Heat management system for new energy vehicle and vehicle

Abstract

The application provides a heat management system for a new energy vehicle and the vehicle, and a refrigerant circuit of the heat management system comprises a compressor, a first heat exchanger, a high-pressure liquid storage drier, a first internal heat exchanger, a second heat exchanger, a third heat exchanger and a first double-fluid heat exchanger. The flow direction of refrigerant in the first heat exchanger is reversible, and the first heat exchanger can be used as an evaporator or a condenser; and the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the first internal heat exchanger can exchange heat. The application can form a directly reversible heat pump air conditioning system, which is relatively simple in structure, and can realize single refrigeration, double refrigeration, waste heat recovery, heat pump + heat recovery and dehumidification and other working modes on the basis of the heat pump mode, thereby facilitating the popularization and application of the heat pump type management system.

Description

Technical Field

[0001] This invention relates to the field of technology, and in particular to a thermal management system for new energy vehicles. The invention also relates to vehicles equipped with the aforementioned thermal management system for new energy vehicles. Background Technology

[0002] With technological advancements and rising living standards, new energy vehicles are gaining increasing popularity among consumers. Currently, many new energy vehicles still utilize the same single-unit systems as gasoline vehicles, typically replacing the engine waste heat heating system with PTC water heating or electric heating. This simple PTC heating method suffers from drawbacks such as difficulty in controlling power and temperature, low energy efficiency, and high power consumption, severely restricting the thermal management effectiveness of new energy vehicles.

[0003] As a more energy-efficient vehicle thermal management architecture, the heat pump air conditioning system significantly reduces power consumption during heating compared to the traditional PTC heating method, helping to ensure the vehicle's driving range. However, the heat pump air conditioning systems currently used in new energy vehicles still have shortcomings such as relatively complex structure, high cost, limited operating modes, and low heat exchange capacity, which to some extent restrict the widespread application of heat pump air conditioning systems. Summary of the Invention

[0004] In view of this, the present invention aims to propose a thermal management system for new energy vehicles, so as to facilitate the promotion and application of heat pump air conditioning systems.

[0005] To achieve the above objectives, the technical solution of the present invention is implemented as follows:

[0006] A thermal management system for new energy vehicles, wherein the refrigerant circuit of the thermal management system includes a compressor, a first heat exchanger, a high-pressure liquid receiver-dryer, a first internal heat exchanger, a second heat exchanger, a third heat exchanger, and a first dual-fluid heat exchanger.

[0007] One end of the first heat exchanger is connected to the outlet of the compressor through a first shut-off valve, and the other end of the first heat exchanger is connected in parallel with a first check valve and a second expansion valve. The first check valve is connected to the inlet of the high-pressure liquid storage dryer, and the second expansion valve is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger.

[0008] The inlet of the second heat exchanger is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger through the first expansion valve. The outlet of the second heat exchanger is connected in parallel with a second check valve and a second shut-off valve. The second check valve is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger. The second shut-off valve and the first shut-off valve are connected in parallel at the same end of the first heat exchanger.

[0009] One end of the third heat exchanger is connected to the outlet of the compressor via a third shut-off valve, and the other end of the third heat exchanger is connected to the inlet of the high-pressure liquid storage dryer via a third check valve. The outlet of the high-pressure liquid storage dryer is connected to the inlet of the high-pressure side heat exchange channel in the first internal heat exchanger, and the outlet of the low-pressure side heat exchange channel in the first internal heat exchanger is connected to the inlet of the compressor.

[0010] One end of the first dual-fluid heat exchanger is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger via a third expansion valve, and the other end of the first dual-fluid heat exchanger is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger.

[0011] The refrigerant in the first heat exchanger is reversible and can function as an evaporator or condenser. Furthermore, the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the first internal heat exchanger can exchange heat.

[0012] Furthermore, the coolant channel in the first dual-fluid heat exchanger is connected to the cooling channel in the battery pack and the cooling channel in the drive motor.

[0013] Furthermore, the refrigerant circuit also includes a second two-fluid heat exchanger;

[0014] One end of the second dual-fluid heat exchanger is connected to the outlet of the compressor via a fourth shut-off valve, and the other end of the second dual-fluid heat exchanger is connected to the inlet of the high-pressure liquid storage dryer.

[0015] Furthermore, the refrigerant circuit also includes a second internal heat exchanger;

[0016] The inlet of the high-pressure side heat exchange channel in the second internal heat exchanger is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger, and the outlet of the high-pressure side heat exchange channel in the second internal heat exchanger is connected to the inlet of the second heat exchanger through the first expansion valve.

[0017] The inlet of the low-pressure side heat exchange channel in the second internal heat exchanger is connected to the outlet of the second heat exchanger, and the outlet of the low-pressure side heat exchange channel in the second internal heat exchanger is connected in parallel with the second check valve and the second shut-off valve.

[0018] The refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the second internal heat exchanger can exchange heat.

[0019] Furthermore, the first internal heat exchanger and / or the second internal heat exchanger may be coaxial tubes.

[0020] Furthermore, all valves in the refrigerant circuit, as well as at least one of the two-fluid heat exchangers, high-pressure liquid receiver-dryer, and internal heat exchangers, are integrated and arranged together.

[0021] Furthermore, the thermal management system has a single air conditioning cooling mode;

[0022] When the thermal management system is in the single air conditioning cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first heat exchanger through the first shut-off valve, and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger and becomes liquid.

[0023] Next, the refrigerant enters the high-pressure liquid storage dryer through the first check valve, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve, and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger to cool the gas inside the air conditioning unit and obtain enthalpy.

[0024] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger through the second check valve, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0025] Furthermore, the thermal management system has a single-battery cooling mode;

[0026] When the thermal management system is in the single-cell cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first heat exchanger through the first shut-off valve, and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger and becomes liquid.

[0027] Next, the refrigerant enters the high-pressure liquid storage dryer through the first check valve, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve, and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first two-fluid heat exchanger to cool the battery pack coolant flowing through the first two-fluid heat exchanger and obtain enthalpy.

[0028] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger, obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0029] Furthermore, the thermal management system has dual cooling modes;

[0030] When the thermal management system is in the dual cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first heat exchanger through the first shut-off valve, and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger and becomes liquid.

[0031] Next, the refrigerant enters the high-pressure liquid storage dryer through the first check valve, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant is split, with one path passing through the third expansion valve. The high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first two-fluid heat exchanger to cool the battery pack coolant flowing through the first two-fluid heat exchanger and obtain enthalpy.

[0032] Another refrigerant passes through the first expansion valve. The high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger to cool the gas inside the air conditioning unit and obtain enthalpy.

[0033] Next, the refrigerant passing through the second check valve merges with the refrigerant passing through the first dual-fluid heat exchanger and enters the low-pressure side heat exchange channel in the first internal heat exchanger. It obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0034] Furthermore, the thermal management system has a heat pump mode;

[0035] When the thermal management system is in the heat pump mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the third heat exchanger through the third shut-off valve and heats the air in the air conditioning unit to lose enthalpy at the third heat exchanger.

[0036] Next, the refrigerant enters the high-pressure liquid storage dryer after passing through the third check valve, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, transferring enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve, undergoes an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first heat exchanger to absorb heat from the outside air and obtain enthalpy.

[0037] Next, the refrigerant passes through the second shut-off valve and the second check valve into the low-pressure side heat exchange channel of the first internal heat exchanger. The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0038] Furthermore, the thermal management system has a waste heat recovery mode;

[0039] When the thermal management system is in the waste heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the third heat exchanger through the third shut-off valve and heats the air in the air conditioning unit to lose enthalpy at the third heat exchanger.

[0040] Next, the refrigerant enters the high-pressure liquid storage dryer through the third check valve, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant enters the third expansion valve, where it experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture.

[0041] Then, the low-pressure refrigerant passes through the first dual-fluid heat exchanger, absorbs heat from the coolant of the drive motor, and obtains enthalpy. Next, the refrigerant passes through the low-pressure side heat exchange channel in the first internal heat exchanger, obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel, and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0042] Furthermore, the thermal management system has a heat pump + heat recovery mode;

[0043] When the thermal management system is in the heat pump + heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the third heat exchanger through the third shut-off valve and heats the air in the air conditioning unit to lose enthalpy at the third heat exchanger.

[0044] Next, the refrigerant enters the high-pressure liquid storage dryer through the third check valve, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, transferring the enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant is divided into two paths. One path of the refrigerant passes through the second expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first heat exchanger to absorb heat from the outside air and obtain enthalpy, and then passes through the second shut-off valve into the second check valve.

[0045] Another refrigerant passes through the third expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first dual-fluid heat exchanger to absorb heat from the coolant of the drive motor and obtain enthalpy.

[0046] Next, after passing through the second check valve and the two refrigerants from the first dual-fluid heat exchanger, the refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger, obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0047] Furthermore, the thermal management system has a first dehumidification mode;

[0048] When the thermal management system is in the first dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the third heat exchanger through the third shut-off valve and heats the air in the air conditioning unit to lose enthalpy at the third heat exchanger.

[0049] Next, the refrigerant enters the high-pressure liquid receiver-dryer through the third check valve, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve, undergoes an isenthalpic pressure drop and crosses the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger to dehumidify the vehicle interior and obtain enthalpy.

[0050] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger through the second check valve, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0051] Furthermore, the thermal management system has a second dehumidification mode;

[0052] When the thermal management system is in the second dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the third heat exchanger through the third shut-off valve and heats the air in the air conditioning unit to lose enthalpy at the third heat exchanger.

[0053] Next, the refrigerant enters the high-pressure liquid receiver-dryer through the third check valve, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant is divided into two paths. One path of the refrigerant passes through the first expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the second heat exchanger to dehumidify the vehicle interior and obtain enthalpy.

[0054] Another refrigerant passes through the second expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first heat exchanger, where it absorbs heat from the outside air to gain enthalpy.

[0055] Next, after the two refrigerants pass through the second shut-off valve and the second heat exchanger, they merge and then enter the low-pressure side heat exchange channel in the first internal heat exchanger through the second check valve. They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0056] Furthermore, the thermal management system has a heat pump heating battery mode;

[0057] When the thermal management system is in the heat pump heating battery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger through the fourth shut-off valve to heat the battery and lose enthalpy.

[0058] Next, the refrigerant enters the high-pressure side heat exchange channel of the first internal heat exchanger through the high-pressure liquid storage dryer, and transfers its enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve, undergoes an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the first heat exchanger and absorbs heat from the outside air to obtain enthalpy.

[0059] Next, the refrigerant enters the low-pressure side heat exchange channel of the first internal heat exchanger through the second shut-off valve and the second check valve. The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0060] Furthermore, the thermal management system has a mode for heating the battery with waste heat from the motor;

[0061] When the thermal management system is in the mode of heating the battery with the waste heat of the motor, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger through the fourth shut-off valve to heat the battery and lose enthalpy.

[0062] Next, the refrigerant passes through the high-pressure liquid storage dryer and enters the high-pressure side heat exchange channel of the first internal heat exchanger, transferring its enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve, undergoes an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then passes through the second dual-fluid heat exchanger to absorb heat from the drive motor and obtain enthalpy.

[0063] Next, the refrigerant passes through the low-pressure side heat exchange channel in the first internal heat exchanger and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and crosses the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0064] Furthermore, the thermal management system has a mode of using waste heat from the motor plus a heat pump to heat the battery;

[0065] When the thermal management system is in the mode of motor waste heat + heat pump heating battery, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger through the fourth shut-off valve to heat the battery and lose enthalpy.

[0066] Next, the refrigerant passes through the high-pressure liquid storage dryer and enters the high-pressure side heat exchange channel of the first internal heat exchanger, transferring enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. The refrigerant is divided into two paths. One path of the refrigerant passes through the third expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second dual-fluid heat exchanger, absorbing heat from the drive motor to obtain enthalpy.

[0067] Another refrigerant passes through the second expansion valve, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first heat exchanger to absorb heat from the outside air and obtain enthalpy, before passing through the second check valve.

[0068] Next, after passing through the second check valve and the second dual-fluid heat exchanger, the two refrigerants merge and enter the low-pressure side heat exchange channel of the first internal heat exchanger. They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor.

[0069] Compared with the prior art, the present invention has the following advantages:

[0070] The thermal management system for new energy vehicles described in this invention, through the arrangement of a compressor, a high-pressure liquid storage dryer, an internal heat exchanger, and various heat exchangers and a dual-fluid heat exchanger, and through the control connection of multiple control valves, can form a directly reversible heat pump air conditioning system. Its structure is relatively simple. At the same time, based on the heat pump mode, it can also realize single cooling, dual cooling, as well as multiple working modes such as waste heat recovery, heat pump + heat recovery and dehumidification, which is conducive to the promotion and application of heat pump management systems.

[0071] Another object of the present invention is to provide a vehicle, which is a new energy vehicle, and the vehicle is provided with a thermal management system for new energy vehicles as described above.

[0072] The vehicle described in this invention has the same beneficial effects as the thermal management system for new energy vehicles described above, and will not be repeated here. Attached Figure Description

[0073] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0074] Figure 1 This is a schematic diagram of the thermal management system according to an embodiment of the present invention;

[0075] Figure 2 This is a schematic diagram illustrating the configuration of a first alternative to the thermal management system described in this embodiment of the invention.

[0076] Figure 3 This is a schematic diagram illustrating the configuration of a second alternative to the thermal management system described in this embodiment of the invention.

[0077] Figure 4 This is a schematic diagram illustrating the third alternative configuration of the thermal management system described in this embodiment of the invention.

[0078] Figure 5 This is a schematic diagram of the integrated arrangement of valves and heat exchange devices in the thermal management system described in an embodiment of the present invention;

[0079] Figure 6This is a schematic diagram of the integrated arrangement of valves and heat exchange devices in the thermal management system described in an embodiment of the present invention;

[0080] Figure 7 This is a schematic diagram of the thermal management system loop in single air conditioner cooling mode according to an embodiment of the present invention;

[0081] Figure 8 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy during single-air conditioner cooling mode as described in an embodiment of the present invention;

[0082] Figure 9 This is a schematic diagram of the thermal management system loop in the single-battery cooling mode according to an embodiment of the present invention;

[0083] Figure 10 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy in the single-cell cooling mode as described in an embodiment of the present invention;

[0084] Figure 11 This is a schematic diagram of the thermal management system loop in dual cooling mode as described in an embodiment of the present invention;

[0085] Figure 12 This is a schematic diagram showing the changes in refrigerant pressure and enthalpy during the dual-cooling mode described in this embodiment of the invention;

[0086] Figure 13 This is a schematic diagram of the thermal management system loop in heat pump mode as described in an embodiment of the present invention;

[0087] Figure 14 This is a schematic diagram showing the changes in refrigerant pressure and enthalpy in the heat pump mode described in this embodiment of the invention;

[0088] Figure 15 This is a schematic diagram of the thermal management system loop in the waste heat recovery mode described in the embodiment of the present invention;

[0089] Figure 16 This is a schematic diagram showing the changes in refrigerant pressure and enthalpy during the waste heat recovery mode described in this embodiment of the invention;

[0090] Figure 17 This is a schematic diagram of the thermal management system loop in the heat pump + heat recovery mode according to an embodiment of the present invention;

[0091] Figure 18 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy during the heat pump + heat recovery mode described in this embodiment of the invention.

[0092] Figure 19 This is a schematic diagram of the thermal management system loop in the first dehumidification mode according to an embodiment of the present invention;

[0093] Figure 20This is a schematic diagram showing the changes in refrigerant pressure and enthalpy during the first dehumidification mode described in this embodiment of the invention;

[0094] Figure 21 This is a schematic diagram of the thermal management system loop in the second dehumidification mode according to an embodiment of the present invention;

[0095] Figure 22 This is a schematic diagram showing the changes in refrigerant pressure and enthalpy during the second dehumidification mode as described in this embodiment of the invention;

[0096] Figure 23 This is a schematic diagram of the thermal management system loop in the heat pump heating battery mode according to an embodiment of the present invention;

[0097] Figure 24 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy during the heat pump heating battery mode as described in this embodiment of the invention.

[0098] Figure 25 This is a schematic diagram of the thermal management system circuit in the motor waste heat heating battery mode according to an embodiment of the present invention;

[0099] Figure 26 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy during the motor waste heat heating battery mode as described in an embodiment of the present invention;

[0100] Figure 27 This is a schematic diagram of the thermal management system loop in the motor waste heat + heat pump battery heating mode according to an embodiment of the present invention;

[0101] Figure 28 This is a schematic diagram illustrating the changes in refrigerant pressure and enthalpy during the motor waste heat + heat pump battery heating mode as described in an embodiment of the present invention;

[0102] Explanation of reference numerals in the attached figures:

[0103] 1. Compressor; 2. First shut-off valve; 3. First heat exchanger; 4. First check valve; 5. High-pressure liquid receiver-dryer; 6. First internal heat exchanger; 7. First expansion valve; 8. Second heat exchanger; 9. Second check valve; 10. Third heat exchanger; 11. Third check valve; 12. Second shut-off valve; 13. Third shut-off valve; 14. Fourth shut-off valve; 15. Second dual-fluid heat exchanger; 16. Second expansion valve; 17. First dual-fluid heat exchanger; 18. Third expansion valve; 25. Second internal heat exchanger;

[0104] 19-24, Connection Points;

[0105] 100. Integrated components. Detailed Implementation

[0106] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other.

[0107] In the description of this invention, it should be noted that the use of terms such as "upper," "lower," "inner," and "outer," indicating orientation or positional relationship, is based on the orientation or positional relationship shown in the accompanying drawings and is only for the convenience of describing the invention and simplifying the description. It does not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the use of terms such as "first" and "second" is also for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0108] Furthermore, in the description of this invention, unless otherwise explicitly defined, the terms "installation," "connection," "joining," and "connector" 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 via an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention in light of the specific circumstances.

[0109] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0110] Example 1

[0111] This embodiment relates to a thermal management system for new energy vehicles, which can realize multiple working modes such as single cooling, dual cooling, waste heat recovery, heat pump + heat recovery and dehumidification on the basis of heat pump mode, and is conducive to the promotion and application of heat pump management system in new energy vehicles.

[0112] At this point, it should be noted that the new energy vehicle in this embodiment can be, for example, a pure electric vehicle, a hybrid electric vehicle, or a fuel cell vehicle. Furthermore, in conjunction with... Figure 1 As shown, in terms of overall structure, the refrigerant circuit of the thermal management system in this embodiment includes a compressor 1, a first heat exchanger 3, a high-pressure liquid receiver-dryer 5, a first internal heat exchanger 6, a second heat exchanger 8, a third heat exchanger 10, and a first dual-fluid heat exchanger 17.

[0113] One end of the first heat exchanger 3 is connected to the outlet of the compressor 1 via a first shut-off valve 2 and a connection point 24. The other end of the first heat exchanger 3 is connected in parallel with a first check valve 4 and a second expansion valve 16 via a connection point 19. The first check valve 4 is connected to the inlet of the high-pressure liquid storage dryer 5, and the second expansion valve 16 is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger 6.

[0114] The inlet of the second heat exchanger 8 is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger 6 via the first expansion valve 7 and the connection points 20 and 21. The outlet of the second heat exchanger 8 is connected in parallel with the second check valve 9 and the second shut-off valve 12. The second check valve 9 is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger 6. The second shut-off valve 12 is connected in parallel with the first shut-off valve 2 at the same end of the first heat exchanger 3.

[0115] One end of the aforementioned third heat exchanger 10 is connected to the outlet of compressor 1 via a third shut-off valve 13 and a connection point 24. The other end of the third heat exchanger 10 is connected to the inlet of the high-pressure liquid receiver-dryer 5 via a third check valve 11. The outlet of the aforementioned high-pressure liquid receiver-dryer 5 is connected to the inlet of the high-pressure side heat exchange channel in the first internal heat exchanger 6, and the outlet of the low-pressure side heat exchange channel in the first internal heat exchanger 6 is connected to the inlet of compressor 1. Simultaneously, the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel in the first internal heat exchanger 6 can exchange heat.

[0116] The two fluids in the aforementioned first dual-fluid heat exchanger 17 are refrigerant and coolant, and correspondingly, the first dual-fluid heat exchanger 17 has a refrigerant channel and a coolant channel capable of heat exchange. One end of the refrigerant channel in the first dual-fluid heat exchanger 17 is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger 6 via a third expansion valve 18 and a connection point 21, while the other end of the refrigerant channel in the first dual-fluid heat exchanger 17 is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger 6.

[0117] Furthermore, the refrigerant flow direction in the first heat exchanger 3 is reversible, and depending on the refrigerant flow direction, it can function as an evaporator or a condenser. When it functions as an evaporator, the refrigerant in the first heat exchanger 3 absorbs heat from the outside air. When it functions as a condenser, the first heat exchanger 3 acts as a radiator, and the refrigerant inside it releases heat to the outside air.

[0118] The aforementioned second heat exchanger 8 is generally used as an evaporator in the vehicle's air conditioning unit to cool the air flowing through the air conditioning unit. The aforementioned third heat exchanger 8 is generally used as a heater core in the vehicle's air conditioning unit. Obviously, in this embodiment, the heater core is a direct heat exchange method in which the refrigerant directly exchanges heat with the air inside the air conditioning unit.

[0119] Meanwhile, based on the above overall configuration, as a preferred embodiment, the coolant passage in the first dual-fluid heat exchanger 17 is generally connected to the cooling passage in the vehicle's battery pack and the cooling passage in the drive motor. Thus, through heat exchange between the refrigerant and coolant in the first dual-fluid heat exchanger 17, the thermal management system of this embodiment can not only achieve battery cooling and heat pump heating of the battery, but also utilize the heat generated by the drive motor to absorb heat in heat pump mode, thereby eliminating the need for electric heating devices for heating the coolant and saving system costs.

[0120] Of course, based on the connection between the coolant passage in the first dual-fluid heat exchanger 17 and the cooling passage in the battery pack and drive motor, the specific design of the connection pipeline between the first dual-fluid heat exchanger 17 and the battery pack and drive motor, especially the arrangement of the corresponding control valves on the connection pipeline, can be set according to the design requirements of the specific vehicle model, in the case of matching the thermal management system design of this embodiment.

[0121] In this embodiment, as a preferred implementation, such as Figure 2 As shown, the refrigerant circuit may further include a second two-fluid heat exchanger 15. This second two-fluid heat exchanger 15 also exchanges heat between the refrigerant and the coolant. At this time, one end of the refrigerant passage in the second two-fluid heat exchanger 15 is connected to the outlet of the compressor 1 via a fourth shut-off valve 14 and a connection point 24, while the other end of the refrigerant passage in the second two-fluid heat exchanger 15 is connected to the inlet of the high-pressure liquid receiver-dryer 5 via a connection point 23.

[0122] It should be noted that the coolant passage in the second dual-fluid heat exchanger 15 can also be connected to the cooling passage in the battery pack of the vehicle. Thus, by connecting the second dual-fluid heat exchanger 15 to the outlet of the compressor 1, in particular, this embodiment allows the refrigerant and coolant in the second dual-fluid heat exchanger 15 to heat the battery during low-temperature fast charging of the entire vehicle, thereby better ensuring the battery's operating performance.

[0123] Of course, in addition to connecting to the cooling channels in the battery pack, the coolant channels in the second dual-fluid heat exchanger 15 in this embodiment can also be connected to the cooling channels in other components in the vehicle that need to be heated. The connecting pipes between the second dual-fluid heat exchanger 15 and them, as well as the control valves on the connecting pipes, can also be arranged according to specific design requirements.

[0124] like Figure 3 As shown, in Figure 1Based on the thermal management system configuration shown, as a preferred embodiment, the refrigerant circuit of this embodiment may further include a second internal heat exchanger 25. The inlet of the high-pressure side heat exchange channel of the second internal heat exchanger 25 is connected to the outlet of the high-pressure side heat exchange channel of the first internal heat exchanger 6 via connection points 20 and 21, and the outlet of the high-pressure side heat exchange channel of the second internal heat exchanger 25 is connected to the inlet of the second heat exchanger 8 via the first expansion valve 7.

[0125] The inlet of the low-pressure side heat exchange channel in the second internal heat exchanger 25 is connected to the outlet of the second heat exchanger 8, and the outlet of the low-pressure side heat exchange channel in the second internal heat exchanger 25 is connected in parallel with the second check valve 9 and the second shut-off valve 12 via connection point 22. Simultaneously, the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the second internal heat exchanger 25 can exchange heat.

[0126] like Figure 4 As shown, in Figure 2 Based on the thermal management system configuration shown, and also as a preferred embodiment, the refrigerant circuit of this embodiment may further include a second internal heat exchanger 25.

[0127] Moreover, with Figure 3 The second internal heat exchanger 25 is configured the same as in the previous one. Figure 4 In the heat management system shown, the inlet of the high-pressure side heat exchange channel in the second internal heat exchanger 25 is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger 6 via connection point 20 and connection point 21, and the outlet of the high-pressure side heat exchange channel in the second internal heat exchanger 25 is connected to the inlet of the second heat exchanger 8 via the first expansion valve 7.

[0128] The inlet of the low-pressure side heat exchange channel in the second internal heat exchanger 25 is connected to the outlet of the second heat exchanger 8, and the outlet of the low-pressure side heat exchange channel in the second internal heat exchanger 25 is connected in parallel with the second check valve 9 and the second shut-off valve 12 via connection point 22. At the same time, the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel in the second internal heat exchanger 25 can exchange heat.

[0129] It should be pointed out that, regardless of Figure 3 The thermal management system shown is still Figure 4 The thermal management system shown herein, by further providing the aforementioned second internal heat exchanger 25 in the thermal management system, enables the refrigerant to better exchange heat with the air flowing through the vehicle air conditioning unit in the second heat exchanger 8 by utilizing the heat exchange in the second internal heat exchanger 25 located before the second heat exchanger 8, thereby meeting the cooling performance requirements of the thermal management system.

[0130] In specific implementation, as a preferred embodiment, the first internal heat exchanger 6 and the second internal heat exchanger 25, or either of them, can be a coaxial tube. Using a coaxial tube not only ensures the heat exchange effect of the refrigerant within it, but also offers advantages such as simple structure, small space occupation, and ease of arrangement.

[0131] In addition, specifically, when the first internal heat exchanger 6 adopts a coaxial tube, this embodiment uses a high-pressure liquid storage dryer 5 in conjunction with the first internal heat exchanger 6 with a coaxial tube structure to replace the conventional gas-liquid separator form to ensure superheat, and the cooling and heating share a coaxial tube, which can also reduce system costs and help reduce the overall vehicle cost.

[0132] In this embodiment, as a preferred implementation, refer to Figure 5 or Figure 6 As shown, all valves in the refrigerant circuit described above, namely the first shut-off valve 2, the first check valve 4, the first expansion valve 7, the second check valve 9, the third check valve 11, the second shut-off valve 12, the third shut-off valve 13, the fourth shut-off valve 14, the second expansion valve 16, and the third expansion valve 18, as well as each of the two-fluid heat exchangers (the first two-fluid heat exchanger 17 and the second two-fluid heat exchanger 15), the high-pressure liquid receiver-dryer 5, and each of the internal heat exchangers (the first internal heat exchanger 6, which is included when the second internal heat exchanger 25 is provided), at least one of them can be integrated and arranged together.

[0133] At this point, all valves, as well as at least one of the two-fluid heat exchangers, the high-pressure liquid storage dryer 5, and the internal heat exchangers, are integrated together. For example, the housings of the valves, the two-fluid heat exchangers, the high-pressure liquid storage dryer 5, and the internal heat exchangers can be connected as a single integrated structure. Alternatively, a common mounting platform can be provided, and the valves, the two-fluid heat exchangers, the high-pressure liquid storage dryer 5, and the internal heat exchangers can be integrated and mounted on the mounting platform to form a single integrated component 100.

[0134] By integrating at least one of the dual-fluid heat exchangers, the high-pressure liquid receiver-dryer 5, and the internal heat exchangers together, it is understood that this reduces the number of parts, decreases the system space occupied, and facilitates the overall layout of the heat pump air conditioning system in the vehicle.

[0135] In this embodiment, it is still based on Figure 1Taking the thermal management system shown as an example, through the compressor 1, high-pressure liquid storage dryer 5, internal heat exchanger, and the setting of each heat exchanger and dual-fluid heat exchanger, and through the control connection of multiple control valves, the thermal management system can, for example, operate in single air conditioning cooling mode, single battery cooling mode, dual cooling mode, heat pump mode, waste heat recovery mode, heat pump + heat recovery mode, first dehumidification mode and second dehumidification mode.

[0136] In detail, such as Figure 7 As shown, when the thermal management system in this embodiment is in single air conditioning cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first heat exchanger 3 through the first shut-off valve 2, and the refrigerant transfers its enthalpy value to the outside air at the first heat exchanger 3 and becomes liquid.

[0137] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 through the first check valve 4, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve 7, and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger 8 to cool the gas inside the air conditioning unit and obtain enthalpy.

[0138] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger 6 through the second check valve 9, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0139] Figure 8 The diagram shows the changes in pressure and enthalpy experienced by the refrigerant fluid during single air conditioning cooling mode, where curve X represents the refrigerant fluid saturation state.

[0140] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as shown by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the first heat exchanger 3 and transfers its enthalpy to the external airflow, as shown by arrow 300. The refrigerant exiting the first heat exchanger 3 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6, where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0141] Next, the high-pressure refrigerant passes through the first expansion valve 7, where it experiences an isenthalpic pressure drop as indicated by arrow 700 and crosses the saturation curve X. This causes it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant then passes through the second heat exchanger 8, where it gains enthalpy, as shown in 800, while simultaneously cooling the airflow inside the air conditioning unit. The low-pressure refrigerant then passes through the first internal heat exchanger 6, where it gains enthalpy from the high-pressure refrigerant passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X. This causes it to switch to a gaseous state, and the low-pressure refrigerant then returns to the compressor 1.

[0142] like Figure 9 As shown, when the thermal management system in this embodiment is in single-cell cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first heat exchanger 3 through the first shut-off valve 2, and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger 3 and becomes liquid.

[0143] Next, the refrigerant enters the high-pressure liquid storage dryer 5 through the first check valve 4, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve 18, and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first two-fluid heat exchanger 17 to cool the battery pack coolant flowing through the first two-fluid heat exchanger 17 and obtain enthalpy.

[0144] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger 6, obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0145] Figure 10 The changes in pressure and enthalpy experienced by the refrigerant fluid during single-cell cooling mode are shown, where curve X represents the refrigerant fluid saturation state.

[0146] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it is compressed, as shown by arrow 100, at which point it is under high pressure. Then, the high-pressure refrigerant fluid enters the first heat exchanger 3 and transfers its enthalpy to the external airflow, as shown by arrow 300. The refrigerant exiting the first heat exchanger 3 is in a pure liquid state, and then enters the first internal heat exchanger 6 where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0147] Next, the high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 1800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first two-fluid heat exchanger 17, where it gains enthalpy, as indicated by arrow 1700, while simultaneously cooling the heat transfer fluid. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it gains enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0148] like Figure 11 As shown, when the thermal management system in this embodiment is in dual cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first heat exchanger 3 through the first shut-off valve 2, and the refrigerant transfers its enthalpy value to the outside air at the first heat exchanger 3 and becomes liquid.

[0149] Next, the refrigerant enters the high-pressure liquid storage dryer 5 through the first check valve 4, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is split, with one path passing through the third expansion valve 18. The high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the first two-fluid heat exchanger 17 to cool the battery pack coolant flowing through the first two-fluid heat exchanger 17 and obtain enthalpy.

[0150] Another refrigerant passes through the first expansion valve 7. The high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger 8 to cool the gas inside the air conditioning unit and obtain enthalpy.

[0151] Next, the refrigerant passing through the second check valve 9 merges with the refrigerant passing through the first dual-fluid heat exchanger 17 and enters the low-pressure side heat exchange channel in the first internal heat exchanger 6. It obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0152] Figure 12 The changes in pressure and enthalpy experienced by the refrigerant fluid during dual cooling modes are shown, where curve X represents the refrigerant fluid saturation state.

[0153] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as shown by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the first heat exchanger 3 and transfers its enthalpy to the external airflow, as shown by arrow 300. The refrigerant exiting the first heat exchanger 3 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6, where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0154] Next, the high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 1700, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. Then, the low-pressure refrigerant fluid passes through the first two-fluid heat exchanger 17, where it acquires enthalpy, as shown in 1700. The high-pressure refrigerant then passes through the first expansion valve 7. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure.

[0155] Another low-pressure refrigerant fluid passes through the second heat exchanger 8, where it acquires enthalpy, as shown in 800, while simultaneously cooling the airflow inside the air conditioning unit. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it acquires enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as shown by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0156] like Figure 13 As shown, when the thermal management system in this embodiment is in heat pump mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the third heat exchanger 10 through the third shut-off valve 13 and heats the air in the air conditioning unit at the third heat exchanger 10 to lose enthalpy.

[0157] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 after passing through the third check valve 11, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, where the enthalpy is transferred to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve 16, where it experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Finally, the low-pressure refrigerant enters the first heat exchanger 3 to absorb heat from the outside air and obtain enthalpy.

[0158] Next, the refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger (6) through the second shut-off valve 12 and the second check valve 9. The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0159] Figure 14 The changes in pressure and enthalpy experienced by the refrigerant fluid during heat pump mode are shown, where curve X represents the refrigerant fluid saturation state.

[0160] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as shown by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the third heat exchanger 10 and transfers its enthalpy to the cockpit, heating it, as shown by arrow 1000. The refrigerant flowing out of the third heat exchanger 10 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6 where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0161] Next, the high-pressure refrigerant passes through the third expansion valve 16. The high-pressure refrigerant fluid undergoes an isenthalpic pressure drop, as indicated by arrow 1600, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first heat exchanger 3, where it acquires enthalpy, as indicated by arrow 300. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it acquires enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0162] like Figure 15 As shown, when the thermal management system in this embodiment is in waste heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the third heat exchanger 10 through the third shut-off valve 13 and heats the air in the air conditioning unit at the third heat exchanger 10 to lose enthalpy.

[0163] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 through the third check valve 11, then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant enters the third expansion valve 18, where it experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture.

[0164] Then, the low-pressure refrigerant passes through the first dual-fluid heat exchanger 17, absorbs heat from the coolant of the drive motor, and obtains enthalpy. Next, the refrigerant passes through the low-pressure side heat exchange channel in the first internal heat exchanger 6, obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel, and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0165] Figure 16 The changes in pressure and enthalpy experienced by the refrigerant fluid during the waste heat recovery mode are shown, where curve X represents the refrigerant fluid saturation state.

[0166] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as indicated by arrow 100, at which point it is under high pressure. The high-pressure refrigerant fluid then enters the third heat exchanger 10 and transfers its enthalpy to the cockpit to heat it, as indicated by arrow 1000. The refrigerant exiting the third heat exchanger 10 is in a pure liquid state, and then enters the first internal heat exchanger 6 where it loses its enthalpy, as indicated by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as indicated by arrow 600b.

[0167] Next, the high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid undergoes an isenthalpic pressure drop, as indicated by arrow 1800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first dual-fluid heat exchanger 17, where it gains enthalpy from the heat generated by the drive motor, as shown in 1700. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it gains enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0168] like Figure 17 As shown, when the thermal management system in this embodiment is in heat pump + heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the third heat exchanger 10 through the third shut-off valve 13 and heats the air in the air conditioning unit at the third heat exchanger 10 to lose enthalpy.

[0169] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 through the third check valve 11, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, transferring the enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is divided into two paths. One path of the refrigerant passes through the second expansion valve 16, where the refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the first heat exchanger 3 to absorb heat from the outside air and obtain enthalpy, and then passes through the second shut-off valve 12 to enter the second check valve 9.

[0170] Another refrigerant passes through the third expansion valve 18, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first dual-fluid heat exchanger 17 to absorb heat from the coolant of the drive motor and obtain enthalpy.

[0171] Next, after the two refrigerants pass through the second check valve 9 and the first dual-fluid heat exchanger 17, they merge and enter the low-pressure side heat exchange channel in the first internal heat exchanger 6. They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0172] Figure 18 The changes in pressure and enthalpy experienced by the refrigerant fluid during the heat pump + waste heat recovery mode are shown, where curve X represents the refrigerant fluid saturation state.

[0173] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the third heat exchanger 10 and transfers its enthalpy to the cockpit, as indicated by arrow 1000. The refrigerant flowing out of the third heat exchanger 10 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6 where it loses its enthalpy, as indicated by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as indicated by arrow 600b.

[0174] Next, the high-pressure refrigerant flows through the third expansion valve 18. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 1800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then flows through the first two-fluid heat exchanger 17, where it gains enthalpy from the heat generated by the drive motor, as shown in 1700.

[0175] Another high-pressure refrigerant stream passes through the second expansion valve 16. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 1600, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first heat exchanger 3, where it acquires the enthalpy of the outside air, as shown in 300. The merged low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it acquires the enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0176] like Figure 19 As shown, when the thermal management system is in the first dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the third heat exchanger 10 through the third shut-off valve 13 and heats the air in the air conditioning unit at the third heat exchanger 10 to lose enthalpy.

[0177] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 through the third check valve 11, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve 7, undergoes an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger 8 to dehumidify the vehicle interior and obtain enthalpy.

[0178] Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger 6 through the second check valve 9, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0179] Figure 20 The changes in pressure and enthalpy experienced by the refrigerant fluid during the first dehumidification mode are shown, where curve X represents the refrigerant fluid saturation state.

[0180] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as shown by arrow 100, at which point it is under high pressure. Then, the high-pressure refrigerant fluid enters the third heat exchanger 10 and transfers its enthalpy to the air in the air conditioning unit, as shown by arrow 1000. The refrigerant exiting the third heat exchanger 10 is in a pure liquid state, and then enters the first internal heat exchanger 6 where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0181] Next, the high-pressure refrigerant passes through the first expansion valve 7. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 700, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the second heat exchanger 8, where it gains enthalpy for cooling and dehumidification, as shown in 800. The refrigerant then passes through the first internal heat exchanger 6, where it gains enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0182] like Figure 21 As shown, when the thermal management system in this embodiment is in the second dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the third heat exchanger 10 through the third shut-off valve 13 and heats the air in the air conditioning unit at the third heat exchanger 10 to lose enthalpy.

[0183] Next, the refrigerant enters the high-pressure liquid receiver-dryer 5 through the third check valve 11, and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger 6, transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is divided into two paths. One path of refrigerant passes through the first expansion valve 7, where the refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the second heat exchanger 8 to dehumidify the vehicle interior and obtain enthalpy.

[0184] Another refrigerant passes through the second expansion valve 16, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first heat exchanger 3, where it absorbs heat from the outside air to obtain enthalpy.

[0185] Next, after the two refrigerants pass through the second shut-off valve 12 and the second heat exchanger 8, they merge and then enter the low-pressure side heat exchange channel in the first internal heat exchanger 6 through the second check valve 9. They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0186] Figure 22 The changes in pressure and enthalpy experienced by the refrigerant fluid during the second dehumidification mode are shown, where curve X represents the refrigerant fluid saturation state.

[0187] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as shown by arrow 100, at which point it is under high pressure. Then, the high-pressure refrigerant fluid enters the third heat exchanger 10 and transfers its enthalpy to the air inside the air conditioning unit, as shown by arrow 1000. The refrigerant flowing out of the first heat exchanger 10 is in a pure liquid state, and then enters the first internal heat exchanger 6 where it loses its enthalpy, as shown by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as shown by arrow 600b.

[0188] Next, the high-pressure refrigerant flows through the first expansion valve 7. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 700, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the second heat exchanger 8, where it gains enthalpy for cooling and dehumidification, as shown in 800.

[0189] Another path of high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid undergoes an isenthalpic pressure drop, as indicated by arrow 1800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first dual-fluid heat exchanger 17, where it acquires the enthalpy needed to drive the motor, as indicated by 1700. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it acquires the enthalpy, as indicated by arrow 600b, from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6 and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0190] In addition, with Figure 2 Taking the thermal management system shown in the figure as an example, by further setting the second dual-fluid heat exchanger 15, the thermal management system of this embodiment can operate in, for example, heat pump heating battery mode, motor waste heat heating battery mode, and motor waste heat + heat pump heating battery mode.

[0191] At this point, specifically, such as Figure 23 As shown, when the thermal management system of this embodiment is in the heat pump heating battery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger 15 through the fourth shut-off valve 14 to heat the battery and lose enthalpy.

[0192] Next, the refrigerant enters the high-pressure side heat exchange channel of the first internal heat exchanger 6 through the high-pressure liquid receiver-dryer 5, and transfers its enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve 16, undergoes an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the first heat exchanger 3 and absorbs heat from the outside air to obtain enthalpy.

[0193] Next, the refrigerant enters the low-pressure side heat exchange channel of the first internal heat exchanger 6 through the second shut-off valve 12 and the second check valve 9. The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0194] Figure 24 The changes in pressure and enthalpy experienced by the refrigerant fluid during heat pump heating battery mode are shown, where curve X represents the refrigerant fluid saturation state.

[0195] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the second two-fluid heat exchanger 15 and transfers its enthalpy to the coolant to heat the battery, as indicated by arrow 1500. The refrigerant exiting the second two-fluid heat exchanger 15 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6 where it loses its enthalpy, as indicated by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as indicated by arrow 600b.

[0196] Next, the high-pressure refrigerant passes through the second expansion valve 16. The high-pressure refrigerant fluid undergoes an isenthalpic pressure drop, as indicated by arrow 1600, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first heat exchanger 3, where it acquires the enthalpy of the outside air, as shown in 300. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it acquires the enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0197] like Figure 25 As shown in the figure, when the thermal management system of this embodiment is in the mode of heating the battery with the waste heat of the motor, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger 15 through the fourth shut-off valve 14 to heat the battery and lose enthalpy.

[0198] Next, the refrigerant passes through the high-pressure liquid storage dryer 5 and enters the high-pressure side heat exchange channel of the first internal heat exchanger 6, transferring its enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve 18, experiences an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the second dual-fluid heat exchanger 17 to absorb heat from the drive motor and obtain enthalpy.

[0199] Next, the refrigerant passes through the low-pressure side heat exchange channel in the first internal heat exchanger 6, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0200] Figure 26 The changes in pressure and enthalpy experienced by the refrigerant fluid during the motor waste heat heating battery mode are shown, where curve X represents the refrigerant fluid saturation state.

[0201] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the second two-fluid heat exchanger 15 and transfers its enthalpy to the coolant to heat the battery, as indicated by arrow 1500. The refrigerant exiting the second two-fluid heat exchanger 15 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6 where it loses its enthalpy, as indicated by arrow 600a, which is then transferred to the low-pressure refrigerant fluid, as indicated by arrow 600b.

[0202] Next, the high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid undergoes an isenthalpic pressure drop, as indicated by arrow 1800, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the second dual-fluid heat exchanger 17, where it receives enthalpy from the drive motor, as indicated by 1700. The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it receives enthalpy from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6, as indicated by arrow 600b, and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0203] like Figure 27 As shown in the figure, when the thermal management system of this embodiment is in the mode of motor waste heat + heat pump heating battery, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger 15 through the fourth shut-off valve 14 to heat the battery and lose enthalpy.

[0204] Next, the refrigerant passes through the high-pressure liquid storage dryer 5 and enters the high-pressure side heat exchange channel of the first internal heat exchanger 6, where the enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange channel. The refrigerant is divided into two paths. One path of the refrigerant passes through the third expansion valve 18, where the refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second dual-fluid heat exchanger 17, where it absorbs heat from the drive motor to obtain enthalpy.

[0205] Another refrigerant passes through the second expansion valve 16, where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. The low-pressure refrigerant then enters the first heat exchanger 3 to absorb heat from the outside air and obtain enthalpy, before passing through the second check valve 12 and entering the second check valve 9.

[0206] Next, after the two refrigerants pass through the second check valve 9 and the second dual-fluid heat exchanger 17, they merge and enter the low-pressure side heat exchange channel of the first internal heat exchanger 6. They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor 1.

[0207] Figure 28 The changes in pressure and enthalpy experienced by the refrigerant fluid during the motor waste heat + heat pump heating battery mode are shown, where curve X represents the refrigerant fluid saturation state.

[0208] Specifically, the refrigerant fluid entering compressor 1 is in the gas phase. As the refrigerant fluid passes through compressor 1, it undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at high pressure. Then, the high-pressure refrigerant fluid enters the second two-fluid heat exchanger 15, transferring its enthalpy to the coolant to heat the battery, as indicated by arrow 150. The refrigerant exiting the second two-fluid heat exchanger 15 is in a pure liquid state, and then the refrigerant fluid enters the first internal heat exchanger 6, where it loses its enthalpy, as indicated by arrow 600a, which is transferred to the low-pressure refrigerant fluid, as indicated by arrow 600b.

[0209] Next, one stream of high-pressure refrigerant passes through the third expansion valve 18. The high-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 180, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first fluid heat exchanger 17, where it gains enthalpy from the drive motor, as shown in 170. The other stream of high-pressure refrigerant passes through the second expansion valve 16. The low-pressure refrigerant fluid experiences an isenthalpic pressure drop, as indicated by arrow 1600, and crosses the saturation curve X, causing it to switch to a gas-liquid mixture state and be at low pressure. The low-pressure refrigerant fluid then passes through the first heat exchanger 3, where it gains enthalpy from the outside air, as shown in 300.

[0210] The low-pressure refrigerant fluid then passes through the first internal heat exchanger 6, where it gains enthalpy (as indicated by arrow 600b) from the high-pressure refrigerant fluid passing through the first internal heat exchanger 6 and crosses the saturation curve X, causing its temperature to rise and its enthalpy value to increase. The low-pressure refrigerant fluid then returns to the compressor 1.

[0211] Example 2

[0212] This embodiment relates to a vehicle, which is a new energy vehicle, and the vehicle is equipped with the thermal management system for new energy vehicles as described in Embodiment 1.

[0213] As mentioned in Embodiment 1, the new energy vehicle in this embodiment can be one of pure electric vehicle, hybrid vehicle, or fuel cell vehicle. Meanwhile, the arrangement of the above-mentioned thermal management system in the vehicle can refer to the setting method of relevant components in existing new energy vehicles.

[0214] Moreover, the vehicle in this embodiment, by setting the thermal management system in Embodiment 1, has a relatively simple structure. At the same time, based on the heat pump mode, it can also realize single cooling, dual cooling, as well as multiple working modes such as waste heat recovery, heat pump + heat recovery and dehumidification, which is conducive to the promotion and application of heat pump management system.

[0215] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A thermal management system for new energy vehicles, characterized in that: The refrigerant circuit of the thermal management system includes a compressor (1), a first heat exchanger (3), a high-pressure liquid receiver-dryer (5), a first internal heat exchanger (6), a second heat exchanger (8), a third heat exchanger (10), and a first dual-fluid heat exchanger (17). One end of the first heat exchanger (3) is connected to the outlet of the compressor (1) through the first shut-off valve (2), and the other end of the first heat exchanger (3) is connected in parallel with the first check valve (4) and the second expansion valve (16). The first check valve (4) is connected to the inlet of the high-pressure liquid storage dryer (5), and the second expansion valve (16) is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger (6). The inlet of the second heat exchanger (8) is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger (6) through the first expansion valve (7). The outlet of the second heat exchanger (8) is connected in parallel with a second check valve (9) and a second shut-off valve (12). The second check valve (9) is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger (6). The second shut-off valve (12) is connected in parallel with the first shut-off valve (2) at the same end of the first heat exchanger (3). One end of the third heat exchanger (10) is connected to the outlet of the compressor (1) through the third shut-off valve (13), and the other end of the third heat exchanger (10) is connected to the inlet of the high-pressure liquid storage dryer (5) through the third check valve (11). The outlet of the high-pressure liquid storage dryer (5) is connected to the inlet of the high-pressure side heat exchange channel in the first internal heat exchanger (6), and the outlet of the low-pressure side heat exchange channel in the first internal heat exchanger (6) is connected to the inlet of the compressor (1). One end of the first dual-fluid heat exchanger (17) is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger (6) through the third expansion valve (18), and the other end of the first dual-fluid heat exchanger (17) is connected to the inlet of the low-pressure side heat exchange channel in the first internal heat exchanger (6). The refrigerant in the first heat exchanger (3) is reversible and can be used as an evaporator or condenser. The refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the first internal heat exchanger (6) can exchange heat.

2. The thermal management system for new energy vehicles according to claim 1, characterized in that: The coolant passage in the first dual-fluid heat exchanger (17) is connected to the cooling passage in the battery pack and the cooling passage in the drive motor.

3. The thermal management system for new energy vehicles according to claim 1, characterized in that: The refrigerant circuit also includes a second two-fluid heat exchanger (15). One end of the second dual-fluid heat exchanger (15) is connected to the outlet of the compressor (1) through the fourth shut-off valve (14), and the other end of the second dual-fluid heat exchanger (15) is connected to the inlet of the high-pressure liquid storage dryer (5).

4. The thermal management system for new energy vehicles according to claim 1 or 3, characterized in that: The refrigerant circuit also includes a second internal heat exchanger (25). The inlet of the high-pressure side heat exchange channel in the second internal heat exchanger (25) is connected to the outlet of the high-pressure side heat exchange channel in the first internal heat exchanger (6), and the outlet of the high-pressure side heat exchange channel in the second internal heat exchanger (25) is connected to the inlet of the second heat exchanger (8) through the first expansion valve (7). The inlet of the low-pressure side heat exchange channel in the second internal heat exchanger (25) is connected to the outlet of the second heat exchanger (8), and the outlet of the low-pressure side heat exchange channel in the second internal heat exchanger (25) is connected in parallel to the second check valve (9) and the second shut-off valve (12). The refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel of the second internal heat exchanger (25) can exchange heat.

5. The thermal management system for new energy vehicles according to claim 4, characterized in that: The first internal heat exchanger (6) and / or the second internal heat exchanger (25) are coaxial tubes.

6. The thermal management system for new energy vehicles according to claim 3, characterized in that: All valves in the refrigerant circuit, as well as at least one of the two-fluid heat exchangers, high-pressure liquid receiver-dryer, and internal heat exchangers, are integrated and arranged together.

7. The thermal management system for new energy vehicles according to claim 1, characterized in that: The thermal management system has a single air conditioning cooling mode; When the thermal management system is in the single air conditioning cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first heat exchanger (3) through the first shut-off valve (2), and the refrigerant transfers its enthalpy value to the outside air at the first heat exchanger (3) and becomes liquid. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the first check valve (4), then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6), and transfers the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve (7), and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger (8) to cool the gas inside the air conditioning unit and obtain enthalpy. Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger (6) through the second check valve (9), and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

8. The thermal management system for new energy vehicles according to claim 2, characterized in that: The thermal management system has a single-battery cooling mode; When the thermal management system is in the single-cell cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first heat exchanger (3) through the first shut-off valve (2), and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger (3) and becomes liquid. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the first check valve (4), then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6), and transfers the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve (18), and the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first dual-fluid heat exchanger (17) to cool the battery pack coolant flowing through the first dual-fluid heat exchanger (17) and obtain enthalpy. Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger (6), obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor (1).

9. The thermal management system for new energy vehicles according to claim 2, characterized in that: The thermal management system has dual cooling modes; When the thermal management system is in the dual cooling mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first heat exchanger (3) through the first shut-off valve (2), and the refrigerant transfers its enthalpy to the outside air at the first heat exchanger (3) and becomes liquid. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the first check valve (4), and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6) to transfer the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is split, and one refrigerant passes through the third expansion valve (18). The high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the first dual-fluid heat exchanger (17) to cool the battery pack coolant flowing through the first dual-fluid heat exchanger (17) and obtain enthalpy. Another refrigerant passes through the first expansion valve (7), where the high-pressure refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve to become a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger (8) to cool the gas inside the air conditioning unit and obtain enthalpy. Next, the refrigerant passing through the second check valve (9) merges with the refrigerant passing through the first dual-fluid heat exchanger (17) and enters the low-pressure side heat exchange channel in the first internal heat exchanger (6). It obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

10. The thermal management system for new energy vehicles according to claim 1, characterized in that: The thermal management system has a heat pump mode; When the thermal management system is in the heat pump mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the third heat exchanger (10) through the third shut-off valve (13) and heats the air in the air conditioning unit at the third heat exchanger (10) to lose enthalpy. Next, the refrigerant enters the high-pressure liquid storage dryer (5) after passing through the third check valve (11), and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6), transferring the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve (16), and the refrigerant experiences an isoenthalpy pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first heat exchanger (3) to absorb heat from the outside air and obtain enthalpy. Next, the refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger (6) through the second shut-off valve (12) and the second check valve (9). The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

11. The thermal management system for new energy vehicles according to claim 2, characterized in that: The thermal management system has a waste heat recovery mode; When the thermal management system is in the waste heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the third heat exchanger (10) through the third shut-off valve (13) and heats the air in the air conditioning unit at the third heat exchanger (10) to lose enthalpy. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the third check valve (11), then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6), and transfers its enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant enters the third expansion valve (18), and the refrigerant experiences an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the first dual-fluid heat exchanger (17), absorbs heat from the coolant of the drive motor to obtain enthalpy, and then passes through the low-pressure side heat exchange channel in the first internal heat exchanger (6), obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor (1).

12. The thermal management system for new energy vehicles according to claim 2, characterized in that: The thermal management system has a heat pump + heat recovery mode; When the thermal management system is in the heat pump + heat recovery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the third heat exchanger (10) through the third shut-off valve (13) and heats the air in the air conditioning unit at the third heat exchanger (10) to lose enthalpy. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the third check valve (11), and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6) to transfer the enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is divided into two paths. One path of the refrigerant passes through the second expansion valve (16), where the refrigerant experiences an isoenthalpy pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the first heat exchanger (3) to absorb heat from the outside air to obtain enthalpy, and then passes through the second shut-off valve (12) to enter the second check valve (9). Another refrigerant passes through the third expansion valve (18), where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first dual-fluid heat exchanger (17) to absorb heat from the coolant of the drive motor and obtain enthalpy. Next, after the two refrigerants pass through the second check valve (9) and the first dual-fluid heat exchanger (17), they merge and enter the low-pressure side heat exchange channel in the first internal heat exchanger (6). They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

13. The thermal management system for new energy vehicles according to claim 1, characterized in that: The thermal management system has a first dehumidification mode; When the thermal management system is in the first dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the third heat exchanger (10) through the third shut-off valve (13) and heats the air in the air conditioning unit at the third heat exchanger (10) to lose enthalpy. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the third check valve (11), and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6) to transfer the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the first expansion valve (7), and the refrigerant experiences an isoenthalpy pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second heat exchanger (8) to dehumidify the vehicle interior and obtain enthalpy. Next, the low-pressure refrigerant enters the low-pressure side heat exchange channel in the first internal heat exchanger (6) through the second check valve (9), and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

14. The thermal management system for new energy vehicles according to claim 1, characterized in that: The thermal management system has a second dehumidification mode; When the thermal management system is in the second dehumidification mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the third heat exchanger (10) through the third shut-off valve (13) and heats the air in the air conditioning unit at the third heat exchanger (10) to lose enthalpy. Next, the refrigerant enters the high-pressure liquid storage dryer (5) through the third check valve (11), and then passes through the high-pressure side heat exchange channel in the first internal heat exchanger (6) to transfer the enthalpy to the refrigerant in the low-pressure side heat exchange channel. Then the refrigerant is divided into two paths. One path of the refrigerant passes through the first expansion valve (7), and the refrigerant experiences an isoenthalpy pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then the low-pressure refrigerant enters the second heat exchanger (8) to dehumidify the vehicle interior and obtain enthalpy. Another refrigerant passes through the second expansion valve (16), where it experiences an isenthalpic pressure drop and crosses the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first heat exchanger (3) and absorbs heat from the outside air to obtain enthalpy. Next, the two refrigerants, after passing through the second shut-off valve (12) and the second heat exchanger (8), merge and then enter the low-pressure side heat exchange channel in the first internal heat exchanger (6) through the second check valve (9). They obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

15. The thermal management system for new energy vehicles according to claim 3, characterized in that: The thermal management system has a heat pump heating battery mode; When the thermal management system is in the heat pump heating battery mode, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger (17) through the fourth shut-off valve (14) to heat the battery and lose enthalpy. Next, the refrigerant enters the high-pressure side heat exchange channel of the first internal heat exchanger (6) through the high-pressure liquid storage dryer (5), and transfers its enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the second expansion valve (16), experiences an isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the first heat exchanger (3) and absorbs heat from the outside air to obtain enthalpy. Next, the refrigerant enters the low-pressure side heat exchange channel of the first internal heat exchanger (6) through the second shut-off valve (12) and the second check valve (9). The refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

16. The thermal management system for new energy vehicles according to claim 3, characterized in that: The thermal management system has a mode for heating the battery with waste heat from the motor. When the thermal management system is in the mode of heating the battery with the waste heat of the motor, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger (17) through the fourth shut-off valve (14) to heat the battery and lose enthalpy. Next, the refrigerant passes through the high-pressure liquid storage dryer (5) and enters the high-pressure side heat exchange channel of the first internal heat exchanger (6), transferring enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. Then, the refrigerant passes through the third expansion valve (18), undergoes an isenthalpy pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant passes through the second dual-fluid heat exchanger (15) to absorb heat from the drive motor and obtain enthalpy. Next, the refrigerant passes through the low-pressure side heat exchange channel in the first internal heat exchanger (6), and obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

17. The thermal management system for new energy vehicles according to claim 3, characterized in that: The thermal management system has a mode of motor waste heat + heat pump heating battery. When the thermal management system is in the mode of motor waste heat + heat pump heating battery, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor (1) and is under high pressure. The high-pressure refrigerant enters the first dual-fluid heat exchanger (17) through the fourth shut-off valve (14) to heat the battery and lose enthalpy. Next, the refrigerant passes through the high-pressure liquid storage dryer (5) and enters the high-pressure side heat exchange channel of the first internal heat exchanger (6), transferring the enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channel. The refrigerant is divided into two paths. One path of the refrigerant passes through the third expansion valve (18), where the refrigerant experiences an isoenthalpy pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the second dual-fluid heat exchanger (15) and absorbs heat from the drive motor to obtain enthalpy. Another refrigerant passes through the second expansion valve (16), where it experiences an isenthalpic pressure drop and passes through the saturation curve, becoming a low-pressure gas-liquid mixture. Then, the low-pressure refrigerant enters the first heat exchanger (3) to absorb heat from the outside air and obtain enthalpy. It then passes through the second shut-off valve (12) and enters the second check valve (9). Next, after the two refrigerants pass through the second check valve (9) and the second dual-fluid heat exchanger (15), they enter the low-pressure side heat exchange channel of the first internal heat exchanger (6) and obtain enthalpy from the refrigerant in the high-pressure side heat exchange channel and pass through the saturation curve, causing the refrigerant to become gaseous. Finally, the low-pressure refrigerant returns to the compressor (1).

18. A vehicle, characterized in that: The vehicle is a new energy vehicle, and the vehicle is equipped with a thermal management system for new energy vehicles as described in any one of claims 1 to 17.

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