condenser. When the air conditioning system cools, the refrigerant evaporates and absorbs heat at the indoor evaporator, and the indoor condenser is idle. When the air conditioning system heats, the refrigerant condenses and releases heat at the indoor condenser, and the indoor evaporator is idle. However, nowadays, new energy vehicles are constantly pursuing the expansion of the occupant compartment space, and the available layout space of the air conditioning system is very limited. Therefore, the heat exchange area of the core body used in the air conditioning system under the existing technology and system architecture design is limited, which directly affects the performance of the system. Summary of the Invention

[0003] The purpose of the present invention is to provide a heat pump thermal management system with a dual-purpose heat exchanger and a new energy vehicle, so as to solve to a certain extent the technical problem of poor heat exchange of the heat pump thermal management system with a dual-purpose heat exchanger in the existing technology.

[0004] The present invention provides a heat pump thermal management system with a dual-purpose heat exchanger, including: a power source assembly, a commutation control member, a circulating heat exchanger, a communication circuit, a first heat exchanger, and a second heat exchanger; the first heat exchanger, the circulating heat exchanger, and the power source assembly are connected to the communication circuit, and a first control valve is provided at the inflow end of the communication circuit close to the power source assembly; a first communication pipeline is further included; the first communication pipeline is connected between the communication circuit and the inflow end of the power source assembly, and the connection point of the first communication pipeline and the communication circuit is located on the side where the circulating heat exchanger is connected to the outflow end of the power source assembly, and a second control valve is provided on the first communication pipeline; a second communication pipeline and a series pipeline are further included; the second communication pipeline is connected between the outflow end of the power source assembly and the second heat exchanger; the series pipeline is connected between the first heat exchanger and the second heat exchanger, and a third control valve is provided on the series pipeline; a first branch pipeline is connected between the second communication pipeline and the inflow end of the power source assembly, and a fourth control valve is provided on the first branch pipeline; the outflow end of the power source assembly can be connected to the communication circuit or the second communication pipeline through the commutation control member.

[0005] In the heat pump thermal management system with a dual-purpose heat exchanger provided by the present invention, the first heat exchanger and the second heat exchanger can both be used as condensers and as evaporators simultaneously. Without increasing the number of evaporators and condensers, the heat transfer area is increased, the heat transfer efficiency is improved, and the heat transfer effect is enhanced.

[0006] Further, the first heat exchanger includes a first interface and a second interface, the second heat exchanger includes a third interface and a fourth interface, and the circulating heat exchanger includes a first circulating interface and a second circulating interface; the communication loop includes an outflow-side pipeline, an intermediate pipeline, and an inflow-side pipeline; the outflow-side pipeline is connected between the outflow end of the power source assembly and the first circulating interface, the intermediate pipeline is connected between the second circulating interface and the first interface, and the inflow-side pipeline is connected between the second interface and the inflow end of the power source assembly; the first communication pipeline is connected between the outflow-side pipeline and the inflow end of the power source assembly, the second communication pipeline is connected between the outflow end of the power source assembly and the third interface, the first branch pipeline is connected between the second communication pipeline and the inflow-side pipeline, and the series pipeline is connected between the fourth interface and the inflow-side pipeline; the first control valve is arranged on the inflow-side pipeline and is located between the connection point of the inflow-side pipeline and the series pipeline and the connection point of the inflow-side pipeline and the first branch pipeline; the outflow end of the power source assembly can be connected to the outflow-side pipeline or the second communication pipeline through the commutation control member.

[0007] Further, the heat pump thermal management system with a dual-purpose heat exchanger further includes a third heat exchanger, a fifth control valve, and a second branch pipeline. The third heat exchanger is connected between the intermediate pipeline and the inflow end of the power source assembly through the second branch pipeline, and the fifth control valve is arranged on the second branch pipeline.

[0008] Further, the heat pump thermal management system with a dual-purpose heat exchanger further includes a sixth control valve; the sixth control valve is arranged on the intermediate pipeline.

[0009] Further, the heat pump thermal management system with a dual-purpose heat exchanger further includes a third branch pipeline and a seventh control valve; the third branch pipeline is connected between the outflow-side pipeline and the fourth interface, the series pipeline is connected between the inflow-side pipeline and the third branch pipeline; the seventh control valve is arranged on the third branch pipeline and is located between the connection point of the third branch pipeline and the series pipeline and the connection point of the third branch pipeline and the outflow-side pipeline.

[0010] Further, the commutation control member is a three-way solenoid valve.

[0011] Further, the heat pump thermal management system with dual-purpose heat exchangers further includes a fourth pipeline and a fifth pipeline; the fourth pipeline is connected between the outflow end of the power source assembly and the second communication pipeline, and the fifth pipeline is connected between the outflow end of the power source assembly and the outflow side pipeline; the commutation control member includes a first solenoid valve and a second solenoid valve; the first solenoid valve is arranged on the fourth pipeline, and the second solenoid valve is arranged on the fifth pipeline.

[0012] Further, the heat pump thermal management system with dual-purpose heat exchangers further includes a one-way pipeline and a parallel one-way valve; the one-way pipeline is connected between the intermediate pipeline and the series pipeline, and the parallel one-way valve is arranged on the one-way pipeline.

[0013] Further, the commutation control member, the second control valve, and the seventh control valve are integrated into a multi-way solenoid valve.

[0014] Further, the heat pump thermal management system with dual-purpose heat exchangers further includes an interface parallel pipeline, and the second heat exchanger further includes a fifth interface; the interface parallel pipeline is connected between the second communication pipeline and the fifth interface; on the second communication pipeline, an eighth control valve is provided between the connection point of the second communication pipeline and the interface parallel pipeline and the third interface, and a ninth control valve is provided on the interface parallel pipeline.

[0015] It should be understood that both the foregoing general description and the following detailed description are for the purpose of illustration and example and are not necessarily limiting to the present disclosure. The accompanying drawings incorporated in and constituting a part of the specification illustrate the subject matter of the present disclosure. At the same time, the specification and the drawings are used to explain the principles of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the specific embodiments or the prior art. Obviously, the following drawings are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0017] Figure 1 is the schematic diagram of the heat pump thermal management system with dual-purpose heat exchangers according to the first embodiment of the present invention;

[0018] Figure 2 is the schematic diagram of the heat pump thermal management system with dual-purpose heat exchangers according to the second embodiment of the present invention;

[0019] Figure 3 is Figure 2 the operation diagram of the heat pump thermal management system with dual-purpose heat exchangers shown in the refrigeration mode;

[0020] Figure 4 For Figure 2 The operation diagrams of the heat pump thermal management system with dual-purpose heat exchangers in the refrigeration mode and the forced cooling mode of the heating component;

[0021] Figure 5 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the forced cooling mode of the heating component;

[0022] Figure 6 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the heating mode;

[0023] Figure 7 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the heating waste heat recovery mode;

[0024] Figure 8 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the compressor self-heating heating mode;

[0025] Figure 9 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the first dehumidification mode;

[0026] Figure 10 For Figure 2 The operation diagram of the heat pump thermal management system with dual-purpose heat exchangers in the second dehumidification mode;

[0027] Figure 11 The schematic diagram of the heat pump thermal management system with dual-purpose heat exchangers according to the third embodiment of the present invention.

[0028] Icons: 1 - Compressor; 2 - Gas-liquid separator; 3 - Circulation heat exchanger; 301 - First circulation interface; 302 - Second circulation interface; 4 - First heat exchanger; 401 - First interface; 402 - Second interface; 5 - Second heat exchanger; 501 - Third interface; 502 - Fourth interface; 503 - Fifth interface; 6 - Third heat exchanger; 7 - First solenoid valve; 8 - Second solenoid valve; 9 - Third solenoid valve; 10 - Fourth solenoid valve; 11 - Fifth solenoid valve; 12 - First electronic expansion valve; 13 - Second electronic expansion valve; 14 - Third electronic expansion valve; 15 - Fourth electronic expansion valve; 16 - Fifth electronic expansion valve; 17 - Sixth electronic expansion valve; 18 - Blower; 201 - Outlet side pipeline; 202 - Intermediate pipeline; 203 - Inlet side pipeline; 21 - First connecting pipeline; 22 - Second connecting pipeline; 23 - Series pipeline; 24 - First branch pipeline; 25 - Second branch pipeline; 26 - Third branch pipeline; 27 - Fourth branch pipeline; 28 - Fifth branch pipeline; 29 - Parallel check valve; 30 - One-way pipeline; 31 - Interface parallel pipeline. Detailed implementation

[0029] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all of the embodiments.

[0030] The components of the embodiments of the present invention usually described and shown in the accompanying drawings here can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely represents the selected embodiments of the present invention.

[0031] All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention.

[0032] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first", "second", "third", "fourth", "fifth", "sixth", "seventh", "eighth" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0033] In the description of the present invention, it should be noted that unless otherwise clearly specified and defined, the terms "installation", "connection", and "coupling" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0034] As Figures 1 to 11 shown, the present invention provides a heat pump thermal management system for dual use of a heat exchanger, including: a power source assembly, a circulation heat exchanger 3, a commutation control member, a communication circuit, a first heat exchanger 4, and a second heat exchanger 5; the first heat exchanger 4, the circulation heat exchanger 3, and the power source assembly are connected to the communication circuit, and a first control valve is provided at the inflow end of the communication circuit close to the power source assembly; a first communication pipeline 21 is further included; the first communication pipeline 21 is communicated between the communication circuit and the inflow end of the power source assembly, and the connection point of the first communication pipeline 21 and the communication circuit is located on the side where the circulation heat exchanger 3 is communicated with the outflow end of the power source assembly, and a second control valve is provided on the first communication pipeline 21; a second communication pipeline 22 and a series pipeline 23 are further included; the second communication pipeline 22 is communicated between the outflow end of the power source assembly and the second heat exchanger 5; the series pipeline 23 is communicated between the first heat exchanger 4 and the second heat exchanger 5, and a third control valve is provided on the series pipeline 23; a first branch pipeline 24 is communicated between the second communication pipeline 22 and the inflow end of the power source assembly, and a fourth control valve is provided on the first branch pipeline 24; the outflow end of the power source assembly can be communicated with the communication circuit or the second communication pipeline 22 through the commutation control member.

[0035] In this embodiment, when refrigeration is required, the first control valve and the second control valve can be closed, and the third control valve and the fourth control valve can be opened; the commutation control member connects the outflow end of the power source assembly to the communication circuit, and the medium flowing out of the power source assembly enters the circulation heat exchanger 3 through the commutation control member, and the medium enters the first heat exchanger 4 for heat exchange from the circulation heat exchanger 3. At this time, the series pipeline 23 is opened, and the medium can enter the second heat exchanger 5 for heat exchange from the first heat exchanger 4. Both the first heat exchanger 4 and the second heat exchanger 5 can work as evaporators, with high refrigeration intensity and high refrigeration efficiency; after flowing out of the second heat exchanger 5, the medium flows to the inflow end of the power source assembly through the second communication pipeline 22, and thus flows back to the power source assembly. Of course, if forced refrigeration is not required, the first control valve can be opened and the third control valve can be closed, so that the medium only passes through the first heat exchanger 4 for heat exchange, that is, at this time the first heat exchanger 4 is used as an evaporator, and traditional refrigeration can be achieved.

[0036] When heating is required, the first control valve and the fourth control valve can be closed, and the second control valve and the third control valve can be opened. At this time, the commutation control member connects the outflow end of the power source assembly to the second communication pipeline; the medium flowing out of the power source assembly enters the second communication pipeline 22 through the commutation control member, and then enters the second heat exchanger 5 for heat exchange. After the medium flows out of the second heat exchanger 5, it enters the series pipeline 23, and then enters the first heat exchanger 4 for heat exchange. At this time, both heat exchangers work as condensers, with high heating intensity and high heating efficiency. After the medium flows out of the first heat exchanger 4, it enters the circulation heat exchanger 3. After the medium flows out of the circulation heat exchanger 3, it flows back to the power source assembly through the first communication pipeline 21.

[0037] In the heat pump thermal management system with dual-purpose heat exchangers provided in this embodiment, the first heat exchanger 4 and the second heat exchanger 5 can be used as condensers simultaneously and can also be used as evaporators simultaneously. Without increasing the number of evaporators and condensers, the heat exchange area is increased, the heat exchange efficiency is improved, and the heat exchange effect is improved.

[0038] The circulation heat exchanger 3 has a reversible flow structure, and the inlet and outlet directions of the medium are opposite in the refrigeration mode and the heating mode.

[0039] Elements for detecting the pressure and temperature of the medium can also be provided in the heat pump thermal management system with dual-purpose heat exchangers.

[0040] Specifically, as Figures 1 to 11 shown, in the heat pump thermal management system with dual-purpose heat exchangers of this embodiment, the first heat exchanger 4 includes a first interface 401 and a second interface 402, the second heat exchanger 5 includes a third interface 501 and a fourth interface 502, and the circulation heat exchanger 3 includes a first circulation interface 301 and a second circulation interface 302; the communication loop includes an outflow side pipeline 201, an intermediate pipeline 202, and an inflow side pipeline 203; the outflow side pipeline 201 is connected between the outflow end of the power source assembly and the first circulation interface 301, the intermediate pipeline 202 is connected between the second circulation interface 302 and the first interface 401, and the inflow side pipeline 203 is connected between the second interface 402 and the inflow end of the power source assembly; the first communication pipeline 21 is connected between the outflow side pipeline 201 and the inflow end of the power source assembly, the second communication pipeline 22 is connected between the outflow end of the power source assembly and the third interface 501, the first branch pipeline 24 is connected between the second communication pipeline 22 and the inflow side pipeline 203, and the series pipeline is connected between the fourth interface 502 and the inflow side pipeline 203; the first control valve is provided on the inflow side pipeline 203 and is located between the connection point of the inflow side pipeline 203 and the series pipeline 23 and the connection point of the inflow side pipeline 203 and the first branch pipeline 24; the outflow end of the power source assembly can be connected to the outflow side pipeline 201 or the second communication pipeline 22 through the commutation control member.

[0041] It can be understood that the first interface 401 and the second interface 402 are both connected to the heat exchange core of the first heat exchanger 4, the third interface 501 and the fourth interface 502 are both connected to the heat exchange core of the second heat exchanger 5, and the first circulation interface 301 and the second circulation interface 302 are both connected to the heat exchange core of the circulation heat exchanger 3.

[0042] In this embodiment, during refrigeration, the first control valve and the second control valve can be closed, and the third control valve and the fourth control valve can be opened. At this time, the outflow end of the power source assembly is connected to the outflow side pipeline 201, the series pipeline 23 is opened, the pipeline between the second interface 402 and the inflow end of the power source assembly is closed, and the pipeline between the second communication pipeline 22 and the inflow end of the power source assembly is opened; the medium flows out from the outflow end of the power source assembly and enters the outflow side pipeline 201, then enters the heat exchange core in the circulation heat exchanger 3 through the first circulation interface 301. The medium flows out from the second circulation interface 302 and enters the intermediate pipeline 202, then enters the heat exchange core in the first heat exchanger 4 through the first interface 401, then flows out from the second interface 402 and enters the series pipeline 23, then enters the heat exchange core in the second heat exchanger 5 through the fourth interface 502, then flows out from the third interface 501 and enters the second communication pipeline 22, then enters the inflow side pipeline 203 from the second communication pipeline 22, and finally flows back to the power source assembly from the inflow side pipeline 203 to complete the refrigeration cycle. If forced refrigeration is not required, the first control valve can be opened and the third control valve can be closed. At this time, the series pipeline 23 is closed, and the pipeline between the second interface 402 and the inflow end of the power source assembly is opened. Then the medium flows out from the second interface 402 and directly flows back to the power source assembly through the inflow side pipeline 203 without entering the second heat exchanger 5.

[0043] During heating, the first control valve and the fourth control valve are closed, and the second control valve and the third control valve are opened. At this time, the outflow end of the power source assembly is connected to the second communication pipeline 22 through the commutation control member; the medium enters the second communication pipeline 22 from the outflow end of the power source assembly through the commutation control member, then enters the second heat exchanger 5 through the third interface 501, flows out from the fourth interface 502 after passing through the heat exchange core of the second heat exchanger 5, then enters the first heat exchanger 4 through the series pipeline 23 and the second interface 402. The medium flows out through the first interface 401 to the intermediate pipeline 202 after passing through the heat exchange core of the first heat exchanger 4, then enters the circulation heat exchanger 3 through the second circulation interface 302. The medium flows out from the first circulation interface 301 to the first communication pipeline 21 after passing through the heat exchange core of the circulation heat exchanger 3, and then flows back into the power source assembly from the first communication pipeline 21 to complete the heating cycle.

[0044] As Figures 1 to 11As shown, based on any of the above embodiments, further, the heat pump thermal management system with dual-purpose heat exchangers further includes a third heat exchanger 6, a fifth control valve, and a second branch pipeline 25. The third heat exchanger 6 is connected between the intermediate pipeline 202 and the inflow end of the power source assembly through the second branch pipeline 25. The fifth control valve is arranged on the second branch pipeline 25. Specifically, the fifth control valve can be located on the side of the second branch pipeline 25 that communicates with the intermediate pipeline 202. The third heat exchanger 6 is used for heat exchange with the heat-generating component.

[0045] In this embodiment, setting the third heat exchanger 6 can cool the heat-generating components on the vehicle (such as batteries or generators, etc.), or recover the waste heat of the heat-generating components for heating.

[0046] As Figures 1 to 11 shown, based on any of the above embodiments, further, the heat pump thermal management system with dual-purpose heat exchangers further includes a sixth control valve; the sixth control valve is arranged on the intermediate pipeline 202. The sixth control valve can control the circulation, closing, or flow rate of the circulation heat exchanger 3, so as to achieve more mode control purposes.

[0047] As Figures 1 to 11 shown, based on any of the above embodiments, further, the heat pump thermal management system with dual-purpose heat exchangers further includes a third branch pipeline 26 and a seventh control valve; the third branch pipeline 26 is connected between the outflow side pipeline 201 and the fourth interface 502, and the series pipeline 23 is connected between the inflow side pipeline 203 and the third branch pipeline 26; the seventh control valve is arranged on the third branch pipeline 26 and is located between the connection point of the third branch pipeline 26 and the series pipeline 23 and the connection point of the third branch pipeline 26 and the outflow side pipeline 201. Setting the third branch pipeline 26 and the seventh control valve is beneficial to realizing the dehumidification work of the heat pump thermal management system with dual-purpose heat exchangers, and the specific working process will be described below.

[0048] Based on any of the above embodiments, the commutation control member can be a three-way solenoid valve, which can make the pipeline structure of the heat pump thermal management system with dual-purpose heat exchangers simple.

[0049] Or, as Figures 1 to 11 shown, the heat pump thermal management system with dual-purpose heat exchangers further includes a fourth branch pipeline 27 and a fifth branch pipeline 28; the fourth branch pipeline 27 is connected between the outflow end of the power source assembly and the second connection pipeline 22, and the fifth branch pipeline 28 is connected between the outflow end of the power source assembly and the outflow side pipeline 201; the commutation control member includes a first solenoid valve 7 (for controlling the pipeline switch) and a second solenoid valve 8 (for controlling the pipeline switch), the first solenoid valve 7 is arranged on the fourth branch pipeline 27, and the second solenoid valve 8 is arranged on the fifth branch pipeline 28.

[0050] In this embodiment, the purpose of controlling the medium to change direction is achieved through the mutual cooperation of the first solenoid valve 7 and the second solenoid valve 8. When it is necessary to connect the outflow end of the power source assembly to the outflow side pipeline 201, the second solenoid valve 8 is opened and the first solenoid valve 7 is closed. When it is necessary to connect the outflow end of the power source assembly to the second connection pipeline 22, the first solenoid valve 7 is opened and the second solenoid valve 8 is closed.

[0051] As Figure 11 shown, based on any of the above embodiments, further, the heat pump thermal management system with dual-purpose heat exchangers further includes a one-way pipeline 30 and a parallel one-way valve 29; the one-way pipeline 30 is connected between the intermediate pipeline 202 and the series pipeline 23, and the parallel one-way valve 29 is arranged on the one-way pipeline 30.

[0052] In this embodiment, during refrigeration, after the medium flows out of the fourth electronic expansion valve 15, a part of the medium (for example, refrigerant) flows into the first heat exchanger 4 through the first interface 401, and a part of the medium passes through the parallel one-way valve 29 and the second electronic expansion valve 13 and enters the second heat exchanger 5 through the fourth interface 502, so as to realize the parallel refrigeration of the first heat exchanger 4 and the second heat exchanger 5. That is, the purpose of adding the one-way pipeline 30 and the parallel one-way valve 29 can realize that the first heat exchanger 4 and the second heat exchanger 5 are connected in parallel as an evaporator in the refrigeration mode.

[0053] Based on any of the above embodiments, further, the commutation control member, the second control valve and the seventh control valve can be integrated into a multi-way solenoid valve, so as to simplify the pipeline structure.

[0054] As Figures 2 to 10 shown, based on any of the above embodiments, further, the heat pump thermal management system with dual-purpose heat exchangers further includes an interface parallel pipeline 31, and the second heat exchanger 5 further includes a fifth interface 503; the interface parallel pipeline 31 is connected between the second connection pipeline 22 and the fifth interface 503; on the second connection pipeline 22, an eighth control valve is arranged between the connection point of the second connection pipeline 22 and the interface parallel pipeline 31 and the third interface 501, and a ninth control valve is arranged on the interface parallel pipeline 31.

[0055] In this embodiment, the flow rate of the medium entering the second heat exchanger 5 can be controlled by the eighth control valve and the ninth control valve, so as to realize the dual-temperature zone function, avoid setting a temperature air door, and reduce the production cost.

[0056] Based on the above embodiments, the first control valve, the second control valve, and the seventh control valve can all be valves that achieve opening and closing. For example, the first control valve is the third solenoid valve 9, the second control valve is the fourth solenoid valve 10, and the seventh control valve is the fifth solenoid valve 11; the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the eighth control valve, and the ninth control valve can all be valves that can adjust the flow rate. Preferably, they are all electronic expansion valves, which can be: the third control valve is the first electronic expansion valve 12, the fourth control valve is the second electronic expansion valve 13, the fifth control valve is the third electronic expansion valve 14, the sixth control valve is the fourth electronic expansion valve 15, the eighth control valve is the fifth electronic expansion valve 16, and the ninth control valve is the sixth electronic expansion valve 17.

[0057] Specifically, the power source assembly includes a compressor 1 and a gas-liquid separator 2. The inlet end of the gas-liquid separator 2 is the inlet end of the power source assembly, and the outlet end of the compressor 1 is the outlet end of the power source assembly. The outlet end of the gas-liquid separator 2 is connected to the inlet end of the compressor 1. The gas-liquid separator 2 can be a double-tube type or a U-tube type, and the structure is not limited. It mainly plays roles such as separating liquid refrigerant and gaseous refrigerant, storing liquid, returning oil, drying, and filtering, and can prevent the compressor 1 from lacking oil and wet compression.

[0058] Specifically, a blower 18 is provided on one side of the first heat exchanger 4, which can suck in air and pass it through the first heat exchanger 4, or blow it into the passenger compartment through the first heat exchanger 4 and the second heat exchanger 5.

[0059] Next, the working process of the heat pump thermal management system with dual-purpose heat exchangers (taking the Figure 2 heat pump thermal management system with dual-purpose heat exchangers shown as an example) in different working modes will be described. The medium is taken as refrigerant:

[0060] As Figure 3 shown, the refrigeration mode of the heat pump thermal management system with dual-purpose heat exchangers:

[0061] The first solenoid valve 7, the third solenoid valve 9, the fourth solenoid valve 10, and the fifth solenoid valve 11 are all closed, and the second solenoid valve 8 is opened; the first electronic expansion valve 12, the second electronic expansion valve 13, the fourth electronic expansion valve 15, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 are all opened, the third electronic expansion valve 14 is closed, and the blower 18 is turned on; the compressor 1 discharges high-temperature and high-pressure refrigerant (high temperature and high pressure are relative. The refrigerant flowing out of the compressor has a higher temperature and pressure than the refrigerant flowing back into the compressor) and flows into the circulation heat exchanger 3 through the second solenoid valve 8, then passes through the fourth electronic expansion valve 15 and flows into the first heat exchanger 4 through the first interface 401. At this time, the fourth electronic expansion valve 15 throttles; the refrigerant evaporates and absorbs heat in the first heat exchanger 4 and then flows out through the second interface 402 to the series pipeline 23, passes through the first electronic expansion valve 12 on the series pipeline 23, and then flows into the second heat exchanger 5 through the fourth interface 502. At this time, the first electronic expansion valve 12 can be fully opened. The refrigerant continues to evaporate and absorb heat in the second heat exchanger 5, and then the refrigerant flows out through the third interface 501, the fifth electronic expansion valve 16, the fifth interface 503, and the sixth electronic expansion valve 17 respectively; the refrigerant flowing out enters the second communication pipeline 22 and flows into the gas-liquid separator 2 after passing through the second electronic expansion valve 13. At this time, the second electronic expansion valve 13, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 can all be fully opened; the refrigerant is separated and dried in the gas-liquid separator 2 and then flows into the compressor 1, thus completing the refrigerant refrigeration mode cycle. The blower 18 inhales air, exchanges heat through the first heat exchanger 4 and the second heat exchanger 5, and then blows it into the passenger compartment to achieve passenger compartment refrigeration.

[0062] When the refrigeration mode is running, if people have a low demand for passenger compartment refrigeration, the first electronic expansion valve 12, the second electronic expansion valve 13, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 can be all closed, and the third solenoid valve 9 is opened; at this time, the refrigerant flowing out from the second interface 402 directly flows into the gas-liquid separator 2 for gas-liquid separation, that is, the refrigerant does not flow into the second heat exchanger 5 to exchange heat with air. The other flow modes of the refrigerant are the same as the above flow process and will not be elaborated here.

[0063] When the dual-zone refrigeration mode is running, it is only necessary to adjust the opening degrees of the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17, that is, to control the flow rate of the refrigerant flowing out of the second heat exchanger 5 to control the heat exchange amount between the refrigerant and air. The other flow modes of the refrigerant are the same as the above flow process and will not be elaborated here.

[0064] As Figure 4 shown, the refrigeration mode and the forced cooling mode of the heating component of the heat pump thermal management system with dual-purpose heat exchangers:

[0065] When this mode is run when both the temperature of the passenger compartment and the temperature of the heat-generating components need to be controlled, the passenger compartment can be cooled and the heat-generating components can be cooled simultaneously. The first solenoid valve 7, the third solenoid valve 9, the fourth solenoid valve 10, and the fifth solenoid valve 11 are all closed, and the second solenoid valve 8 is opened; the first electronic expansion valve 12, the second electronic expansion valve 13, the third electronic expansion valve 14, the fourth electronic expansion valve 15, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 are all opened, and the blower 18 is turned on; the high-temperature and high-pressure refrigerant discharged by the compressor 1 flows into the circulation heat exchanger 3 through the second solenoid valve 8, and then branches into two paths after passing through the fourth electronic expansion valve 15 (at this time, the fourth electronic expansion valve 15 throttles), one path flows into the third heat exchanger 6 after passing through the third electronic expansion valve 14, and the other path flows into the first heat exchanger 4 through the first interface 401; the refrigerant evaporates and absorbs heat in the first heat exchanger 4 and then flows out through the second interface 402 to the series pipeline 23, and then flows into the second heat exchanger 5 through the fourth interface 502 after passing through the first electronic expansion valve 12 (at this time, the first electronic expansion valve 12 can be fully opened), the refrigerant continues to evaporate and absorb heat in the second heat exchanger 5, and then flows out through the third interface 501, the fifth electronic expansion valve 16, the fifth interface 503, and the sixth electronic expansion valve 17 respectively; the medium flowing out of the second heat exchanger 5 flows through the second electronic expansion valve 13 and then converges with the refrigerant flowing out of the third heat exchanger 6 and flows into the gas-liquid separator 2 together. At this time, the second electronic expansion valve 13, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 can all be fully opened; the refrigerant is separated and dried in the gas-liquid separator 2 and then flows into the compressor 1 to complete the refrigerant refrigeration mode and the heat-generating component forced cooling mode cycle. The air inhaled by the blower 18 is blown into the passenger compartment after heat exchange in the first heat exchanger 4 and the second heat exchanger 5 to achieve passenger compartment refrigeration. The third heat exchanger 6 exchanges heat with the heat-generating components to cool the heat exchange components.

[0066] When this mode is running, if people have a low demand for passenger compartment refrigeration, the first electronic expansion valve 12, the second electronic expansion valve 13, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 can all be closed, and the third solenoid valve 9 is opened. The refrigerant flowing out through the second interface 402 directly flows into the gas-liquid separator 2 for gas-liquid separation, that is, the refrigerant does not flow into the second heat exchanger 5 for heat exchange with the air. The other flow modes of the refrigerant are the same as the above flow process and will not be elaborated here.

[0067] As Figure 5 shown, the heat-generating component forced cooling mode of the heat pump thermal management system with dual-purpose heat exchangers:

[0068] There is no refrigeration requirement in the crew cabin. When the heat-generating components exceed the temperature controlled by the heat pump thermal management system with dual-purpose heat exchangers, only the heat-generating components are cooled. Close the first solenoid valve 7, the third solenoid valve 9, the fourth solenoid valve 10, and the fifth solenoid valve 11, and open the second solenoid valve 8; close the first electronic expansion valve 12, the second electronic expansion valve 13, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17, open the third electronic expansion valve 14 and the fourth electronic expansion valve 15, and turn off the blower 18. The high-temperature and high-pressure refrigerant discharged from the compressor 1 flows into the circulation heat exchanger 3 through the second solenoid valve 8, and then flows into the third heat exchanger 6 after passing through the fourth electronic expansion valve 15 and the third electronic expansion valve 14. At this time, the fourth electronic expansion valve 15 can be fully opened, and the third electronic expansion valve 14 throttles; the refrigerant evaporates and absorbs heat in the third heat exchanger 6 and then flows out to the gas-liquid separator 2. The refrigerant is gas-liquid separated and dried in the gas-liquid separator 2 and then flows into the compressor 1, thus completing the forced cooling mode cycle of the heat-generating components.

[0069] As Figure 6 shown, the heating mode of the heat pump thermal management system with dual-purpose heat exchangers:

[0070] Close the second solenoid valve 8, the third solenoid valve 9, and the fifth solenoid valve 11, and open the first solenoid valve 7 and the fourth solenoid valve 10; close the second electronic expansion valve 13 and the third electronic expansion valve 14, and open the first electronic expansion valve 12, the fourth electronic expansion valve 15, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17, and turn on the blower 18. The refrigerant discharged from the compressor 1 passes through the first solenoid valve 7 and then flows into the corresponding second heat exchanger 5 through the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 respectively through the corresponding third interface 501 and the fifth interface 503 to condense and release heat. At this time, both the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 can adjust the flow rate. When both are fully opened, it is single-zone heating for the crew cabin. When the flow rate is distributed through control adjustment, dual-zone heating for the crew cabin can be achieved. The refrigerant flows out from the fourth interface 502 of the second heat exchanger 5 and into the series pipeline 23. After the medium passes through the first electronic expansion valve 12, it flows into the first heat exchanger 4 through the second interface 402 to condense and release heat. The refrigerant after releasing heat flows out from the first interface 401 to the intermediate pipeline 202, and then the medium is throttled by the fourth electronic expansion valve 15 and flows into the circulation heat exchanger 3 to evaporate and absorb heat, and flows out from the first circulation interface 301 of the circulation heat exchanger 3 and enters the gas-liquid separator 2 through the fourth solenoid valve 10. The refrigerant is gas-liquid separated and dried in the gas-liquid separator 2 and then flows into the compressor 1, thus completing the refrigerant heating mode cycle. The blower 18 inhales the air in the environment and blows it into the crew cabin after heat exchange through the first heat exchanger 4 and the second heat exchanger 5 in sequence to achieve heating of the crew cabin.

[0071] As Figure 7As shown, the heat recovery mode of the heat generating component of the heat pump thermal management system with dual-purpose heat exchangers:

[0072] When heating the passenger compartment, there is excess heat in the heat generating component circuit for the system to recover waste heat, which will reduce the system energy consumption. At this time, the second solenoid valve 8, the third solenoid valve 9, the fourth solenoid valve 10 and the fifth solenoid valve 11 are all closed, and the first solenoid valve 7 is opened; the second electronic expansion valve 13 and the fourth electronic expansion valve 15 are both closed, the first electronic expansion valve 12, the third electronic expansion valve 14, the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 are all opened, and the blower 18 is opened. The refrigerant discharged from the compressor 1 passes through the first solenoid valve 7 and then through the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 respectively, and then flows into the second heat exchanger 5 through the corresponding third interface 501 and fifth interface 503 for condensation and heat release. At this time, both the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 can adjust the flow rate. When both are fully opened, it is for heating the single temperature zone of the passenger compartment. When the flow rate is distributed by controlling and adjusting the two, dual temperature zone heating of the passenger compartment can be achieved. The refrigerant flows out from the fourth interface 502 of the second heat exchanger 5 and flows to the series pipeline 23. After the medium passes through the first electronic expansion valve 12, it flows into the first heat exchanger 4 through the second interface 402 for condensation and heat release. The refrigerant after heat release flows out through the first interface 401 and enters the intermediate pipeline 202. After being throttled by the third electronic expansion valve 14, it flows into the third heat exchanger 6 for evaporation and heat absorption, and then enters the gas-liquid separator 2. The refrigerant is gas-liquid separated and dried in the gas-liquid separator 2 and then flows into the compressor 1, thus completing the cycle of the refrigerant heat recovery mode. The blower 18 inhales the air in the environment and blows it into the passenger compartment after heat exchange through the first heat exchanger 4 and the second heat exchanger 5 in sequence to achieve heating of the passenger compartment. The third heat exchanger exchanges heat with the heat generating component to absorb the waste heat of the heat generating component.

[0073] As Figure 8 shown, the compressor self-heating heating mode of the heat pump thermal management system with dual-purpose heat exchangers:

[0074] In a lower temperature environment, when the vehicle is cold-started and the passenger compartment is heated, the heat pump thermal management system with dual-purpose heat exchangers will switch to the compressor 1 self-heating heating passenger compartment mode, leading the gaseous refrigerant at the outlet of the compressor 1 to the inlet of the gas-liquid separator 2 to increase the suction density of the compressor 1, thereby improving the heating capacity of the heat pump thermal management system with dual-purpose heat exchangers.

[0075] When the compressor 1 operates in the self-heating heating mode, the second solenoid valve 8, the third solenoid valve 9, the fourth solenoid valve 10, and the fifth solenoid valve 11 are all closed, and the first solenoid valve 7 is opened; the fourth electronic expansion valve 15 is closed, and the first electronic expansion valve 12, the second electronic expansion valve 13, the third electronic expansion valve 14, the fourth electronic expansion valve 15, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 are all opened, and the blower 18 is turned on. The refrigerant discharged from the compressor 1 branches into two paths through the first solenoid valve 7. One path flows into the gas-liquid separator 2 after throttling through the second electronic expansion valve 13; the other path flows into the second heat exchanger 5 through the corresponding third interface 501 and fifth interface 503 after passing through the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 respectively to condense and release heat. Both the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 can adjust the flow rate. When both are fully opened, it is for heating in a single temperature zone in the passenger compartment. When the flow rate is distributed through control adjustment, dual-zone heating in the passenger compartment can be achieved. After the refrigerant flows out from the fourth interface 502 of the second heat exchanger 5, it enters the series pipeline 23. Then, after the medium passes through the first electronic expansion valve 12, it flows into the first heat exchanger 4 through the second interface 402 to continue condensing and releasing heat; the refrigerant after condensing and releasing heat flows out from the first interface 401 to the intermediate pipeline 202. Then, the medium flows into the third heat exchanger 6 after throttling through the third electronic expansion valve 14. At this time, it is controlled that no other fluid flows in the third heat exchanger 6, that is, the medium does not exchange heat with other fluids in the third heat exchanger 6. The third heat exchanger 6 only serves as a connecting channel. The refrigerant flowing out from the third heat exchanger 6 converges with the refrigerant flowing out from the second electronic expansion valve 13 and flows into the gas-liquid separator 2 together. After gas-liquid separation and drying in the gas-liquid separator 2, it flows into the compressor 1 to complete the cycle of the self-heating heating mode of the compressor 1. The blower 18 inhales the air in the environment, passes through the first heat exchanger 4 and the second heat exchanger 5 in sequence for heat exchange, and then blows into the passenger compartment to achieve heating in the passenger compartment.

[0076] As Figure 9 shown, the dehumidification mode 1 of the heat pump thermal management system with dual-purpose heat exchanger:

[0077] When the humidity in the passenger compartment is too high, the heat pump thermal management system with dual-purpose heat exchangers will operate in the dehumidification mode. When the dehumidification mode is operating, the second solenoid valve 8 and the fourth solenoid valve 10 are closed, and the first solenoid valve 7, the third solenoid valve 9 and the fifth solenoid valve 11 are all opened; the first electronic expansion valve 12, the second electronic expansion valve 13 and the third electronic expansion valve 14 are all closed, and the fourth electronic expansion valve 15, the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 are all opened, and the blower 18 is turned on. After the refrigerant discharged from the compressor 1 passes through the first solenoid valve 7, it passes through the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17 respectively, and then flows into the second heat exchanger 5 through the corresponding third interface 501 and the fifth interface 503. After the refrigerant releases heat in the second heat exchanger 5, it flows out of the third pipeline 26 through the fourth interface 502. Then the medium flows into the circulation heat exchanger 3 through the fifth solenoid valve 11 to continue condensing and releasing heat. After condensing and releasing heat, the refrigerant is throttled by the fourth electronic expansion valve 15. Then the medium flows into the first heat exchanger 4 through the first interface 401. The medium absorbs the heat of the air in the first heat exchanger 4 to reduce the air humidity, and then flows out through the second interface 402 to the inflow side pipeline 203, and then flows into the gas-liquid separator 2 through the third solenoid valve 9. The refrigerant is separated and dried in the gas-liquid separator 2 and then flows into the compressor 1. The wet air inhaled by the blower 18 from the passenger compartment is cooled and dehumidified by the first heat exchanger 4, and then absorbs heat and warms up through the second heat exchanger 5 to maintain the comfort of the passenger compartment. In this way, the dehumidification of the passenger compartment is realized. This method is applicable to the dehumidification under the working conditions where the ambient temperature is relatively high and the heating demand of the passenger compartment is not high.

[0078] As Figure 10 shown, the dehumidification mode two of the heat pump thermal management system with dual-purpose heat exchangers:

[0079] The second solenoid valve 8, the third solenoid valve 9, and the fifth solenoid valve 11 are closed, while the first solenoid valve 7 and the fourth solenoid valve 10 are open; the second electronic expansion valve 13 and the third electronic expansion valve 14 are closed, while the first electronic expansion valve 12, the fourth electronic expansion valve 15, the fifth electronic expansion valve 16, and the sixth electronic expansion valve 17 are all open, and the blower 18 is turned on. After the refrigerant discharged from the compressor 1 passes through the first solenoid valve 7, it respectively passes through the fifth electronic expansion valve 16 and the sixth electronic expansion valve 17, and then flows into the second heat exchanger 5 through the corresponding third interface 501 and fifth interface 503. After releasing heat in the second heat exchanger 5, the refrigerant flows out through the fourth interface 502 and then into the series pipeline 23. The medium passes through the first electronic expansion valve 12 and throttles into the first heat exchanger 4 from the second interface 402. The refrigerant absorbs the heat of the air in the first heat exchanger 4 to reduce the air humidity, and then flows into the intermediate pipeline 202 through the second interface 402, and then into the circulating heat exchanger 3 to continue evaporating and absorbing heat. The opening degree of the fourth electronic expansion valve 15 is determined by the ambient temperature and the control target. After absorbing heat, the refrigerant flows into the gas-liquid separator 2 through the fourth solenoid valve 10 and then enters the compressor 1. The wet air inhaled by the blower 18 from the passenger compartment is cooled and dehumidified by the first heat exchanger 4, and then absorbs heat and warms up through the second heat exchanger 5 to maintain the comfort of the passenger compartment. In this way, the cycle is repeated to achieve the dehumidification of the passenger compartment. This method is applicable to the working conditions where the ambient temperature is relatively low and the heating demand of the passenger compartment is relatively high for dehumidification.

[0080] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements on some or all of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present invention. In the specification provided here, a large number of specific details are described. However, it can be understood that the embodiments of the present invention can be practiced without these specific details. In some instances, well-known methods, structures, and technologies are not shown in detail so as not to obscure the understanding of this specification. In addition, those skilled in the art can understand that although some embodiments described herein include certain features included in other embodiments but not other features, the combination of the features of different embodiments means that it is within the scope of the present invention and forms different embodiments.

Claims

1. A heat pump thermal management system that can be used for two purposes in a heat exchanger, characterized in that, it includes: a power source assembly, a commutation control member, a circulating heat exchanger (3), a communication loop, a first heat exchanger (4) and a second heat exchanger (5); the first heat exchanger (4), the circulating heat exchanger (3) and the power source assembly are connected to the communication loop, and a first control valve is provided at the inflow end of the communication loop near the power source assembly; it further includes a first communication pipeline (21); the first communication pipeline (21) is communicated between the communication loop and the inflow end of the power source assembly, and the connection point of the first communication pipeline (21) and the communication loop is located on the side where the circulating heat exchanger (3) is communicated with the outflow end of the power source assembly, and a second control valve is provided on the first communication pipeline (21); it further includes a second communication pipeline (22) and a series pipeline (23); the second communication pipeline (22) is communicated between the outflow end of the power source assembly and the second heat exchanger (5); the series pipeline (23) is communicated between the first heat exchanger (4) and the second heat exchanger (5), and a third control valve is provided on the series pipeline (23); a first branch pipeline (24) is communicated between the second communication pipeline (22) and the inflow end of the power source assembly, and a fourth control valve is provided on the first branch pipeline (24); the outflow end of the power source assembly can be communicated with the communication loop or the second communication pipeline (22) through the commutation control member; the first heat exchanger (4) includes a first interface (401) and a second interface (402), the second heat exchanger (5) includes a third interface (501) and a fourth interface (502), and the circulating heat exchanger (3) includes a first circulation interface (301) and a second circulation interface (302); the communication loop includes an outflow side pipeline (201), an intermediate pipeline (202) and an inflow side pipeline (203); the outflow side pipeline (201) is communicated between the outflow end of the power source assembly and the first circulation interface (301), the intermediate pipeline (202) is communicated between the second circulation interface (302) and the first interface (401), and the inflow side pipeline (203) is communicated between the second interface (402) and the inflow end of the power source assembly; The first connecting pipeline (21) is connected between the outflow side pipeline (201) and the inflow end of the power source assembly. The second connecting pipeline (22) is connected between the outflow end of the power source assembly and the third interface (501). The first branch pipeline (24) is connected between the second connecting pipeline (22) and the inflow side pipeline (203). The series pipeline (23) is connected between the fourth interface (502) and the inflow side pipeline (203). The first control valve is arranged on the inflow side pipeline (203) and is located between the connection point of the inflow side pipeline (203) and the series pipeline (23) and the connection point of the inflow side pipeline (203) and the first branch pipeline (24). The outflow end of the power source assembly can be connected to the outflow side pipeline (201) or the second connecting pipeline (22) through the commutation control member.

2. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, it further includes a third heat exchanger (6), a fifth control valve and a second branch pipeline (25). The third heat exchanger (6) is connected between the intermediate pipeline (202) and the inflow end of the power source assembly through the second branch pipeline (25). The fifth control valve is arranged on the second branch pipeline (25).

3. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, it further includes a sixth control valve. The sixth control valve is arranged on the intermediate pipeline (202).

4. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, it further includes a third branch pipeline (26) and a seventh control valve. The third branch pipeline (26) is connected between the outflow side pipeline (201) and the fourth interface (502). The series pipeline (23) is connected between the inflow side pipeline (203) and the third branch pipeline (26). The seventh control valve is arranged on the third branch pipeline (26) and is located between the connection point of the third branch pipeline (26) and the series pipeline (23) and the connection point of the third branch pipeline (26) and the outflow side pipeline (201).

5. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, the commutation control member is a three-way solenoid valve.

6. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, it further includes a fourth branch pipeline (27) and a fifth branch pipeline (28). The fourth branch pipeline (27) is connected between the outflow end of the power source assembly and the second connecting pipeline (22). The fifth branch pipeline (28) is connected between the outflow end of the power source assembly and the outflow side pipeline (201). The commutation control member includes a first solenoid valve (7) and a second solenoid valve (8). The first solenoid valve (7) is arranged on the fourth branch pipeline (27), and the second solenoid valve (8) is arranged on the fifth branch pipeline (28).

7. The heat pump thermal management system with dual-purpose heat exchanger according to claim 1, characterized in that, it further includes a one-way pipeline (30) and a parallel one-way valve (29); the one-way pipeline (30) is connected between the intermediate pipeline (202) and the series pipeline (23), and the parallel one-way valve (29) is arranged on the one-way pipeline (30).

8. The heat pump thermal management system with dual-purpose heat exchanger according to claim 4, characterized in that, the commutation control member, the second control valve and the seventh control valve are integrated into a multi-way solenoid valve.

9. The heat pump thermal management system with dual-purpose heat exchanger according to any one of claims 1-8, characterized in that, it further includes an interface parallel pipeline (31), and the second heat exchanger (5) further includes a fifth interface (503); the interface parallel pipeline (31) is connected between the second communication pipeline (22) and the fifth interface (503); on the second communication pipeline (22), an eighth control valve is arranged between the connection point of the second communication pipeline (22) and the interface parallel pipeline (31) and the third interface (501), and a ninth control valve is arranged on the interface parallel pipeline (31).

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