Thermal management device and vehicle

Abstract

The invention relates to the technical field of heat management devices, in particular to a heat management device and a vehicle. The heat management device comprises a first circulation loop and a second circulation loop, the first circulation loop comprises a first heat exchanger, a compressor and a second heat exchanger, the second heat exchanger comprises a first heat exchange channel and a second heat exchange channel, and the first heat exchange channel is connected with the first heat exchanger and the compressor. The second circulation loop comprises a second heat exchanger and a heat exchange assembly, the heat exchange assembly is connected with the second heat exchange channel, and the heat exchange assembly is suitable for exchanging heat with at least part of the driving assembly. In this way, the heat exchange assembly can be coupled with the first heat exchanger, the compressor and the second heat exchanger, and integration and light weight of the heat management device can be achieved easily.

Description

Technical Field

[0001] This invention relates to the field of thermal management device technology, and more particularly to a thermal management device and vehicle. Background Technology

[0002] In existing vehicles, the electric drive and electronic control components are typically temperature-controlled independently using liquid cooling systems, while batteries, air conditioning, and onboard refrigerators use refrigerant cooling. This means that vehicles need at least two cooling systems, including a liquid cooling system and a refrigerant cooling system. Having at least two cooling systems occupies a significant amount of interior space, hindering vehicle integration and weight reduction. Summary of the Invention

[0003] To address the aforementioned issues, embodiments of this application provide a thermal management device and a vehicle.

[0004] In a first aspect, embodiments of this application provide a thermal management device adapted to supply refrigerant flow, comprising: The first circulation loop includes a first heat exchanger, a compressor, and a second heat exchanger. The second heat exchanger includes a first heat exchange channel and a second heat exchange channel. The first heat exchange channel is connected to the first heat exchanger and the compressor, respectively. The second circulation loop includes the second heat exchanger and a heat exchange assembly, the heat exchange assembly being connected to the second heat exchange channel and adapted to exchange heat with at least a portion of the drive assembly.

[0005] Optionally, the heat exchange assembly includes a first cold plate adapted to exchange heat with the electronic control components of the drive assembly; and / or The heat exchange assembly includes a second cold plate adapted to exchange heat with the electric drive component of the drive assembly.

[0006] Optionally, the first port of the first cold plate and the first port of the second cold plate are respectively connected to the second port of the second heat exchange channel, and the second port of the first cold plate and the second port of the second cold plate are respectively connected to the first port of the second heat exchange channel. Alternatively, the first port of the first cold plate is connected to the second port of the second heat exchange channel, the first port of the second cold plate is connected to the second port of the first cold plate, and the second port of the second cold plate is connected to the first port of the second heat exchange channel.

[0007] Optionally, the thermal management device includes a power pump, a first control valve, a second control valve, a third control valve, and a fourth control valve; The second port of the power pump is connected to the first port of the heat exchange assembly. The first port of the power pump is connected to the second port of the first control valve and the second port of the second control valve. The first port of the first control valve is connected to the second port of the first heat exchanger. The first port of the second control valve is connected to the second port of the second heat exchange channel. The second port of the heat exchange component is connected to the first port of the third control valve and the first port of the fourth control valve. The second port of the third control valve is connected to the first port of the second heat exchange channel, and the second port of the fourth control valve is connected to the first port of the first heat exchanger.

[0008] Optionally, the thermal management device includes a first liquid storage tank, a second port of the first liquid storage tank being connected to a first port of the power pump, and the first port of the first liquid storage tank being connected to a second port of the first control valve and a second port of the second control valve.

[0009] Optionally, the first circulation loop includes a first expansion valve; the second port of the compressor is connected to the first port of the first heat exchanger, the first port of the first expansion valve is connected to the second port of the first heat exchanger, the first port of the first heat exchange channel is connected to the second port of the first expansion valve, and the second port of the first heat exchange channel is connected to the first port of the compressor.

[0010] Optionally, the thermal management device includes a third heat exchanger and a second expansion valve, wherein a first port of the third heat exchanger is connected to a second port of the second expansion valve, a second port of the third heat exchanger is connected to a first port of the compressor, and a first port of the second expansion valve is connected to a second port of the first heat exchanger. And / or, the thermal management device includes a fourth heat exchanger and a third expansion valve, with a first port of the fourth heat exchanger connected to a second port of the third expansion valve, the second port of the fourth heat exchanger connected to a first port of the compressor, and the first port of the third expansion valve connected to a second port of the first heat exchanger.

[0011] Optionally, the thermal management device includes a fifth heat exchanger and a fourth expansion valve, wherein the first port of the fifth heat exchanger is connected to the first port of the compressor, or the first port of the fifth heat exchanger is connected to the second port of the compressor; The second port of the fifth heat exchanger is connected to the first port of the fourth expansion valve, and the second port of the fourth expansion valve is connected to the first port of the first expansion valve, the first port of the second expansion valve, the first port of the third expansion valve, and the second port of the first heat exchanger.

[0012] Optionally, the thermal management device includes a sixth heat exchanger and a seventh expansion valve. The first port of the sixth heat exchanger is connected to the first port of the compressor, and the second port of the sixth heat exchanger is connected to the first port of the seventh expansion valve. The second port of the seventh expansion valve is also connected to the first port of the first expansion valve, the first port of the second expansion valve, and the second port of the fourth expansion valve.

[0013] Optionally, the compressor has two first ports, one of which is connected to the first port of the fifth heat exchanger and the second port of the second heat exchange channel, and the other is connected to the second port of the third heat exchanger and the second port of the fourth heat exchanger.

[0014] Optionally, the thermal management device includes a second liquid storage tank, the first port of which is connected to the second port of the first heat exchanger, and the second port of which is connected to the first port of the first expansion valve, the first port of the second expansion valve, the first port of the third expansion valve, and the second port of the fourth expansion valve.

[0015] Optionally, the thermal management device includes a sixth expansion valve disposed between the second port of the second heat exchange channel and the first port of the compressor; and / or, the sixth expansion valve disposed between the second port of the third heat exchanger and the first port of the compressor; and / or, the sixth expansion valve disposed between the first port of the fifth heat exchanger and the first port of the compressor.

[0016] Optionally, the thermal management device includes a seventh expansion valve, which is disposed between the first port of the first heat exchanger and the second port of the compressor.

[0017] Optionally, the thermal management device includes an eighth expansion valve disposed between the first port of the fifth heat exchanger and the second port of the compressor.

[0018] Secondly, embodiments of this application provide a vehicle that includes any of the thermal management devices described in the first aspect.

[0019] Compared with prior art, the present invention has the following advantages: This application provides a thermal management device, specifically including a first circulation loop and a second circulation loop. The first circulation loop includes a first heat exchanger, a compressor, and a second heat exchanger. The second heat exchanger includes a first heat exchange channel and a second heat exchange channel, with the first heat exchange channel connected to both the first heat exchanger and the compressor. The second circulation loop includes a second heat exchanger and a heat exchange component, with the heat exchange component connected to the second heat exchange channel. The heat exchange component is adapted to exchange heat with at least a portion of the drive assembly. This allows for cooling of the heat exchange component through a refrigerant cooling system formed by the first heat exchanger, compressor, and second heat exchanger. Therefore, the heat source thermal management system consisting of the heat exchange component and at least a portion of the drive assembly can be coupled with the refrigerant cooling system formed by the first heat exchanger, compressor, and second heat exchanger, achieving integration and weight reduction of the thermal management device.

[0020] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, and in order to make the above and other objects, features and advantages of the present invention more apparent and understandable, specific embodiments of the present invention are described below. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the accompanying drawings used in the description of the embodiments will be briefly introduced below.

[0022] Figure 1 This is a system schematic diagram of the thermal management device described in some embodiments of the present invention; Figure 2 This is a system schematic diagram of the thermal management device described in some embodiments of the present invention; Figure 3 This is a system schematic diagram of the thermal management device described in some embodiments of the present invention; Figure 4 This is a system schematic diagram of the heat exchange assembly described in some embodiments of the present invention; Figure 5 This is a system schematic diagram of the heat exchange assembly described in some embodiments of the present invention; Reference numerals: 1. First heat exchanger; 1a. Electric fan; 2. Compressor; 3. Second heat exchanger; 3a. First heat exchange channel; 3b. Second heat exchange channel; 4. Heat exchange assembly; 4a. First cold plate; 4b. Second cold plate; 4c. Fifth control valve; 4d. Sixth control valve; 4e. Seventh control valve; 5. First expansion valve; 6. Power pump; 7. First control valve; 8. Second control valve; 9. Third control valve; 10. Fourth control valve; 11. First storage tank; 12. Third heat exchanger; 13. Second expansion valve; 14. Fourth heat exchanger; 15. Third expansion valve; 16. Fifth heat exchanger; 17. Fourth expansion valve; 18. Sixth heat exchanger; 19. Fifth expansion valve; 20. Gas-liquid separator; 21. Second storage tank; 22. Sixth expansion valve; 23. Seventh expansion valve; 24. Eighth expansion valve; 25. Check valve; 26. Eighth control valve. Detailed Implementation

[0023] Exemplary embodiments of the invention will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the invention are shown in the drawings, it should be understood that the invention can be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided to enable a more thorough understanding of the invention and to fully convey the scope of the invention to those skilled in the art.

[0024] In existing vehicles, the electric drive and electronic control components typically achieve independent temperature control through a liquid cooling system. This system generally includes components such as a radiator, power pump, coolant tank, and cold plate. The coolant in the tank flows into the cold plate under the action of the power pump to absorb heat from the electric drive and electronic control components, and then flows out into the radiator for cooling. Components such as batteries, air conditioning, and onboard refrigerators generally use a refrigerant refrigeration system for temperature control. This system typically includes a compressor, expansion valve, evaporator, and condenser. In the refrigerant refrigeration system, the refrigerant is compressed by the compressor and flows into the condenser to condense and release heat. Then, it flows through the expansion valve into the evaporator to evaporate and absorb heat.

[0025] The above setup requires the vehicle to have at least two cooling systems, including a liquid cooling system and a refrigerant cooling system. Having at least two cooling systems will occupy a significant amount of interior space, hindering vehicle integration and weight reduction.

[0026] refer to Figure 1 To address the aforementioned problems, in a first aspect, embodiments of this application provide a thermal management device suitable for supplying refrigerant. The refrigerant is a substance that circulates within the thermal management device, specifically including Freon, ammonia, hydrocarbons, etc. The refrigerant can absorb heat and cool down through evaporation within the thermal management device, or it can release heat and heat up through condensation.

[0027] refer to Figure 1 The thermal management device specifically includes a first circulation loop and a second circulation loop. The first circulation loop includes a first heat exchanger 1, a compressor 2, and a second heat exchanger 3. The second heat exchanger 3 includes a first heat exchange channel 3a and a second heat exchange channel 3b, with the first heat exchange channel 3a connected to both the first heat exchanger 1 and the compressor 2. The second circulation loop includes the second heat exchanger 3 and a heat exchange assembly 4, which is connected to the second heat exchange channel 3b. The heat exchange assembly 4 is adapted to exchange heat with at least a portion of the drive assembly.

[0028] Specifically, the first heat exchanger 1 is suitable for heat exchange with the external environment. The type of the first heat exchanger 1 can be selected according to actual needs, specifically it can be a condenser, or a combination of a condenser and an electric fan 1a, etc. When the thermal management device is applied to a vehicle, the first heat exchanger 1 can specifically be an external heat exchanger installed in the front compartment of the vehicle. The compressor 2 is a fluid machine that can compress refrigerant to increase the refrigerant pressure. After being compressed by the compressor 2, the refrigerant can flow into the first heat exchanger 1 to condense and release heat to the external environment. The second heat exchanger 3 includes a first heat exchange channel 3a and a second heat exchange channel 3b. The refrigerant in the first heat exchange channel 3a can exchange heat with the refrigerant in the second heat exchange channel 3b. The refrigerant can flow into the first heat exchange channel 3a to evaporate and absorb heat, thereby lowering the temperature of the refrigerant in the second heat exchange channel 3b, and then flow back into the compressor 2 for compression. In some embodiments of this application, the second heat exchanger 3 is preferably a plate heat exchanger, and the first heat exchange channel 3a and the second heat exchange channel 3b are different flow channels on the plate heat exchanger that can exchange heat.

[0029] In the above configuration, the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, and second heat exchanger 3 achieves the cooling of the heat exchange component 4. Therefore, the heat source thermal management system composed of the heat exchange component 4 and the drive assembly can be coupled with the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, and second heat exchanger 3. This eliminates the need for components such as radiators in traditional liquid cooling systems, thereby achieving the integration and weight reduction of the thermal management device.

[0030] Refrigerants can actively absorb a large amount of heat through phase change, while coolants can only absorb heat by increasing their temperature. Under the same mass, the heat absorbed by a refrigerant through phase change is far greater than the heat absorbed by refrigerants such as water and ethylene glycol by increasing their temperature by tens of degrees. Therefore, compared to coolants such as water and ethylene glycol, refrigerants can provide better heat dissipation. Using refrigerant as the cooling medium in heat exchange component 4 can improve its heat dissipation capacity and efficiency. When the heat exchange component 4 is used to cool electric drive components or electronic control components, it can meet the high cooling requirements of ultra-fast charging and kilovolt high-voltage platforms, effectively preventing performance degradation of electric drive and electronic control components due to high temperatures.

[0031] The thermal management system described in this application allows heat from a heat source to be dissipated to the outside via heat exchange component 4, second heat exchanger 3, and first heat exchanger 1. Compared to the technical solution of direct heat exchange between the first heat exchanger 1 and heat exchange component 4, the thermal management system described in this application uses the second heat exchanger 3 as an intermediate heat exchanger, which can avoid the problem of condensation caused by excessively low evaporation temperature. Benefiting from the reduction of condensation, the stability and reliability of the thermal management device are significantly improved.

[0032] When thermal management devices are applied to vehicles, the first heat exchanger 1 can be an external heat exchanger in the vehicle's front compartment, and the heat exchange assembly 4 can specifically include the cold plate of the electric drive assembly, the cold plate of the electronic control assembly, etc. Since heat is dissipated to the outside through the heat exchange assembly 4, the second heat exchanger 3, and the first heat exchanger 1, the vehicle does not need a separate radiator to dissipate heat from the cold plates. This facilitates vehicle integration and weight reduction, and also helps reduce vehicle wind resistance. It also avoids the mutual influence of heat damage between the radiator and the external heat exchanger, reducing the pressure on the external heat exchanger, reducing the energy consumption of the compressor 2, and improving the heat dissipation effect of the thermal management device. This further improves the heat dissipation effect and efficiency of the electric drive assembly or electronic control assembly, and also helps meet the large cooling requirements of ultra-fast charging and kilovolt high-voltage platforms, effectively preventing performance degradation of the electric drive assembly and electronic control assembly due to high temperatures.

[0033] refer to Figure 4 , Figure 5 In some embodiments of this application, optionally, the heat exchange component 4 includes a first cold plate 4a, which is adapted to exchange heat with the electronic control component of the drive assembly. And / or, the heat exchange component 4 includes a second cold plate 4b, which is adapted to exchange heat with the electric drive component of the drive assembly. Specifically, in some embodiments of this application, the heat exchange component 4 may be a combination of one, two, three, or even more cold plates. All of the aforementioned cold plates may serve as the first cold plate 4a for heat exchange with the electronic control component, or all of them may serve as the second cold plate 4b for heat exchange with the electric drive component. Alternatively, when the heat exchange component 4 includes two or more cold plates, some of the cold plates may serve as the first cold plate 4a for heat exchange with the electronic control component, and the remaining cold plates may serve as the second cold plate 4b for heat exchange with the electric drive component. When the heat dissipation target of the heat exchange component 4 is at least one of the electric drive component and the electronic control component, it can meet the large cooling requirements of ultra-fast charging and kilovolt high-voltage platforms, and can effectively prevent the performance degradation of the electric drive component and the electronic control component due to high temperature.

[0034] refer to Figure 4 In some embodiments of this application, optionally, the first port of the first cold plate 4a and the first port of the second cold plate 4b are connected to the second port of the second heat exchange channel 3b, and the second port of the first cold plate 4a and the second port of the second cold plate 4b are connected to the first port of the second heat exchange channel 3b.

[0035] Specifically, in some embodiments of this application, the heat exchange assembly 4 includes a first cold plate 4a, a second cold plate 4b, a fifth control valve 4c, and a sixth control valve 4d. The first port of the first cold plate 4a is connected to the second port of the fifth control valve 4c, the first port of the second cold plate 4b is connected to the second port of the sixth control valve 4d, the second ports of the first cold plate 4a and the second cold plate 4b are connected to the first port of the second heat exchange channel 3b, and the first ports of the fifth control valve 4c and the sixth control valve 4d are connected to the second port of the second heat exchange channel 3b. The first cold plate 4a can be an electrically controlled component cold plate, and the second cold plate 4b can be an electrically driven component cold plate. When the fifth control valve 4c is opened, refrigerant can flow into the first cold plate 4a. When the sixth control valve 4d is opened, refrigerant can flow into the second cold plate 4b. By controlling the fifth control valve 4c and the sixth control valve 4d, the thermal management device described in this application can select the object to be cooled according to actual needs. This allows the thermal management device to have more diverse operating modes, ensuring heat dissipation effect and efficiency while enabling the thermal management device to make flexible adjustments according to actual needs.

[0036] refer to Figure 5 Alternatively, in some embodiments of this application, the first port of the first cold plate 4a is connected to the second port of the second heat exchange channel 3b, the first port of the second cold plate 4b is connected to the second port of the first cold plate 4a, and the second port of the second cold plate 4a is connected to the first port of the second heat exchange channel 3b. Specifically, the heat exchange assembly 4 includes a first cold plate 4a, a second cold plate 4b, and a seventh control valve 4e. The first port of the seventh control valve 4e is connected to the second port of the second heat exchange channel 3b; the first port of the first cold plate 4a is connected to the second port of the seventh control valve 4e; the first port of the second cold plate 4b is connected to the second port of the first cold plate 4a; and the second port of the second cold plate 4b is connected to the first port of the second heat exchange channel 3b. The second cold plate 4b can be an electric drive assembly cold plate, and the first cold plate 4a can be an electronic control assembly cold plate. In this case, refrigerant can flow from the seventh control valve 4e into the first cold plate 4a, and then from the first cold plate 4a into the second cold plate 4b. This allows for precise cooling of different heat sources, helping to avoid overheating damage and performance degradation of the heat sources, and also helps to avoid wasting refrigerant cooling capacity. For example, the second cold plate 4b can be an electric drive assembly cold plate, and the first cold plate 4a can be an electronic control assembly cold plate. The electronic control components can withstand temperatures up to 80 degrees Celsius, while the electric drive components can withstand temperatures between 120 and 150 degrees Celsius. The low-temperature refrigerant first passes through the first cold plate 4a, absorbing heat, and then enters the second cold plate 4b to absorb heat, thereby achieving precise cooling of the electronic control components and electric drive components. This fully utilizes the cooling capacity of the refrigerant while preventing overheating damage and performance degradation of the electronic control components and electric drive components.

[0037] refer to Figure 1 In some embodiments of this application, optionally, the thermal management device includes a power pump 6, a first control valve 7, a second control valve 8, a third control valve 9, and a fourth control valve 10. The power pump 6 is a fluid machine that provides power for the flow of refrigerant. The first control valve 7, the second control valve 8, the third control valve 9, and the fourth control valve 10 are preferably solenoid valves to control the opening and closing of the flow path. The second port of the power pump 6 is connected to the first port of the heat exchange assembly 4. The first port of the power pump 6 is connected to the second ports of the first control valve 7 and the second control valve 8. The first port of the first control valve 7 is connected to the second port of the first heat exchanger 1. The first port of the second control valve 8 is connected to the second port of the second heat exchange channel 3b. The second port of the heat exchange assembly 4 is connected to the first ports of the third control valve 9 and the fourth control valve 10. The second port of the third control valve 9 is connected to the first port of the second heat exchange channel 3b. The second port of the fourth control valve 10 is connected to the first port of the first heat exchanger 1.

[0038] Based on the above settings, the thermal management device described in this application can have two working modes: Mode 1 and Mode 2. Mode 1 and Mode 2 can be selected and activated according to the actual heat dissipation requirements.

[0039] refer to Figure 1 In the first mode, compressor 2 and power pump 6 are both started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are opened. Part of the refrigerant circulates within the flow path formed by the first heat exchanger 1, the first heat exchange channel 3a of the second heat exchanger 3, and compressor 2, driven by compressor 2. Specifically, after being compressed by compressor 2, the refrigerant enters the first heat exchanger 1 as a high-temperature, high-pressure gas. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant within the first heat exchanger 1, then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. Within the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0040] Driven by the power pump 6, a portion of the refrigerant circulates within the flow path formed by the heat exchange assembly 4, the second heat exchange channel 3b of the second heat exchanger 3, and the power pump 6. Specifically, the refrigerant flows to the heat exchange assembly 4 under the action of the power pump 6. Within the heat exchange assembly 4, the refrigerant exchanges heat with a heat source and then flows to the second heat exchange channel 3b of the second heat exchanger 3. After exchanging heat with the refrigerant in the first heat exchange channel 3a, the refrigerant in the second heat exchange channel 3b flows back to the power pump 6.

[0041] refer to Figure 1In mode two, compressor 2 is off, power pump 6 is on, first control valve 7 and fourth control valve 10 are open, and second control valve 8 and third control valve 9 are closed. At this time, the refrigerant flows to heat exchange assembly 4 under the drive of power pump 6. After exchanging heat with the heat source in heat exchange assembly 4, it flows to first heat exchanger 1. After exchanging heat with the external environment in first heat exchanger 1, it flows back to power pump 6.

[0042] Based on the above configuration, the thermal management device described in this application can flexibly select between two operating modes, Mode 1 and Mode 2, according to actual heat dissipation needs. For example, when the thermal management device is applied to a vehicle, the first heat exchanger 1 can be an external heat exchanger, the second heat exchanger 3 can be a plate heat exchanger, and the heat exchange component 4 can be a cold plate for the electric drive component or the electronic control component. When the heat dissipation demand of the electric drive component or the electronic control component is high, the thermal management device can activate Mode 1, which allows the refrigerant to circulate rapidly within the compressor 2, the first heat exchanger 1, the first expansion valve 5, and the second heat exchanger 3, transferring a large amount of heat absorbed by the heat exchange component 4 to the outside through circulation. When the heat dissipation demand of the electric drive component or the electronic control component is low, the thermal management device can activate Mode 2, allowing the heat absorbed by the heat exchange component 4 to be pumped into the first heat exchanger 1 by the power pump 6 and dissipated to the outside. This significantly improves the flexibility of the thermal management device and reduces its dependence on the compressor 2 while ensuring heat dissipation effect and efficiency, thus helping to reduce the total energy consumption of the thermal management device during use.

[0043] refer to Figure 1 In some embodiments of this application, optionally, the thermal management device includes a first liquid storage tank 11. The second port of the first liquid storage tank 11 is connected to the first port of the power pump 6, and the first port of the first liquid storage tank 11 is connected to the second port of the first control valve 7 and the second port of the second control valve 8.

[0044] In the first mode, compressor 2 and power pump 6 are both started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are opened. The refrigerant flows to heat exchange assembly 4 under the action of power pump 6. The refrigerant exchanges heat with the heat source in heat exchange assembly 4, and then flows to the second heat exchange channel 3b of the second heat exchanger 3. The refrigerant in the second heat exchange channel 3b exchanges heat with the refrigerant in the first heat exchange channel 3a and then flows into the first liquid storage tank 11, and then flows back to power pump 6 from the first liquid storage tank 11.

[0045] In Mode 2, compressor 2 is off, power pump 6 is on, first control valve 7 and fourth control valve 10 are open, and second control valve 8 and third control valve 9 are closed. At this time, the refrigerant flows to heat exchange assembly 4 under the drive of power pump 6. After exchanging heat with the heat source in heat exchange assembly 4, it flows to first heat exchanger 1. After exchanging heat with the external environment in first heat exchanger 1, it flows into first liquid storage tank 11, and then flows back to power pump 6 from first liquid storage tank 11.

[0046] The first liquid storage tank 11 can provide the power pump 6 with safe, stable and cavitation-free operating conditions. During the refrigerant circulation process, the first liquid storage tank 11 can contain the refrigerant returning from the second heat exchange channel 3b. The refrigerant can release bubbles, settle impurities, and dissipate some heat in the first liquid storage tank 11 before flowing into the power pump 6, so as to prevent bubbles, impurities, and excess heat from damaging the power pump 6.

[0047] In some embodiments of this application, optionally, the first circulation loop includes a first expansion valve 5. The second port of the compressor 2 is connected to the first port of the first heat exchanger 1, the first port of the first expansion valve 5 is connected to the second port of the first heat exchanger 1, the first port of the first heat exchange channel 3a is connected to the second port of the first expansion valve 5, and the second port of the first heat exchange channel 3a is connected to the first port of the compressor 2.

[0048] The second port of compressor 2 is connected to the first port of the first heat exchanger 1. After being compressed by compressor 2, the refrigerant flows into the first heat exchanger 1, condenses, and releases heat to the external environment. The first port of the first expansion valve 5 is connected to the second port of the first heat exchanger 1. After condensation and heat release, the refrigerant enters the first expansion valve 5 for throttling and pressure reduction. The first port of the first heat exchange channel 3a is connected to the second port of the first expansion valve 5, and the second port within the first heat exchange channel 3a is connected to the first port of compressor 2. After being throttled and pressure-reduced by the first expansion valve 5, the refrigerant flows into the first heat exchange channel 3a to evaporate and absorb heat, thereby lowering the temperature of the refrigerant in the second heat exchange channel 3b, and then flows back into compressor 2 for compression. This allows for the cooling of the heat exchange component 4 based on the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, second heat exchanger 3, and first expansion valve 5. Consequently, the heat source thermal management system composed of the heat exchange component 4 and the drive assembly can be coupled with the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, second heat exchanger 3, and first expansion valve 5. This eliminates the need for components such as radiators in traditional liquid cooling systems, thereby achieving integration and lightweighting of the thermal management device.

[0049] refer to Figure 2In some embodiments of this application, optionally, the thermal management device includes a third heat exchanger 12 and a second expansion valve 13. The third heat exchanger 12 may specifically be an air conditioning evaporator. The first port of the third heat exchanger 12 is connected to the second port of the second expansion valve 13, the second port of the third heat exchanger 12 is connected to the first port of the compressor 2, and the first port of the second expansion valve 13 is connected to the second port of the first heat exchanger 1.

[0050] Based on the configuration of the third heat exchanger 12, the thermal management device can be further developed into Mode 3 based on the aforementioned Mode 1.

[0051] In Mode 3, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0052] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the second expansion valve 13, where it is throttled and its pressure reduced. Inside the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0053] Based on the above configuration, the thermal management device described in this application can meet the thermal management needs in more scenarios. For example, when the thermal management device is applied to a vehicle, the third heat exchanger 12 can be the vehicle's air conditioning evaporator, and the heat source exchanging heat with the third heat exchanger 12 is the vehicle's interior environment. This allows the air conditioning refrigeration system to be coupled into the thermal management device described in this application, further improving the vehicle's integration and lightweighting.

[0054] refer to Figure 2 Optionally, in some embodiments of this application, the thermal management device includes a fourth heat exchanger 14 and a third expansion valve 15, with the first port of the fourth heat exchanger 14 connected to the second port of the third expansion valve 15, the second port of the fourth heat exchanger 14 connected to the first port of the compressor 2, and the first port of the third expansion valve 15 connected to the second port of the first heat exchanger 1.

[0055] Based on the configuration of the fourth heat exchanger 14, the thermal management device can be further developed into Mode 4 and Mode 5 based on the aforementioned Mode 1.

[0056] In mode four, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0057] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the third expansion valve 15 for throttling and pressure reduction. Inside the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0058] In mode five, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0059] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the second expansion valve 13, where it is throttled and its pressure reduced. Inside the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0060] The medium-temperature, high-pressure liquid refrigerant flows into the third expansion valve 15, where it is throttled and its pressure reduced. Inside the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fourth heat exchanger 14, and then flows back into the compressor 2.

[0061] Based on the above configuration, the thermal management device described in this application can meet the thermal management needs in more scenarios. For example, when the thermal management device is applied to a vehicle, the fourth heat exchanger 14 can be the evaporator of a vehicle refrigerator, etc., and the heat source exchanging heat with the fourth heat exchanger 14 is the internal environment of the refrigerator. When the thermal management device is in mode four, the second heat exchanger 3 can exchange heat with the heat exchange component 4, and the fourth heat exchanger 14 can absorb heat from inside the refrigerator to achieve refrigerator cooling. When the thermal management device is in mode five, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve vehicle air conditioning cooling, and the fourth heat exchanger 14 can achieve refrigerator cooling. This allows the refrigerator cooling system to be coupled into the thermal management device described in this application, further improving the integration and lightweighting of the vehicle.

[0062] refer to Figure 2 In some embodiments of this application, optionally, at least two fourth heat exchangers 14 and three third expansion valves 15 may be provided, specifically two, three, four, or even more. The first ports of at least two fourth heat exchangers 14 are respectively connected to the second ports of different third expansion valves 15, the second ports of at least two fourth heat exchangers 14 are all connected to the first port of compressor 2, and the first ports of at least two third expansion valves 15 are all connected to the second port of first heat exchanger 1. Based on the increased number of fourth heat exchangers 14 and third expansion valves 15, the thermal management device described in this application can meet the thermal management needs in more scenarios. For example, when the thermal management device is applied to a vehicle, two fourth heat exchangers 14 may be provided. One fourth heat exchanger 14 is a refrigerator evaporator for cooling the interior environment of the refrigerator. The other fourth heat exchanger 14 may be another evaporator for cooling other parts of the vehicle. This allows at least two refrigeration systems, such as a refrigerator refrigeration system, to be coupled within the thermal management device described in this application, enriching the applicable scenarios of the thermal management device while further improving the integration and lightweighting of the vehicle.

[0063] refer to Figure 2In some embodiments of this application, optionally, the thermal management device includes a fifth heat exchanger 16 and a fourth expansion valve 17. The first port of the fifth heat exchanger 16 is connected to both the first and second ports of the compressor 2. Depending on the actual operating conditions, the first port of the fifth heat exchanger 16 can selectively connect to either the first or second port of the compressor 2. When the first port of the fifth heat exchanger 16 is connected to the first port of the compressor 2, refrigerant can flow from the fourth expansion valve 17 into the fifth heat exchanger 16, and then return to the compressor 2 via the first port of the fifth heat exchanger 16 and the first port of the compressor 2. When the first port of the fifth heat exchanger 16 is connected to the second port of the compressor 2, refrigerant can flow from the second port of the compressor 2 into the fifth heat exchanger 16, and then return to the compressor 2 via the second port of the fifth heat exchanger 16, the fourth expansion valve 17, and the first port of the compressor 2. The second port of the fifth heat exchanger 16 is connected to the first port of the fourth expansion valve 17. The second port of the fourth expansion valve 17 is connected to the first port of the first expansion valve 5, the first port of the second expansion valve 13, the first port of the third expansion valve 15, and the second port of the first heat exchanger 1.

[0064] Based on the configuration of the fifth heat exchanger 16, the thermal management device can be further developed into Mode 6, Mode 7, Mode 8, Mode 9, Mode 10, Mode 11, Mode 12, and Mode 13.

[0065] In mode six, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0066] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the fourth expansion valve 17 for throttling and pressure reduction. Inside the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0067] In mode seven, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0068] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the second expansion valve 13, where it is throttled and its pressure reduced. Inside the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0069] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fourth expansion valve 17 for throttling and pressure reduction. Inside the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0070] In mode eight, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0071] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the third expansion valve 15 for throttling and pressure reduction. Inside the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0072] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fourth expansion valve 17 for throttling and pressure reduction. Inside the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0073] In Mode 9, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the first heat exchanger 1 as a high-temperature, high-pressure gas. In the first heat exchanger 1, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into four streams. The first stream of medium-temperature, high-pressure liquid refrigerant flows into the first expansion valve 5 for throttling and pressure reduction. In the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0074] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the second expansion valve 13, where it is throttled and its pressure reduced. Inside the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0075] The medium-temperature, high-pressure liquid refrigerant flows into the third expansion valve 15, where it is throttled and its pressure reduced. Inside the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fourth heat exchanger 14, and then flows back into the compressor 2.

[0076] The fourth channel of medium-temperature, high-pressure liquid refrigerant flows into the fourth expansion valve 17, where it is throttled and its pressure reduced. Inside the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fifth heat exchanger 16, and then flows back into the compressor 2.

[0077] In Mode 10, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the fifth heat exchanger 16 as a high-temperature, high-pressure gas. In the fifth heat exchanger 16, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can flow into the fourth expansion valve 17 and the first expansion valve 5 for throttling and pressure reduction. In the fourth expansion valve 17 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0078] In Mode 11, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the fifth heat exchanger 16 as a high-temperature, high-pressure gas. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant within the fifth heat exchanger 16. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path flows into the fourth expansion valve 17 and the first expansion valve 5 for throttling and pressure reduction. Within the fourth expansion valve 17 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0079] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fourth expansion valve 17 and the second expansion valve 13, where it is throttled and its pressure reduced. Inside the fourth expansion valve 17 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0080] In mode 12, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the fifth heat exchanger 16 as a high-temperature, high-pressure gas. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant within the fifth heat exchanger 16. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path flows into the fourth expansion valve 17 and the first expansion valve 5 for throttling and pressure reduction. Within the fourth expansion valve 17 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. Within the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0081] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the fourth expansion valve 17 and the third expansion valve 15 for throttling and pressure reduction. Inside the fourth and third expansion valves 17 and 15, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0082] In Mode 13, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the fifth heat exchanger 16 as a high-temperature, high-pressure gas. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant within the fifth heat exchanger 16. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path flows into the fourth expansion valve 17 and the first expansion valve 5 for throttling and pressure reduction. Within the fourth expansion valve 17 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0083] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fourth expansion valve 17 and the second expansion valve 13, where it is throttled and its pressure reduced. Inside the fourth expansion valve 17 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the third heat exchanger 12, and then flows back into the compressor 2.

[0084] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fourth expansion valve 17 and the third expansion valve 15 for throttling and pressure reduction. Inside the fourth expansion valve 17 and the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0085] Based on the above settings, the thermal management device described in this application can meet the thermal management needs in more scenarios. For example, when the thermal management device is applied to a vehicle, the fifth heat exchanger 16 can specifically be a battery pack heat exchanger, and the object exchanging heat with the fifth heat exchanger 16 is the battery pack. When the thermal management device is in mode six, the second heat exchanger 3 can exchange heat with the heat exchange component 4, and the fifth heat exchanger 16 can absorb the heat from the battery pack to achieve heat dissipation and cooling of the battery pack. When the thermal management device is in mode seven, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, and the fifth heat exchanger 16 can absorb the heat from the battery pack to achieve heat dissipation and cooling of the battery pack. When the thermal management device is in mode eight, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fourth heat exchanger 14 can achieve refrigerator cooling, and the fifth heat exchanger 16 can absorb the heat from the battery pack to achieve heat dissipation and cooling of the battery pack. When the thermal management device is in mode nine, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fourth heat exchanger 14 can achieve refrigerator cooling, and the fifth heat exchanger 16 can absorb heat from the battery pack to achieve heat dissipation and cooling of the battery pack. When the thermal management device is in mode ten, the second heat exchanger 3 can exchange heat with the heat exchange component 4, and the fifth heat exchanger 16 can release heat and heat the battery pack. When the thermal management device is in mode eleven, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, and the fifth heat exchanger 16 can release heat and heat the battery pack. When the thermal management device is in mode twelve, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fourth heat exchanger 14 can achieve refrigerator cooling, and the fifth heat exchanger 16 can release heat and heat the battery pack. When the thermal management device is in mode thirteen, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fourth heat exchanger 14 can achieve refrigerator cooling, and the fifth heat exchanger 16 can release heat and heat the battery pack. This couples the battery pack thermal management system into the thermal management device described in this application, further improving the vehicle's integration and weight reduction.

[0086] refer to Figure 2In some embodiments of this application, optionally, the thermal management device includes a sixth heat exchanger 18 and a fifth expansion valve 19. The first port of the sixth heat exchanger 18 is connected to the first port of the compressor 2, and the second port of the sixth heat exchanger 18 is connected to the first port of the fifth expansion valve 19. The second port of the fifth expansion valve 19 is also connected to the first ports of the first expansion valve 5, the second expansion valve 13, the third expansion valve 15, and the fourth expansion valve 17.

[0087] Based on the setup of the sixth heat exchanger 18, the thermal management device can be further developed into modes fourteen, fifteen, sixteen, seventeen, eighteen, nineteen, twentieth, twenty-one, twenty-two, twenty-three, twenty-four, and twenty-five.

[0088] In mode fourteen, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can flow into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0089] In Mode 15, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0090] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the second expansion valve 13 for throttling and pressure reduction. Within the fifth expansion valve 19 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0091] In mode sixteen, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0092] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the third expansion valve 15 for throttling and pressure reduction. Within the fifth and third expansion valves 19 and 15, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0093] In mode seventeen, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into two paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0094] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the fourth expansion valve 17, where it is throttled and its pressure reduced. Inside the fifth and fourth expansion valves 19 and 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0095] In mode 18, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant within the sixth heat exchanger 18. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. Within the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. Within the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0096] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the second expansion valve 13 for throttling and pressure reduction. Within the fifth expansion valve 19 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0097] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fifth expansion valve 19 and the third expansion valve 15 for throttling and pressure reduction. Inside the fifth expansion valve 19 and the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fourth heat exchanger 14, and then flows back into the compressor 2.

[0098] In mode nineteen, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0099] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the second expansion valve 13 for throttling and pressure reduction. Within the fifth expansion valve 19 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0100] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fifth expansion valve 19 and the fourth expansion valve 17 for throttling and pressure reduction. Inside the fifth expansion valve 19 and the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0101] In mode 20, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into three paths. The first path flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0102] The second stream of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the third expansion valve 15 for throttling and pressure reduction. Within the fifth and third expansion valves 19 and 15, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with a heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0103] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fifth expansion valve 19 and the fourth expansion valve 17 for throttling and pressure reduction. Inside the fifth expansion valve 19 and the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fifth heat exchanger 16, and then flows back into the compressor 2.

[0104] In mode 21, compressor 2 and power pump 6 are both started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the sixth heat exchanger 18 as a high-temperature, high-pressure gas. In the sixth heat exchanger 18, the high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant. This medium-temperature, high-pressure liquid refrigerant can be divided into four paths. The first path of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the first expansion valve 5 for throttling and pressure reduction. In the fifth expansion valve 19 and the first expansion valve 5, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the first heat exchange channel 3a of the second heat exchanger 3 to exchange heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, and then flows back into compressor 2.

[0105] The second-stage, medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the second expansion valve 13 for throttling and pressure reduction. Within the fifth expansion valve 19 and the second expansion valve 13, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the third heat exchanger 12 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0106] The medium-temperature, high-pressure liquid refrigerant from the third channel flows into the fifth expansion valve 19 and the third expansion valve 15 for throttling and pressure reduction. Inside the fifth expansion valve 19 and the third expansion valve 15, the medium-temperature, high-pressure liquid refrigerant undergoes a phase change to a low-temperature, low-pressure gas-liquid mixture, which then enters the fourth heat exchanger 14 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fourth heat exchanger 14, and then flows back into the compressor 2.

[0107] The fourth type of medium-temperature, high-pressure liquid refrigerant flows into the fifth expansion valve 19 and the fourth expansion valve 17 for throttling and pressure reduction. Inside the fifth expansion valve 19 and the fourth expansion valve 17, the medium-temperature, high-pressure liquid refrigerant transforms into a low-temperature, low-pressure gas-liquid mixture, and then enters the fifth heat exchanger 16 to exchange heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas in the fifth heat exchanger 16, and then flows back into the compressor 2.

[0108] In mode 22, both compressor 2 and power pump 6 are started, first control valve 7 and fourth control valve 10 are closed, and second control valve 8 and third control valve 9 are open. After being compressed by compressor 2, the refrigerant, in a high-temperature, high-pressure gaseous state, enters the fifth heat exchanger 16 and the sixth heat exchanger 18 respectively. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant in the fifth and sixth heat exchangers 16 and 18. The medium-temperature, high-pressure liquid refrigerant is then throttled and depressurized in the fourth expansion valve 17, fifth expansion valve 19, and first expansion valve 5, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the first heat exchange channel 3a of the second heat exchanger 3 and exchanges heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0109] In mode 23, both compressor 2 and power pump 6 are started, control valves 7 and 10 are closed, and control valves 8 and 9 are open. The refrigerant, compressed by compressor 2, enters the fifth heat exchanger 16 and the sixth heat exchanger 18 in a high-temperature, high-pressure gaseous state. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant in these heat exchangers. This medium-temperature, high-pressure liquid refrigerant can then pass through expansion valves 17 and 19 respectively before converging and splitting into two paths. The first path of medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in expansion valves 5, 17, and 19, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the first heat exchange channel 3a of the second heat exchanger 3 and exchanges heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0110] The second-stage, medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in the second expansion valve 13, the fourth expansion valve 17, and the fifth expansion valve 19, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the third heat exchanger 12 and exchanges heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0111] In mode 24, both compressor 2 and power pump 6 are started, control valves 7 and 10 are closed, and control valves 8 and 9 are open. The refrigerant, compressed by compressor 2, enters the fifth heat exchanger 16 and the sixth heat exchanger 18 in a high-temperature, high-pressure gaseous state. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant in these heat exchangers. This medium-temperature, high-pressure liquid refrigerant can then pass through expansion valves 17 and 19 respectively before converging and splitting into two paths. The first path of medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in expansion valves 5, 17, and 19, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the first heat exchange channel 3a of the second heat exchanger 3 and exchanges heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0112] The second-stage, medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in the third expansion valve 15, fourth expansion valve 17, and fifth expansion valve 19, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the fourth heat exchanger 14 and exchanges heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0113] In mode 25, both compressor 2 and power pump 6 are started, control valve 7 and control valve 10 are closed, and control valve 8 and control valve 9 are open. The refrigerant, after being compressed by compressor 2, enters the fifth heat exchanger 16 and the sixth heat exchanger 18 in a high-temperature, high-pressure gaseous state. The high-temperature, high-pressure gaseous refrigerant releases heat and transforms into a medium-temperature, high-pressure liquid refrigerant in the fifth and sixth heat exchangers 16 and 18. The medium-temperature, high-pressure liquid refrigerant can then pass through the fourth expansion valve 17 and the fifth expansion valve 19 respectively, and then be divided into three paths. The first path of medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in the first expansion valve 5, the fourth expansion valve 17, and the fifth expansion valve 19, transforming into a low-temperature, low-pressure gas-liquid mixture, which then enters the first heat exchange channel 3a of the second heat exchanger 3 and exchanges heat with the refrigerant in the second heat exchange channel 3b. In the first heat exchange channel 3a, the low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas, which then flows back into compressor 2.

[0114] The second-stage, medium-temperature, high-pressure liquid refrigerant undergoes throttling and pressure reduction in the second expansion valve 13, the fourth expansion valve 17, and the fifth expansion valve 19, transforming into a low-temperature, low-pressure gas-liquid mixture. This mixture then enters the third heat exchanger 12 and exchanges heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the third heat exchanger 12, and then flows back into the compressor 2.

[0115] The medium-temperature, high-pressure liquid refrigerant in the third path undergoes throttling and pressure reduction in the third expansion valve 15, fourth expansion valve 17, and fifth expansion valve 19, transforming into a low-temperature, low-pressure gas-liquid mixture. It then enters the fourth heat exchanger 14 and exchanges heat with the heat source. The low-temperature, low-pressure gas-liquid mixture evaporates into a low-temperature, low-pressure gas within the fourth heat exchanger 14, and then flows back into the compressor 2.

[0116] Based on the above configuration, the thermal management device described in this application can meet the thermal management needs in more scenarios. For example, when the thermal management device is applied to a vehicle, the sixth heat exchanger 18 can specifically be an air conditioning condenser, in which case the object of heat exchange with the sixth heat exchanger 18 is the external environment. When there is a need for air conditioning heating inside the vehicle, the refrigerant flows from the compressor 2 into the sixth heat exchanger 18. When there is no need for air conditioning heating inside the vehicle, the refrigerant flows from the compressor 2 into the first heat exchanger 1 or the fifth heat exchanger 16.

[0117] Specifically, when the thermal management device is in mode fourteen, the second heat exchanger 3 can exchange heat with the heat exchange component 4, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode fifteen, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode sixteen, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fourth heat exchanger 14 can achieve refrigerator cooling, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode seventeen, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fifth heat exchanger 16 can absorb heat from the battery pack to achieve battery pack heat dissipation, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode 18, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fourth heat exchanger 14 can achieve refrigerator cooling, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode 19, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fifth heat exchanger 16 can absorb heat from the battery pack to achieve battery pack heat dissipation, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode 20, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fourth heat exchanger 14 can achieve refrigerator cooling, the fifth heat exchanger 16 can absorb heat from the battery pack to achieve battery pack heat dissipation, and the sixth heat exchanger 18 can release heat and heat the vehicle interior environment. When the thermal management device is in mode 21, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fourth heat exchanger 14 can achieve refrigerator cooling, the fifth heat exchanger 16 can absorb the heat of the battery pack to achieve heat dissipation of the battery pack, and the sixth heat exchanger 18 can release heat and heat the interior environment of the vehicle.

[0118] When the thermal management device is in mode 22, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fifth heat exchanger 16 can release heat to heat the battery pack, and the sixth heat exchanger 18 can release heat to heat the vehicle interior environment. When the thermal management device is in mode 23, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can provide air conditioning cooling, the fifth heat exchanger 16 can release heat to heat the battery pack, and the sixth heat exchanger 18 can release heat to heat the vehicle interior environment. When the thermal management device is in mode 24, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the fourth heat exchanger 14 can provide refrigerator cooling, the fifth heat exchanger 16 can release heat to heat the battery pack, and the sixth heat exchanger 18 can release heat to heat the vehicle interior environment. When the thermal management device is in mode twenty-five, the second heat exchanger 3 can exchange heat with the heat exchange component 4, the third heat exchanger 12 can achieve air conditioning cooling, the fourth heat exchanger 14 can achieve refrigerator cooling, the fifth heat exchanger 16 can release heat to heat the battery pack, and the sixth heat exchanger 18 can release heat to heat the vehicle interior environment. This allows the air conditioning heating system to be coupled into the thermal management device described in this application, further improving the vehicle's integration and weight reduction.

[0119] In some embodiments of this application, modes one through twenty-five can be set according to actual needs, and the thermal management device is not limited to modes one through twenty-five. For example, the fourth heat exchanger 14 can be selected according to actual needs. Without the fourth heat exchanger 14, the thermal management device described in the embodiments of this application may only have modes one, two, three, six, seven, ten, eleven, fourteen, fifteen, seventeen, nineteen, twenty-two, and twenty-three. For another example, the thermal management device can also couple more evaporators. The setting of the coupled evaporators can refer to the fourth heat exchanger 14. New modes based on newly added evaporators can refer to modes four, five, eight, nine, twelve, thirteen, sixteen, eighteen, twenty, twenty-one, twenty-four, and twenty-five based on the fourth heat exchanger 14, etc., which will not be elaborated here. For example, the thermal management device can also couple more condensers. The arrangement of the coupled condensers can be referenced to the sixth heat exchanger 18. New modes based on the newly added condensers can be referenced to modes fourteen to twenty-five based on the sixth heat exchanger 18, etc., which will not be elaborated here.

[0120] In some embodiments of this application, the sixth heat exchanger 18 may optionally include an auxiliary heater, which may specifically be a PTC (Positive Temperature Coefficient) heater. The auxiliary heater can also be activated for heating when the thermal management device is in any of the above modes.

[0121] refer to Figure 2 In some embodiments of this application, optionally, the thermal management device includes a gas-liquid separator 20. The second port of the gas-liquid separator 20 is connected to the first port of the compressor 2, and the first port of the gas-liquid separator 20 is also connected to the second ports of the second heat exchange channel 3b, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16. The gas-liquid separator 20 can intercept and separate the liquid refrigerant flowing out from the second ports of the second heat exchange channel 3b, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16, ensuring that pure gaseous refrigerant enters the compressor 2. This prevents the compressor 2 from being impacted by the liquid refrigerant, ensuring the safe and stable operation of the compressor 2. Simultaneously, this also prevents the liquid refrigerant from crowding out the suction volume of the compressor 2, which is beneficial for ensuring the efficiency of the compressor 2 during operation.

[0122] In some embodiments of this application, a one-way valve 25 can be connected to the second port of the gas-liquid separator 20 to prevent the refrigerant flowing out of the fifth heat exchanger 16 and the sixth heat exchanger 18 from flowing back into the first heat exchanger 1, thereby preventing the refrigerant from accumulating inside the first heat exchanger 1 when the first heat exchanger 1 is not in use.

[0123] refer to Figure 3In some embodiments of this application, optionally, the compressor 2 has two first ports. One first port of the compressor 2 is connected to the first port of the fifth heat exchanger 16 and the second port of the second heat exchange channel 3b, and the other first port of the compressor 2 is connected to the second port of the third heat exchanger 12 and the second port of the fourth heat exchanger 14. When the thermal management device described in this application is applied to a vehicle, the second heat exchanger 3 can be a plate heat exchanger for dissipating heat from the heat exchange component 4, the third heat exchanger 12 can be an air conditioning evaporator, the fourth heat exchanger 14 can be a refrigerator evaporator, and the fifth heat exchanger 16 can be a battery pack heat exchanger. In this case, the fifth heat exchanger 16 and the second heat exchanger 3 can be considered as medium-temperature evaporators, and the third heat exchanger 12 and the fourth heat exchanger 14 can be considered as low-temperature evaporators. When refrigerant flows out from the second heat exchanger 3, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16 simultaneously, the refrigerant flowing out from the third heat exchanger 12 and the fourth heat exchanger 14 can return to the compressor 2 from one of its first ports, while the refrigerant flowing out from the second heat exchanger 3 and the fifth heat exchanger 16 returns to the compressor 2 from the other first port. When a gas-liquid separator 20 is installed, if only the second heat exchanger 3 and the fifth heat exchanger 16, or only the third heat exchanger 12 and the fourth heat exchanger 14, the refrigerant will uniformly pass through the gas-liquid separator 20 and return to the compressor 2. This allows for pressure isolation when the evaporation pressures of the second heat exchanger 3, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16 are different. This helps ensure that the second heat exchanger 3, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16 maintain their respective optimal evaporation conditions, thereby enabling the thermal management device to have more precise temperature control capabilities and more stable operating conditions.

[0124] refer to Figure 3 In some embodiments of this application, optionally, when the compressor 2 has two first ports, for ease of control, an eighth control valve 26 is provided between the second ports of the second heat exchanger 3 and the second ports of the fifth heat exchanger 16 and the first port of the compressor 2. When refrigerant flows out from the second heat exchanger 3, the third heat exchanger 12, the fourth heat exchanger 14, and the fifth heat exchanger 16 simultaneously, the refrigerant flowing out from the third heat exchanger 12 and the fourth heat exchanger 14 can return to the compressor 2 via the gas-liquid separator 20. At the same time, the eighth control valve 26 opens, and the refrigerant flowing out from the second heat exchanger 3 and the fifth heat exchanger 16 returns to the compressor 2 from the other first port of the compressor 2. When only the second heat exchanger 3 and the fifth heat exchanger 16, or only the third heat exchanger 12 and the fourth heat exchanger 14, flows out refrigerant, the eighth control valve 26 closes, and the refrigerant returns to the compressor 2 after passing through the gas-liquid separator 20.

[0125] refer to Figure 2In some embodiments of this application, optionally, the thermal management device includes a second liquid storage tank 21. The first port of the second liquid storage tank 21 is connected to the second port of the first heat exchanger 1, and the second port of the second liquid storage tank 21 is connected to the first port of the first expansion valve 5, the first port of the second expansion valve 13, the first port of the third expansion valve 15, and the second port of the fourth expansion valve 17. Refrigerant flowing out from the second port of the first heat exchanger 1 can first enter the second liquid storage tank 21, and then from the second liquid storage tank 21 enter the first expansion valve 5, the second expansion valve 13, the third expansion valve 15, and the fourth expansion valve 17. When the load of the thermal management device is low, the second liquid storage tank 21 stores excess liquid refrigerant; when the load of the thermal management device is high, the second liquid storage tank 21 can release the stored liquid refrigerant to cope with changes in the load and operating conditions of the thermal management device. Simultaneously, the arrangement of the second liquid storage tank 21 also helps to increase the subcooling of the refrigerant flowing out from the first heat exchanger 1.

[0126] refer to Figure 2 In some embodiments of this application, the thermal management device optionally includes a sixth expansion valve 22. The sixth expansion valve 22 may be disposed between the second port of the second heat exchange channel 3b and the first port of the compressor 2. Alternatively, the sixth expansion valve 22 may be disposed between the second port of the third heat exchanger 12 and the first port of the compressor 2, or between the first port of the fifth heat exchanger 16 and the first port of the compressor 2. Two or more sixth expansion valves 22 may also be provided, in which case the sixth expansion valve 22 may be disposed at at least two of the following locations: between the second port of the second heat exchange channel 3b and the first port of the compressor 2, between the second port of the third heat exchanger 12 and the first port of the compressor 2, and between the first port of the fifth heat exchanger 16 and the first port of the compressor 2. When the evaporation pressures of the second heat exchanger 3, the fourth heat exchanger 14, and the fifth heat exchanger 16 are different, the sixth expansion valve 22 may be disposed between the heat exchanger with the higher evaporation pressure and the first port of the compressor 2. The sixth expansion valve 22 can maintain the internal pressure of the heat exchanger with high evaporation pressure by adjusting its own opening degree, so as to prevent the internal pressure of the heat exchanger with high evaporation pressure from being pulled down, thereby preventing the heat exchanger's temperature control capability from being damaged.

[0127] Specifically, in some embodiments of this application, when the thermal management device is applied to a vehicle, the second heat exchanger 3 can be a plate heat exchanger for dissipating heat from the heat exchange component 4, the third heat exchanger 12 can be an air conditioning evaporator, the fourth heat exchanger 14 can be a refrigerator evaporator, and the fifth heat exchanger 16 can be a battery pack heat exchanger. The second heat exchanger 3 and the fifth heat exchanger 16 are medium-temperature evaporators, and a sixth expansion valve 22 is provided between them and the first port of the compressor 2. The third heat exchanger 12 and the fourth heat exchanger 14 are low-temperature heat exchangers. A sixth expansion valve 22 is provided between the third heat exchanger 12 and the first port of the compressor 2, while a sixth expansion valve 22 may not be provided between the fourth heat exchanger 14 and the first port of the compressor 2. When the third heat exchanger 12 is in operation and the fourth heat exchanger 14 is not in operation, the sixth expansion valve 22 connected to the second heat exchanger 3 and the sixth expansion valve 22 connected to the fifth heat exchanger 16 can maintain the internal pressure of the second heat exchanger 3 and the fifth heat exchanger 16 by adjusting their own opening. At this time, the sixth expansion valve 22 connected to the third heat exchanger 12 reaches its maximum opening to serve as a flow path. Since the evaporation pressure inside the third heat exchanger 12 is greater than the evaporation pressure inside the fourth heat exchanger 14, when both the third heat exchanger 12 and the fourth heat exchanger 14 are in operation, the sixth expansion valve 22 connected to the third heat exchanger 12 can maintain the internal pressure of the third heat exchanger 12 by adjusting its own opening, the sixth expansion valve 22 connected to the second heat exchanger 3 can maintain the internal pressure of the second heat exchanger 3 by adjusting its own opening, and the sixth expansion valve 22 connected to the fifth heat exchanger 16 can maintain the internal pressure of the fifth heat exchanger 16 by adjusting its own opening.

[0128] refer to Figure 2 In some embodiments of this application, the thermal management device optionally includes a seventh expansion valve 23. The seventh expansion valve 23 is disposed between the first port of the first heat exchanger 1 and the second port of the compressor 2. When refrigerant flows out from the compressor 2, the opening of the seventh expansion valve 23 can be maximized so that refrigerant flows into the first heat exchanger 1. Alternatively, the seventh expansion valve 23 can be closed so that the refrigerant flowing out of the compressor 2 can flow into the fifth heat exchanger 16 or the sixth heat exchanger 18. Since the seventh expansion valve 23 is disposed between the compressor 2 and the first heat exchanger 1, when the seventh expansion valve 23 is closed, refrigerant will not enter the first heat exchanger 1, which helps to prevent refrigerant accumulation in the first heat exchanger 1.

[0129] refer to Figure 2In some embodiments of this application, optionally, the thermal management device includes an eighth expansion valve 24, which is disposed between the first port of the fifth heat exchanger 16 and the second port of the compressor 2. When refrigerant flows out of the compressor 2, the eighth expansion valve 24 can be opened and the seventh expansion valve 23 can be closed to allow refrigerant to flow into the fifth heat exchanger 16 and the sixth heat exchanger 18. Alternatively, the seventh expansion valve 23 and the eighth expansion valve 24 can be closed to allow the refrigerant flowing out of the compressor 2 to flow into the sixth heat exchanger 18. Alternatively, the eighth expansion valve 24 can be opened and the seventh expansion valve 23 and the fifth expansion valve 19 can be closed to allow the refrigerant flowing out of the compressor 2 to flow only into the fifth heat exchanger 16. When the fifth heat exchanger 16 is a battery pack heat exchanger, since the eighth expansion valve 24 is disposed between the compressor 2 and the fifth heat exchanger 16, when the eighth expansion valve 24 is closed, the refrigerant will not enter the fifth heat exchanger 16, which helps to prevent the high-temperature and high-pressure refrigerant from affecting the temperature of the battery pack. When the refrigerant that needs to flow out of compressor 2 flows into both the fifth heat exchanger 16 and the sixth heat exchanger 18, the pressure and flow rate of the refrigerant flowing into the fifth heat exchanger 16 and the refrigerant flowing into the sixth heat exchanger 18 can be distributed by adjusting the opening of the eighth expansion valve 24.

[0130] Secondly, embodiments of this application provide a vehicle, which includes any of the thermal management devices described in the first aspect. The vehicle described in this application can be a common family vehicle such as a sedan or SUV, or a commercial vehicle such as a bus or engineering vehicle. Using the thermal management device described in the first aspect, the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, and second heat exchanger 3 can be used to cool the heat exchange component 4. Therefore, the heat source thermal management system composed of the heat exchange component 4 and the heat source can be coupled with the refrigerant cooling system formed by the first heat exchanger 1, compressor 2, and second heat exchanger 3 to achieve integration and lightweighting of the thermal management device, thereby achieving integration and lightweighting of the vehicle.

[0131] Compared to coolants such as water and ethylene glycol, refrigerants offer superior heat dissipation. Using refrigerant as the cooling medium within heat exchange component 4 enhances its heat dissipation capacity and efficiency. When heat exchange component 4 is used to cool electric drive or electronic control components, it can meet the high cooling demands of ultra-fast charging and kilovolt high-voltage platforms, effectively preventing performance degradation caused by high temperatures in these components and thus contributing to improved vehicle performance.

[0132] The thermal management system described in this application allows heat from a heat source to be dissipated to the outside via heat exchange component 4, second heat exchanger 3, and first heat exchanger 1. Compared to the technical solution where the first heat exchanger 1 directly exchanges heat with the heat exchange component 4, the thermal management system described in this application uses the second heat exchanger 3 as an intermediate heat exchanger, which avoids the problem of condensation caused by excessively low evaporation temperatures. Benefiting from the reduction of condensation, the stability and reliability of the thermal management device are significantly improved, which helps to ensure the stability and reliability of vehicle heat dissipation.

[0133] When thermal management devices are applied to vehicles, the first heat exchanger 1 can be an external heat exchanger in the vehicle's front compartment, and the heat exchange assembly 4 can specifically include the cold plate of the electric drive assembly, the cold plate of the electronic control assembly, etc. Since heat is dissipated to the outside through the heat exchange assembly 4, the second heat exchanger 3, and the first heat exchanger 1, the vehicle does not need a separate radiator to dissipate heat from the cold plates. This facilitates vehicle integration and weight reduction, and also helps reduce vehicle wind resistance. It also avoids the mutual influence of heat damage between the radiator and the external heat exchanger, reducing the pressure on the external heat exchanger, reducing the energy consumption of the compressor 2, and improving the heat dissipation effect of the thermal management device. This further improves the heat dissipation effect and efficiency of the electric drive assembly or electronic control assembly, and also helps meet the large cooling requirements of ultra-fast charging and kilovolt high-voltage platforms, effectively preventing performance degradation of the electric drive assembly and electronic control assembly due to high temperatures.

[0134] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0135] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0136] The various embodiments in this specification are described in a related manner. Similar or identical parts between embodiments can be referred to mutually. Each embodiment focuses on its differences from other embodiments. For the vehicle embodiments, since they are basically similar to the thermal management device embodiments, the description is relatively simple; relevant parts can be referred to the descriptions in the method embodiment sections.

[0137] The above description is merely a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention are included within the scope of protection of the present invention.

Claims

1. A thermal management device, characterized in that, The thermal management device is adapted to supply refrigerant flow, including: The first circulation loop includes a first heat exchanger (1), a compressor (2), and a second heat exchanger (3). The second heat exchanger (3) includes a first heat exchange channel (3a) and a second heat exchange channel (3b). The first heat exchange channel (3a) is connected to the first heat exchanger (1) and the compressor (2) respectively. The second circulation loop includes the second heat exchanger (3) and the heat exchange assembly (4), the heat exchange assembly (4) being connected to the second heat exchange channel (3b), and the heat exchange assembly (4) being adapted to exchange heat with at least a portion of the drive assembly.

2. The thermal management device according to claim 1, characterized in that, The heat exchange assembly (4) includes a first cold plate (4a) adapted to exchange heat with the electronic control components of the drive assembly; and / or The heat exchange assembly (4) includes a second cold plate (4b) adapted to exchange heat with the electric drive assembly of the drive assembly.

3. The thermal management device according to claim 2, characterized in that, The first port of the first cold plate (4a) and the first port of the second cold plate (4b) are respectively connected to the second port of the second heat exchange channel (3b), and the second port of the first cold plate (4a) and the second port of the second cold plate (4b) are respectively connected to the first port of the second heat exchange channel (3b). Alternatively, the first port of the first cold plate (4a) is connected to the second port of the second heat exchange channel (3b), the first port of the second cold plate (4b) is connected to the second port of the first cold plate (4a), and the second port of the second cold plate (4b) is connected to the first port of the second heat exchange channel (3b).

4. The thermal management device according to any one of claims 1-3, characterized in that, The thermal management device includes a power pump (6), a first control valve (7), a second control valve (8), a third control valve (9), and a fourth control valve (10). The second port of the power pump (6) is connected to the first port of the heat exchange assembly (4), the first port of the power pump (6) is connected to the second port of the first control valve (7) and the second port of the second control valve (8), the first port of the first control valve (7) is connected to the second port of the first heat exchanger (1), and the first port of the second control valve (8) is connected to the second port of the second heat exchange channel (3b). The second port of the heat exchange component (4) is connected to the first port of the third control valve (9) and the first port of the fourth control valve (10). The second port of the third control valve (9) is connected to the first port of the second heat exchange channel (3b). The second port of the fourth control valve (10) is connected to the first port of the first heat exchanger (1).

5. The thermal management device according to claim 4, characterized in that, The thermal management device includes a first liquid storage tank (11), the second port of the first liquid storage tank (11) is connected to the first port of the power pump (6), and the first port of the first liquid storage tank (11) is connected to the second port of the first control valve (7) and the second port of the second control valve (8).

6. The thermal management device according to any one of claims 1-3, characterized in that, The first circulation loop includes a first expansion valve (5); the second port of the compressor (2) is connected to the first port of the first heat exchanger (1), the first port of the first expansion valve (5) is connected to the second port of the first heat exchanger (1), the first port of the first heat exchange channel (3a) is connected to the second port of the first expansion valve (4), and the second port of the first heat exchange channel (3a) is connected to the first port of the compressor (2).

7. The thermal management device according to claim 6, characterized in that, The thermal management device includes a third heat exchanger (12) and a second expansion valve (13). The first port of the third heat exchanger (12) is connected to the second port of the second expansion valve (13). The second port of the third heat exchanger (12) is connected to the first port of the compressor (2). The first port of the second expansion valve (13) is connected to the second port of the first heat exchanger (1). And / or, the thermal management device includes a fourth heat exchanger (14) and a third expansion valve (15), the first port of the fourth heat exchanger (14) being connected to the second port of the third expansion valve (15), the second port of the fourth heat exchanger (14) being connected to the first port of the compressor (2), and the first port of the third expansion valve (15) being connected to the second port of the first heat exchanger (1).

8. The thermal management device according to claim 7, characterized in that, The thermal management device includes a fifth heat exchanger (16) and a fourth expansion valve (17). The first port of the fifth heat exchanger (16) is connected to the first port of the compressor (2), or the first port of the fifth heat exchanger (16) is connected to the second port of the compressor (2). The second port of the fifth heat exchanger (16) is connected to the first port of the fourth expansion valve (17), and the second port of the fourth expansion valve (17) is connected to the first port of the first expansion valve (5), the first port of the second expansion valve (13), the first port of the third expansion valve (15), and the second port of the first heat exchanger (1).

9. The thermal management device according to claim 8, characterized in that, The thermal management device includes a sixth heat exchanger (18) and a fifth expansion valve (19). The first port of the sixth heat exchanger (18) is connected to the first port of the compressor (2), and the second port of the sixth heat exchanger (18) is connected to the first port of the fifth expansion valve (19). The second port of the fifth expansion valve (19) is connected to the first port of the first expansion valve (5), the first port of the second expansion valve (13), the first port of the third expansion valve (15), and the second port of the fourth expansion valve (17).

10. The thermal management device according to claim 8, characterized in that, The compressor (2) has two first ports. One of the first ports of the compressor (2) is connected to the first port of the fifth heat exchanger (16) and the second port of the second heat exchange channel (3b). The other first port of the compressor (2) is connected to the second port of the third heat exchanger (12) and the second port of the fourth heat exchanger (14).

11. The thermal management device according to claim 8, characterized in that, The thermal management device includes a second liquid storage tank (21), the first port of the second liquid storage tank (21) is connected to the second port of the first heat exchanger (1), and the second port of the second liquid storage tank (21) is connected to the first port of the first expansion valve (5), the first port of the second expansion valve (13), the first port of the third expansion valve (15), and the second port of the fourth expansion valve (17).

12. The thermal management device according to claim 8, characterized in that, The thermal management device includes a sixth expansion valve (22) disposed between the second port of the second heat exchange channel (3b) and the first port of the compressor (2); and / or, the sixth expansion valve (22) disposed between the second port of the third heat exchanger (12) and the first port of the compressor (2); and / or, the sixth expansion valve (22) disposed between the first port of the fifth heat exchanger (16) and the first port of the compressor (2).

13. The thermal management device according to any one of claims 1-3, characterized in that, The thermal management device includes a seventh expansion valve (23), which is located between the first port of the first heat exchanger (1) and the second port of the compressor (2).

14. The thermal management device according to claim 8, characterized in that, The thermal management device includes an eighth expansion valve (24), which is located between the first port of the fifth heat exchanger (16) and the second port of the compressor (2).

15. A vehicle, characterized in that, Includes the thermal management device according to any one of claims 1-14.

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