A dual-compressor indirect heat management system

Abstract

The application discloses a double-compressor indirect heat management system. The double-compressor indirect heat management system comprises a refrigerant circuit I and a refrigerant circuit II, the refrigerant circuit I comprises a compressor I, a water-cooled condenser I and an air conditioner evaporator which are sequentially and serially connected, the air conditioner evaporator is parallelly connected with a plate exchanger I, the refrigerant circuit II comprises a compressor II, a water-cooled condenser II and a plate exchanger II which are sequentially and serially connected, the refrigerant circuit I is coupled with a cabin heating circuit through the water-cooled condenser I, the cabin heating circuit comprises a heating core, an air conditioner water pump, the water-cooled condenser I and a multi-way valve I which are sequentially and serially connected, the refrigerant circuit I is coupled with a battery cooling circuit through the plate exchanger I, the battery cooling circuit is integrally connected with an electric drive cooling circuit through a multi-way valve II, the electric drive cooling circuit comprises an electric drive system, the multi-way valve II, the water-cooled condenser II, an electric drive water pump and an electric machine radiator which are sequentially and serially connected. The application solves the problem of poor control robustness of the prior art under certain working conditions.

Description

Technical Field

[0001] This invention relates to the field of vehicle thermal management system technology, and in particular to a dual-compressor indirect thermal management system. Background Technology

[0002] There is an existing Chinese utility model patent with publication number CN221873761U, entitled "A Heat Pump Thermal Management System and Vehicle". The disclosed first refrigerant circulation loop includes a first compressor, a condenser, and a first outdoor heat exchanger connected in sequence, and a second refrigerant circulation loop includes a second compressor, a second outdoor heat exchanger, and a second battery cooler connected in sequence. Both the first and second outdoor heat exchangers are outdoor heat exchangers. Under certain operating conditions, such as in air-source heat pump heating mode, the low-temperature, low-pressure refrigerant inside absorbs heat from the outside air through the outdoor heat exchanger, thereby evaporating into gas. At this time, the surface temperature of the outdoor heat exchanger will be below 0°C. When humid air encounters it, the moisture in it will condense and frost, resulting in poor system control robustness. Summary of the Invention

[0003] The purpose of this invention is to provide a dual-compressor indirect thermal management system with good control robustness.

[0004] To achieve the above-mentioned objectives, the dual-compressor indirect thermal management system of the present invention adopts the following technical solution:

[0005] A dual-compressor indirect thermal management system includes a refrigerant circuit one and a refrigerant circuit two. Refrigerant circuit one includes a compressor one, a water-cooled condenser one, and an air conditioning evaporator connected in series. The air conditioning evaporator is connected in parallel with a plate heat exchanger one. Refrigerant circuit two includes a compressor two, a water-cooled condenser two, and a plate heat exchanger two connected in series. Refrigerant circuit one is coupled to a cabin heating circuit through the water-cooled condenser one. The cabin heating circuit includes a heater core, an air conditioning water pump, the water-cooled condenser one, and a multi-way valve one connected in series. The multi-way valve one is also connected to an air conditioning radiator. The air conditioning radiator is connected to the air conditioning water pump. Refrigerant circuit one is coupled to a battery cooling circuit through the plate heat exchanger one. The battery cooling circuit is coupled to refrigerant circuit two through the plate heat exchanger two. The battery cooling circuit is integrated with an electric drive cooling circuit through the multi-way valve two. The electric drive cooling circuit includes an electric drive system, a multi-way valve two, a water-cooled condenser two, an electric drive water pump, and a motor radiator connected in series.

[0006] Preferably, the electric drive cooling circuit further includes a multi-way valve three, which is disposed between the motor radiator and the electric drive water pump. The multi-way valve three is connected to a bypass pipe one, which is connected in parallel with the motor radiator.

[0007] Preferably, the battery cooling circuit includes a battery, an electric heater, a plate heat exchanger one, a plate heat exchanger two, a battery water pump, and a multi-way valve two connected in series.

[0008] Preferably, the second multi-way valve is connected to a second bypass pipe, which is connected in parallel with the battery.

[0009] Preferably, the multi-way valve one and multi-way valve three are three-way water valves, and the multi-way valve two is a five-way water valve.

[0010] Preferably, the inlet end of the air conditioner evaporator is provided with an electronic expansion valve one, the inlet end of the refrigerant side passage of the plate heat exchanger one is provided with an electronic expansion valve two, and the inlet end of the refrigerant side passage of the plate heat exchanger two is provided with an electronic expansion valve three.

[0011] Preferably, the inlet end of the compressor one is provided with a gas-liquid separator, and the outlet end of the agent-side passage of the water-cooled condenser two is provided with a liquid storage tank.

[0012] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0013] 1. Refrigerant circuits one and two can dissipate or absorb heat through the motor radiator, thus eliminating the need for an outdoor heat exchanger for the refrigerant path. This prevents frost buildup on the outdoor heat exchanger and improves system control robustness. Eliminating the outdoor heat exchanger not only reduces costs but also saves space, which is beneficial for the overall vehicle layout.

[0014] 2. The battery can be disconnected through the bypass pipe 2, and the electric heater in the battery cooling circuit can be used to provide a heat source for the refrigerant circuit 1. The compressor 1 can heat the cabin, and there is no need to install an electric heater in the cabin heating circuit, so as to reduce costs.

[0015] 3. The system is more simplified, with fewer valves used for switching circuits (only one five-way water valve and two three-way water valves), resulting in lower cost, lower risk of leakage, higher safety, and easier operation. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of the dual-compressor indirect thermal management system of the present invention.

[0017] Figure 2 This is the working principle diagram for working condition one.

[0018] Figure 3 This is the working principle diagram for working condition two.

[0019] Figure 4 This is the working principle diagram for working condition three.

[0020] Figure 5 This is the working principle diagram for working condition four.

[0021] Figure 6 This is the working principle diagram for working condition five.

[0022] Figure 7 This is the working principle diagram for working condition six.

[0023] The components are as follows: 1. Compressor I; 2. Water-cooled condenser I; 3. Air conditioning evaporator; 4. Plate heat exchanger I; 5. Gas-liquid separator; 6. Electronic expansion valve I; 7. Electronic expansion valve II; 8. Compressor II; 9. Water-cooled condenser II; 10. Plate heat exchanger II; 11. Liquid receiver; 12. Electronic expansion valve III; 13. Heater core; 14. Air conditioning water pump; 15. Multi-way valve I; 16. Air conditioning radiator; 17. Battery; 18. Electric heater; 19. Battery water pump; 20. Multi-way valve II; 21. Electric drive system; 22. Electric drive water pump; 23. Multi-way valve III; 24. Motor radiator; 25. Bypass pipe I; 26. Bypass pipe II. Detailed Implementation

[0024] The present invention will be further illustrated below with reference to specific embodiments. It should be understood that these embodiments are for illustrative purposes only and are not intended to limit the scope of the invention. After reading the present invention, any modifications of the present invention in various equivalent forms by those skilled in the art will fall within the scope defined by the appended claims.

[0025] like Figure 1As shown, a dual-compressor indirect thermal management system includes a refrigerant circuit one and a refrigerant circuit two. Refrigerant circuit one includes a compressor-1, a water-cooled condenser-2, and an air conditioning evaporator-3 connected in series. The air conditioning evaporator-3 is connected in parallel to a plate heat exchanger-4. A gas-liquid separator-5 is installed at the inlet end of compressor-1. The outlet end of compressor-1 is connected to the inlet end of the refrigerant-side passage of the water-cooled condenser-2. The inlet ends of the air conditioning evaporator-3 and the refrigerant-side passages of the plate heat exchanger-4 are connected in parallel to the outlet end of the refrigerant-side passage of the water-cooled condenser-2. The outlet ends of the air conditioning evaporator-3 and the refrigerant-side passages of the plate heat exchanger-4 are connected in parallel to the gas-liquid separator-5. An electronic expansion valve-6 is installed at the inlet end of the air conditioning evaporator-3, and an electronic expansion valve-6 is installed at the inlet end of the refrigerant-side passage of the plate heat exchanger-4. Expansion valve 7; refrigerant circuit 2 includes compressor 8, water-cooled condenser 9, and plate heat exchanger 10 connected in series. The inlet of compressor 10 is connected to the outlet of the refrigerant-side passage of plate heat exchanger 10, and the outlet of compressor 10 is connected to the inlet of the refrigerant-side passage of water-cooled condenser 9. The outlet of the refrigerant-side passage of water-cooled condenser 9 is connected to the inlet of the refrigerant-side passage of plate heat exchanger 10. A liquid receiver 11 is installed at the outlet of the refrigerant-side passage of water-cooled condenser 9, and an electronic expansion valve 12 is installed at the inlet of the refrigerant-side passage of plate heat exchanger 10. Refrigerant circuit 1 is coupled to cabin heating circuit through water-cooled condenser 2. Cabin heating circuit includes heater core 13, air conditioning water pump 14, water-cooled condenser 2, and multi-way valve 15 connected in series. The outlet of the heater core 13 is connected to the inlet of the air conditioning water pump 14. The outlet of the air conditioning water pump 14 is connected to the inlet of the water-side passage of the water-cooled condenser 2. The outlet of the water-side passage of the water-cooled condenser 2 is connected to a multi-way valve 15, which is a three-way water valve. The b port of the multi-way valve 15 is connected to the outlet of the water-side passage of the water-cooled condenser 2. The c port of the multi-way valve 15 is connected to the inlet of the heater core 13. The a port of the multi-way valve 15 is connected to the air conditioning radiator 16. The inlet of the air conditioning radiator 16 is connected to the a port of the multi-way valve 15. The outlet of the air conditioning radiator 16 is connected to the inlet of the air conditioning water pump 14. The refrigerant circuit 1 is coupled to the battery cooling circuit through the plate heat exchanger 4. The battery cooling circuit is connected to the refrigerant circuit through ... The second heat exchanger 10 is coupled to the second refrigerant circuit. The battery cooling circuit includes, in series, a battery 17, an electric heater 18, a first heat exchanger 4, a second heat exchanger 10, a battery water pump 19, and a second multi-way valve 20. The second multi-way valve 20 is a five-way valve. Its a-port is connected to the outlet of the battery water pump 19, and its inlet is connected to the outlet of the water-side passage of the second heat exchanger 10. The inlet of the water-side passage of the second heat exchanger 10 is connected to the outlet of the water-side passage of the first heat exchanger 4. The inlet of the water-side passage of the first heat exchanger 4 is connected to the outlet of the battery 17 via the electric heater 18. The inlet of the battery 17 is connected to the d-port of the second multi-way valve 20, and its e-port is connected to a bypass pipe 26. The bypass pipe 26 is connected in parallel with the battery 17.The battery cooling circuit is integrated with the electric drive cooling circuit via multi-way valve 20. The electric drive cooling circuit includes, in series, an electric drive system 21, multi-way valve 20, water-cooled condenser 29, electric drive water pump 22, multi-way valve 3 23, and motor radiator 24. Multi-way valve 3 23 is a three-way water valve. The inlet of the electric drive system 21 is connected to port b of multi-way valve 22. Port C of multi-way valve 22 is connected to the outlet of the water-side passage of water-cooled condenser 29. The inlet of the water-side passage of water-cooled condenser 29 is connected to the outlet of electric drive water pump 22. The inlet of electric drive water pump 22 is connected to port a of multi-way valve 3 23. Port c of multi-way valve 3 23 is connected to the outlet of motor radiator 24. Port b of multi-way valve 3 23 is connected to bypass pipe 25. Bypass pipe 25 and the inlet of motor radiator 24 are connected in parallel to the outlet of electric drive system 21.

[0026] A control method for a dual-compressor indirect thermal management system, including the following application scenarios:

[0027] Operating Condition 1: Ambient temperature below -20℃, cabin heating and independent electric drive insulation mode.

[0028] like Figure 2 As shown, under this operating condition, the b and c ports of multi-way valve 15 are connected, the a and e ports of multi-way valve 20 are connected, the b and c ports of multi-way valve 20 are connected, and the a and b ports of multi-way valve 3 are connected. Driven by the battery water pump 19, the coolant heated by the electric heater 18 enters the water-side passage of the plate heat exchanger 4, providing a heat source for the vaporization of the liquid refrigerant in the refrigerant-side passage of the plate heat exchanger 4. The low-temperature, low-pressure gaseous refrigerant is compressed by the compressor 1 to form a high-temperature, high-pressure gaseous refrigerant. The gaseous refrigerant, under high temperature and pressure, enters the refrigerant-side passage of the water-cooled condenser 2 and liquefies, releasing heat. The coolant in the water-side passage of the water-cooled condenser 2 absorbs heat and rises in temperature. Driven by the air conditioning water pump 14, the heated coolant enters from port b and exits from port c of the multi-way valve 1, entering the heater core 13 to heat the cabin. The cooled coolant enters from port a and exits from port e of the multi-way valve 20, and then returns to the electric heater 18 for reheating through the bypass pipe 26. Driven by the electric drive water pump 22, the coolant in the electric drive coolant circuit passes through the water-side passage of the water-cooled condenser 29, enters from port c and exits from port b of the multi-way valve 20, absorbs the heat generated after the electric drive system 21 starts, and rises in temperature. The heated coolant then returns to the electric drive water pump 22 through the bypass pipe 25, enters from port b and exits from port a of the multi-way valve 3, completing the circulation. This achieves independent heat preservation of the electric drive cooling circuit.

[0029] This operating condition is suitable for extremely cold weather (ambient temperature below -20℃), where there is no external heat to draw upon. The electric drive system 21 starts up without waste heat. At this time, the electric heater 18 in the battery coolant circuit serves as an "artificial heat source" for the heat pump system (refrigerant circuit one). The battery 17 is disconnected through bypass pipe two 26 in the battery cooling circuit to prevent the low-temperature battery 17 from absorbing heat, thus allowing the coolant in the battery cooling circuit to heat up rapidly and quickly reach the operating conditions of the heat pump system (refrigerant circuit one). The coolant in the electric drive cooling circuit rapidly heats up in the small circulation loop formed by the electric drive system 21, multi-way valve two 20, water-cooled condenser two 9, electric drive water pump 22, multi-way valve three 23, and bypass pipe one 25, relying on the heat generated by the operation of the electric drive system 21 itself.

[0030] Operating Condition 2: Winter Electric-Driven Heat Pump Heating Mode

[0031] like Figure 3 As shown, under this operating condition, the b and c ports of multi-way valve 15 are connected, the a and b ports of multi-way valve 20 are connected, the e and c ports of multi-way valve 20 are connected, and the a and b ports of multi-way valve 3 are connected. Driven by the battery water pump 19 or the electric drive water pump 22, the coolant, which absorbs the heat generated by the operation of the electric drive system 21 and is heated, enters through the b port and exits through the a port of multi-way valve 3 through the bypass pipe 25, then enters through the c port and exits through the e port of multi-way valve 2 through the water-side passage of the water-cooled condenser 29, and directly enters the water-side passage of the plate heat exchanger 4 through the bypass pipe 26, thus becoming part of the heat exchanger 4's heat exchanger side passage. Liquid refrigerant vaporizes to provide a heat source. Low-temperature, low-pressure gaseous refrigerant is compressed by compressor 1 to form high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant enters the refrigerant-side passage of water-cooled condenser 2, liquefies, and releases heat. The coolant in the water-side passage of water-cooled condenser 2 absorbs heat and rises in temperature. Driven by air conditioning water pump 14, the heated coolant enters from port b and exits from port c of multi-port valve 1, enters the heater core 13, and achieves cabin heating. After cooling down, the coolant exits from the water-side passage of plate heat exchanger 4, enters from port a and exits from port b of multi-port valve 20, and then returns to electric drive system 21 to absorb heat and complete the cycle.

[0032] In this operating condition, the waste heat from the electric drive system 21 is recovered and used as a heat source for the heat pump system (refrigerant loop one). The path of the coolant to the battery 17 is forcibly cut off through the bypass pipe 26, preventing the battery 17 from overheating due to the high-temperature coolant, thus ensuring the battery 17's lifespan and safety. Furthermore, in this operating condition, the user can selectively activate the electric heater 18 for supplemental heating as needed to meet the cabin's heating requirements.

[0033] Operating Condition 3: Summer Driving Cooling Mode

[0034] like Figure 4As shown, under this operating condition, ports a and b of multi-way valve 15 are connected, ports a and d of multi-way valve 20 are connected, ports b and c of multi-way valve 20 are connected, and ports a and c of multi-way valve 23 are connected. Driven by air conditioning water pump 14, the low-temperature coolant after exchanging heat with the outside through air conditioning radiator 16 enters the water-side passage of water-cooled condenser 2, providing cooling capacity to the refrigerant-side passage of water-cooled condenser 2. The low-temperature, low-pressure gaseous refrigerant is compressed by compressor 1 to form a high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant enters the refrigerant-side passage of water-cooled condenser 2, liquefies, and releases heat. The coolant in the water-side passage of water-cooled condenser 2 carries away the heat and enters through port b and exits through port a of multi-way valve 15, returning to air conditioning radiator 16 to continue heat dissipation and complete the cycle. A portion of the liquid refrigerant formed in the refrigerant-side passage of water-cooled condenser 2 enters air conditioning evaporator 3 through expansion valve 6. Another portion enters the refrigerant-side passage of the plate heat exchanger 4 through expansion valve 2 7, where the liquid refrigerant in the air conditioning evaporator 3 absorbs heat and evaporates, achieving cabin cooling. The liquid refrigerant entering the refrigerant-side passage of the plate heat exchanger 4 absorbs heat from the coolant in the water-side passage of the plate heat exchanger 4 and evaporates. Driven by the battery water pump 19, the cooled coolant exits from the water-side passage of the plate heat exchanger 4 and enters directly into the battery 17 through the a port and d port of the multi-way valve 20, achieving battery cooling. Driven by the electric drive water pump 22, the coolant in the electric drive coolant circuit carries away the heat generated by the electric drive system 21 during operation. The heated coolant exchanges heat with the outside when passing through the motor radiator 24. The cooled coolant enters from the c port and exits from the a port of the multi-way valve 3 23, then enters from the c port and exits from the b port of the multi-way valve 20 through the water-cooled condenser 2 9, and then returns to the electric drive system 21 to circulate and absorb heat.

[0035] Under this operating condition, the refrigerant circuit indirectly obtains cooling capacity through the air conditioning radiator 16.

[0036] Operating Condition 4: High-Temperature Fast Charging and High-Cooling Demand Mode in Summer

[0037] like Figure 5 As shown, this operating condition is based on operating condition three, in which refrigerant circuit two is activated. That is, the low-temperature and low-pressure gaseous refrigerant is compressed by compressor two 8 to form a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant enters the refrigerant-side passage of water-cooled condenser two 9 and liquefies. At this time, the electric drive cooling circuit provides cooling for the liquefaction of gaseous refrigerant in the refrigerant-side passage of water-cooled condenser two 9. The liquid refrigerant enters the refrigerant-side passage of plate heat exchanger two 10 through electronic expansion valve three 12 to absorb heat and evaporate. The coolant in the battery cooling circuit is cooled twice by plate heat exchanger one 4 and plate heat exchanger two 10 in sequence to obtain a large amount of cooling, suppressing the temperature rise of battery 17 during fast charging.

[0038] Under this operating condition, the refrigerant circuit 2 indirectly obtains cooling capacity through the motor radiator 24.

[0039] Operating Condition 5: Cabin Heating and Dehumidification Mode

[0040] like Figure 6 As shown, under this operating condition, ports b and c of multi-way valve 15 are connected, ports a and d of multi-way valve 20 are connected, ports b and c of multi-way valve 20 are connected, and ports a and c of multi-way valve 3 are connected. Low-temperature, low-pressure gaseous refrigerant is compressed by compressor 1 to form high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant enters the refrigerant-side passage of water-cooled condenser 2, liquefies, and releases heat. Part of the liquid refrigerant enters the air conditioner evaporator 3 through expansion valve 6, and the other part enters the refrigerant-side passage of heat exchanger 4 through expansion valve 2 7. The liquid refrigerant entering the refrigerant-side passage of heat exchanger 4 absorbs heat from the coolant in the water-side passage of heat exchanger 4 and evaporates. Driven by battery water pump 19, the cooled coolant exits from the water-side passage of heat exchanger 4 and enters directly into battery 17 through ports a and d of multi-way valve 20, thus cooling battery 17. The liquid refrigerant entering the air conditioning evaporator 3 absorbs heat and evaporates, cooling the cabin. The circulating air in the cabin is guided to the low-temperature air conditioning evaporator 3, causing water vapor to condense and precipitate, completing dehumidification. Driven by the air conditioning water pump 14, the coolant in the water-side passage of the water-cooled condenser 2 heats up after heat exchange. The heated coolant enters from port b and exits from port c of the multi-way valve 1, entering the heater core 13 and blowing dry warm air into the cabin to achieve heating. Driven by the electric drive water pump 22, the coolant in the electric drive coolant circuit carries away the heat generated by the electric drive system 21 during operation. The heated coolant exchanges heat with the outside when passing through the motor radiator 24. The cooled coolant enters from port c and exits from port a of the multi-way valve 3 23, then enters from port c and exits from port b of the multi-way valve 20 through the water-side passage of the water-cooled condenser 9, and then returns to the electric drive system 21 to circulate and absorb heat.

[0041] Operating Condition 6: Energy-Saving Mode During Transitional Seasons

[0042] like Figure 7 As shown, under this operating condition, the a and b ports of multi-way valve 20 are connected, the c and d ports of multi-way valve 20 are connected, and the a and c ports of multi-way valve 3 are connected. At this time, the battery cooling circuit and the electric drive cooling circuit are connected in series to form a large circulation circuit. Driven by the electric drive water pump 22 (or the battery water pump 19), the coolant in the large circulation circuit passes through the water-side passage of the water-cooled condenser 29, enters from the c port and exits from the d port of multi-way valve 20, and carries away the heat generated by the battery 17 during operation. Then, it passes through the water-side passages of the plate heat exchanger 1 4 and the plate heat exchanger 2 10 in sequence, enters from the a port and exits from the b port of multi-way valve 20, and carries away the heat generated by the electric drive system 21 during operation. When the high-temperature coolant enters the motor radiator 24, it exchanges heat with the outside. The cooled coolant enters from the c port and exits from the a port of multi-way valve 3 23 and returns to the electric drive water pump 22 to complete the circulation.

[0043] This operating condition occurs during the transitional season between spring and autumn, when the ambient temperature is low (e.g., 10℃). Due to the high load, battery 17 needs to dissipate heat. The cool air from nature is used to cool battery 17 directly, achieving "zero compressor energy consumption" natural cooling of the internal battery 17 from an external cold source, thus saving energy.

[0044] This invention also has other applications, which will not be listed one by one, and can meet the needs of use in all scenarios.

[0045] The detailed description listed above is merely a specific description of feasible embodiments of the present invention and is not intended to limit the scope of protection of the present invention.

Claims

1. A dual-compressor indirect thermal management system, characterized in that: The system includes two refrigerant circuits: Refrigerant Circuit 1 and Refrigerant Circuit 2. Refrigerant Circuit 1 consists of a compressor, a water-cooled condenser, and an air conditioning evaporator connected in series. A heat exchanger is connected in parallel to the air conditioning evaporator. Refrigerant Circuit 2 consists of a compressor, a water-cooled condenser, and a heat exchanger connected in series. Refrigerant Circuit 1 is coupled to the cabin heating circuit via the water-cooled condenser. The cabin heating circuit consists of a heater core, an air conditioning water pump, the water-cooled condenser, and a multi-way valve connected in series. The multi-way valve is also connected to an air conditioning radiator, which is connected to the air conditioning water pump. Refrigerant Circuit 1 is coupled to the battery cooling circuit via the heat exchanger. The battery cooling circuit is coupled to Refrigerant Circuit 2 via the heat exchanger. The battery cooling circuit is integrated with an electric drive cooling circuit via the multi-way valve. The electric drive cooling circuit consists of an electric drive system, a multi-way valve, the water-cooled condenser, the electric drive water pump, and a motor radiator connected in series.

2. The dual-compressor indirect thermal management system according to claim 1, characterized in that: The electric drive cooling circuit also includes a multi-way valve three, which is located between the motor radiator and the electric drive water pump. The multi-way valve three is connected to a bypass pipe one, which is connected in parallel with the motor radiator.

3. The dual-compressor indirect thermal management system according to claim 2, characterized in that: The battery cooling circuit includes a battery, an electric heater, a heat exchanger (number 1), a heat exchanger (number 2), a battery water pump, and a multi-way valve (number 2) connected in series.

4. The dual-compressor indirect thermal management system according to claim 3, characterized in that: The second multi-way valve is connected to a second bypass pipe, which is connected in parallel with the battery.

5. The dual-compressor indirect thermal management system according to claim 4, characterized in that: The multi-way valve one and multi-way valve three are three-way water valves, and the multi-way valve two is a five-way water valve.

6. The dual-compressor indirect thermal management system according to claim 3, characterized in that: The air conditioner evaporator is equipped with an electronic expansion valve one at its inlet end, the refrigerant side passage of the plate heat exchanger one is equipped with an electronic expansion valve two at its inlet end, and the refrigerant side passage of the plate heat exchanger two is equipped with an electronic expansion valve three at its inlet end.

7. The dual-compressor indirect thermal management system according to claim 6, characterized in that: The compressor one is equipped with a gas-liquid separator at its inlet end, and the water-cooled condenser two is equipped with a liquid storage tank at the outlet end of its agent-side passage.

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