Heat pump air-conditioning system and vehicle

Abstract

The present disclosure relates to a heat pump air conditioning system and a vehicle. The heat pump air conditioning system includes a compressor, an outdoor heat exchanger, a first heat exchanger, a first expansion valve, and an indoor evaporator. The outlet of the compressor is connected to the inlet of the outdoor heat exchanger. The outlet of the outdoor heat exchanger is connected to the first refrigerant inlet of the first heat exchanger. The first refrigerant outlet of the first heat exchanger is connected to the inlet of the indoor evaporator via the first expansion valve. The outlet of the indoor evaporator is connected to the second refrigerant inlet of the first heat exchanger. The second refrigerant outlet of the first heat exchanger is connected to the inlet of the compressor. By providing the first heat exchanger and enabling the refrigerant to release heat twice in the outdoor heat exchanger and the first heat exchanger in the cooling mode, the supercooling degree of the refrigerant entering the indoor evaporator is increased, thereby solving the problem that the amount of heat released by the refrigerant in the outdoor heat exchanger is limited in a high-temperature environment.

Description

Technical Field

[0001] The present disclosure relates to the technical field of heat pump air conditioning systems, and more particularly, to a heat pump air conditioning system and a vehicle. Background Art

[0002] In the refrigeration condition of the existing vehicle heat pump air conditioning system, the high-temperature and high-pressure gaseous refrigerant discharged by the compressor releases heat to the external atmosphere at the outdoor heat exchanger. After the refrigerant releases heat, it passes through the throttle valve to reduce the pressure and absorb the heat of the passenger compartment in the indoor evaporator, thereby achieving the effect of cooling the passenger compartment. Since the refrigerant needs to release heat to the external atmosphere through the outdoor heat exchanger before entering the evaporator, the heat exchange amount between the refrigerant and the external atmosphere in the outdoor heat exchanger is affected by the ambient temperature. For example, when the external ambient temperature is relatively high, the amount of heat released by the refrigerant to the external atmosphere in the outdoor heat exchanger is limited, which will affect the refrigeration effect and efficiency of the vehicle heat pump air conditioning system.

[0003] In addition, in the existing vehicle heat pump air conditioning system, the outdoor heat exchanger is used as a condenser in the refrigeration condition and as an evaporator in the heating condition. That is to say, whether in the refrigeration condition or the heating condition, the refrigerant will flow through the outdoor heat exchanger, and the flow path of the refrigerant when absorbing heat (condensing) or releasing heat (evaporating) in the outdoor heat exchanger is the same. Since condensation and evaporation are two reverse physical processes, the same flow path will limit the heat exchange performance of the refrigerant when condensing in the outdoor heat exchanger, affecting the refrigeration effect and efficiency of the vehicle heat pump air conditioning system. Summary of the Invention

[0004] The purpose of the present disclosure is to provide a heat pump air conditioning system and a vehicle using the heat pump air conditioning system to overcome the problems existing in the related art.

[0005] To achieve the above object, the present disclosure provides a heat pump air conditioning system, including a compressor, an outdoor heat exchanger, a first heat exchanger, a first expansion valve, and an indoor evaporator.

[0006] The outlet of the compressor is connected to the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger is connected to the first refrigerant inlet of the first heat exchanger, the first refrigerant outlet of the first heat exchanger is connected to the inlet of the indoor evaporator via the first expansion valve, the outlet of the indoor evaporator is connected to the second refrigerant inlet of the first heat exchanger, and the second refrigerant outlet of the first heat exchanger is connected to the inlet of the compressor.

[0007] Optionally, the heat pump air conditioning system further includes a gas-liquid separation device. The outlet of the indoor evaporator is connected to the inlet of the gas-liquid separation device, and the gas outlet of the gas-liquid separation device is connected to the second refrigerant inlet of the first heat exchanger.

[0008] Optionally, the heat pump air conditioning system further includes an indoor condenser, a through-flow path, and a throttling path.

[0009] The outlet of the compressor is connected to the inlet of the through-flow path and the inlet of the indoor condenser. The outlet of the indoor condenser is connected to the inlet of the throttling path. The outlet of the through-flow path and the outlet of the throttling path are connected to the inlet of the outdoor heat exchanger. The outlet of the outdoor heat exchanger is further connected to the inlet of the gas-liquid separation device via a first flow path that can be selectively opened or closed.

[0010] Optionally, the outlet of the compressor is connected to the inlet of the indoor condenser via a second flow path that can be selectively opened or closed.

[0011] Optionally, a first stop valve is provided on the first flow path, a second stop valve is provided on the second flow path, a third stop valve is provided on the through-flow path, and a second expansion valve is provided on the throttling path.

[0012] Optionally, the heat pump air conditioning system further includes an indoor condenser, a through-flow path, and a throttling path.

[0013] The outlet of the compressor is connected to the inlet of the indoor condenser. The outlet of the indoor condenser is selectively connected to the inlet of the outdoor heat exchanger via the through-flow path or the throttling path. The outlet of the outdoor heat exchanger is further connected to the inlet of the gas-liquid separation device via a first flow path that can be selectively opened or closed.

[0014] Optionally, a first stop valve is provided on the first flow path, a third stop valve is provided on the through-flow path, and a second expansion valve is provided on the throttling path; or,

[0015] A first stop valve is provided on the first flow path. The heat pump air conditioning system further includes an expansion switch valve. The outlet of the indoor condenser is connected to the inlet of the outdoor heat exchanger via the expansion switch valve. The through-flow path is the through-flow channel inside the expansion switch valve, and the throttling path is the throttling channel inside the expansion switch valve.

[0016] Optionally, the outlet of the indoor condenser is further connected to the inlet of the first expansion valve via a third flow path that can be selectively opened or closed. The first refrigerant outlet of the first heat exchanger is connected to the inlet of the first expansion valve through a check valve.

[0017] Optionally, the heat pump air conditioning system further includes a second heat exchanger and a third expansion valve. The first refrigerant outlet of the first heat exchanger is further connected to the refrigerant inlet of the second heat exchanger via the third expansion valve. The refrigerant outlet of the second heat exchanger is connected to the inlet of the gas-liquid separation device. The first coolant outlet of the second heat exchanger is used to connect to the inlet of an electronic device of the vehicle, and the first coolant inlet of the second heat exchanger is used to connect to the outlet of the electronic device.

[0018] Optionally, the outlet of the indoor condenser is further connected to the inlet of the first expansion valve and the inlet of the third expansion valve via a third flow path that can be selectively opened or closed. The first refrigerant outlet of the first heat exchanger is connected to the inlet of the first expansion valve and the inlet of the third expansion valve through a one-way valve.

[0019] Optionally, a fourth cut-off valve is provided on the third flow path.

[0020] Optionally, the electronic device includes at least one of a motor, a charger, a motor controller, and a DC-DC converter.

[0021] Optionally, the second coolant outlet of the second heat exchanger is used to connect to the inlet of the battery pack of the vehicle, and the second coolant inlet of the second heat exchanger is used to connect to the outlet of the battery pack.

[0022] According to another aspect of the present disclosure, a vehicle is provided, including the above-mentioned heat pump air conditioning system.

[0023] Through the above technical solution, in the refrigeration mode, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor outlet flows into the outdoor heat exchanger, and dissipates heat to the external atmosphere in the outdoor heat exchanger. The refrigerant loses enthalpy in the outdoor heat exchanger, that is, the enthalpy value decreases. The refrigerant flowing out of the outlet of the outdoor heat exchanger flows into the first heat exchanger through the first refrigerant inlet of the first heat exchanger, and exchanges heat with the refrigerant flowing into the first heat exchanger from the second refrigerant inlet of the first heat exchanger. The refrigerant flowing into the first heat exchanger from the outlet of the outdoor heat exchanger loses enthalpy again, and the enthalpy value further decreases. The enthalpy-lost refrigerant flowing out of the first refrigerant outlet of the first heat exchanger becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and pressure reduction by the first expansion valve. This low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the air in the passenger compartment in the indoor evaporator, reducing the temperature in the passenger compartment and realizing passenger compartment refrigeration. The heat-absorbed refrigerant flowing out of the outlet of the indoor evaporator flows into the first heat exchanger, and obtains the enthalpy lost by the refrigerant flowing into the first heat exchanger from the outlet of the outdoor heat exchanger. The refrigerant flowing out of the second refrigerant outlet of the first heat exchanger finally returns to the compressor.

[0024] Compared with the prior art in which the refrigerant before entering the indoor evaporator only releases heat to the outside world through the outdoor heat exchanger and loses enthalpy, the heat pump air-conditioning system provided by the present disclosure solves the problem that the refrigerant has insufficient heat release due to the influence of the ambient temperature at the outdoor heat exchanger in a high ambient temperature environment by arranging a first heat exchanger, so that the refrigerant flowing out of the outlet of the outdoor heat exchanger exchanges heat with the refrigerant flowing out of the outlet of the indoor evaporator in the first heat exchanger, further dissipating heat and cooling down the refrigerant flowing out of the outlet of the outdoor heat exchanger. That is, the refrigerant can release heat twice through the outdoor heat exchanger and the first heat exchanger before entering the indoor evaporator. In this way, the enthalpy value and the released heat of the refrigerant before entering the indoor evaporator are more, which is beneficial to increasing the subcooling degree of the refrigerant entering the indoor evaporator and to flowing a refrigerant with a lower temperature into the indoor evaporator, so that the vehicle thermal management system provided by the present disclosure can still have good refrigeration effect and refrigeration efficiency in a high-temperature environment, realizing the rapid cooling of the occupant compartment. In other words, by arranging the first heat exchanger and enabling the refrigerant flowing out of the outlet of the outdoor heat exchanger to release heat in the first heat exchanger, the problems that the refrigerant has limited heat release in the outdoor heat exchanger in a high-temperature environment and that the condensation heat transfer performance is affected when the outdoor heat exchanger serves as both a condenser and an evaporator can be solved.

[0025] Other features and advantages of the present disclosure will be described in detail in the subsequent specific implementation section. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The drawings are used to provide a further understanding of the present disclosure, and constitute a part of the specification. They are used to explain the present disclosure together with the following specific implementation, but do not constitute a limitation to the present disclosure. In the drawings:

[0027] Figure 1 is a schematic structural diagram of a heat pump air-conditioning system provided by an embodiment of the present disclosure;

[0028] Figure 2 is a schematic structural diagram of a heat pump air-conditioning system provided by another embodiment of the present disclosure;

[0029] Figure 3 is a schematic structural diagram of a heat pump air-conditioning system provided by still another embodiment of the present disclosure;

[0030] Figure 4 is a schematic structural diagram of a heat pump air-conditioning system provided by yet another embodiment of the present disclosure;

[0031] Figure 5 is a schematic structural diagram of a heat pump air-conditioning system provided by an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a refrigeration mode, and the thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0032] Figure 6 It is the pressure-enthalpy diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the cooling mode;

[0033] Figure 7 It is the schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the cooling and battery pack cooling mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0034] Figure 8 It is the pressure-enthalpy diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the cooling and battery pack cooling mode;

[0035] Figure 9 It is the schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the battery pack cooling mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0036] Figure 10 It is the pressure-enthalpy diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the battery pack cooling mode;

[0037] Figure 11 It is the schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the heat pump heating mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0038] Figure 12 It is the pressure-enthalpy diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the heat pump heating mode;

[0039] Figure 13 It is the schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the waste heat recovery heating mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0040] Figure 14 It is the pressure-enthalpy diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the waste heat recovery heating mode;

[0041] Figure 15 It is the schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the first heat pump with waste heat recovery heating mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0042] Figure 16It is the enthalpy-pressure diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the first heat pump heating mode with waste heat recovery;

[0043] Figure 17 It is a schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the second heat pump heating mode with waste heat recovery. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0044] Figure 18 It is the enthalpy-pressure diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the second heat pump heating mode with waste heat recovery;

[0045] Figure 19 It is a schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the first dehumidification mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0046] Figure 20 It is the enthalpy-pressure diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the first dehumidification mode;

[0047] Figure 21 It is a schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the second dehumidification mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0048] Figure 22 It is the enthalpy-pressure diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the second dehumidification mode;

[0049] Figure 23 It is a schematic structural diagram of the heat pump air-conditioning system provided by an embodiment of the present disclosure. Among them, the heat pump air-conditioning system is in the third dehumidification mode. The thick solid lines and arrows in the figure indicate the flow paths and flow directions of the refrigerant and the coolant in this mode;

[0050] Figure 24 It is the enthalpy-pressure diagram of the refrigerant of the heat pump air-conditioning system provided by an embodiment of the present disclosure in the third dehumidification mode.

[0051] Description of reference numerals

[0052] 1 - Compressor; 2 - Outdoor heat exchanger; 3 - First heat exchanger; 4 - First expansion valve; 5 - Indoor evaporator; 6 - Gas - liquid separation device; 7 - Indoor condenser; 8 - Flow - through flow path; 9 - Throttling flow path; 10 - First flow path; 11 - Second flow path; 12 - First stop valve; 13 - Second stop valve; 14 - Third stop valve; 15 - Second expansion valve; 16 - Expansion switch valve; 17 - Third flow path; 18 - Check valve; 19 - Second heat exchanger; 20 - Third expansion valve; 21 - Fourth stop valve; A - First refrigerant inlet; B - First refrigerant outlet; C - Second refrigerant inlet; D - Second refrigerant outlet. Detailed implementation manners

[0053] The following will describe the detailed implementation manners of the present disclosure with reference to the accompanying drawings. It should be understood that the detailed implementation manners described herein are only for explaining and interpreting the present disclosure, and are not used to limit the present disclosure.

[0054] In the present disclosure, unless otherwise stated, the "connection" mentioned in the present disclosure can be a direct connection between two devices or apparatuses, or an indirect connection. The "throttling flow path" means that this flow path can achieve the throttling and truncation of the refrigerant, and the "flow - through flow path" means that this flow path can achieve the flow - through of the refrigerant (i.e., directly conduct the refrigerant without throttling the refrigerant) and truncation.

[0055] As Figures 1 to 24 shown, the present disclosure provides a heat pump air - conditioning system, which can be used in a vehicle. The heat pump air - conditioning system includes a compressor 1, an outdoor heat exchanger 2, a first heat exchanger 3, a first expansion valve 4, and an indoor evaporator 5. The outlet of the compressor 1 is connected to the inlet of the outdoor heat exchanger 2, the outlet of the outdoor heat exchanger 2 is connected to the first refrigerant inlet A of the first heat exchanger 3, the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the indoor evaporator 5 via the first expansion valve 4, the outlet of the indoor evaporator 5 is connected to the second refrigerant inlet C of the first heat exchanger 3, and the second refrigerant outlet D of the first heat exchanger 3 is connected to the inlet of the compressor 1. That is to say, in the refrigeration mode of the above - mentioned heat pump air - conditioning system, the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 first loses enthalpy in the first heat exchanger 3 and then enters the indoor evaporator 5. By the first heat exchanger 3, the supercooling degree of the refrigerant about to enter the indoor evaporator 5 can be increased, thereby improving the heat absorption capacity of the refrigerant in the indoor evaporator 5.

[0056] Specifically, in the refrigeration mode, as Figure 5 shown, the high - temperature and high - pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the outdoor heat exchanger 2, and dissipates heat to the outside atmosphere in the outdoor heat exchanger 2. The refrigerant loses enthalpy in the outdoor heat exchanger 2, that is, the enthalpy value decreases (as Figure 6as indicated by the arrow 200 in [Figure], the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 through the first refrigerant inlet A of the first heat exchanger 3, and exchanges heat with the refrigerant flowing into the first heat exchanger 3 from the second refrigerant inlet C of the first heat exchanger 3. The refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2 loses enthalpy again, and the enthalpy value further decreases (as Figure 6 indicated by the arrow 300a in [Figure], the enthalpy-lost refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 is throttled and depressurized by the first expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the air in the passenger compartment in the indoor evaporator 5, reducing the temperature in the passenger compartment and realizing passenger compartment refrigeration. The heat-absorbed refrigerant flowing out of the outlet of the indoor evaporator 5 flows into the first heat exchanger 3, and obtains the enthalpy lost by the refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2. The refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 finally returns to the compressor 1.

[0057] Compared with the prior art in which the refrigerant before entering the indoor evaporator only releases heat to the outside and loses enthalpy through the outdoor heat exchanger, the heat pump air-conditioning system provided by the present disclosure solves the problem that the heat release of the refrigerant at the outdoor heat exchanger 2 is insufficient due to the influence of the ambient temperature in a high ambient temperature environment by arranging the first heat exchanger 3, so that the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 exchanges heat with the refrigerant flowing out of the outlet of the indoor evaporator 5 in the first heat exchanger 3, and further dissipates heat and cools down the refrigerant flowing out of the outlet of the outdoor heat exchanger 2. That is, the refrigerant can release heat twice through the outdoor heat exchanger 2 and the first heat exchanger 3 before entering the indoor evaporator 5. In this way, the enthalpy value and the released heat of the refrigerant before entering the indoor evaporator 5 are more, which is beneficial to increasing the subcooling degree of the refrigerant entering the indoor evaporator 5 and is beneficial to the indoor evaporator 5 flowing into a refrigerant with a lower temperature, so that the vehicle thermal management system provided by the present disclosure can still have good refrigeration effect and refrigeration efficiency in a high-temperature environment and realize the rapid cooling of the passenger compartment. In other words, by arranging the first heat exchanger 3 and making the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 release heat in the first heat exchanger 3, the problems that the heat release of the refrigerant in the outdoor heat exchanger 2 is limited in a high-temperature environment and the condensation heat transfer performance is affected when the outdoor heat exchanger 2 serves as both a condenser and an evaporator can be solved.

[0058] To reduce the control complexity of the heat pump air-conditioning system provided by the present disclosure, in an implementation manner provided by the present disclosure, the outlet of the indoor evaporator 5 is connected to the inlet of the gas-liquid separation device 6, and the gas outlet of the gas-liquid separation device 6 is connected to the second refrigerant inlet C of the first heat exchanger 3. That is to say, the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the indoor evaporator 5 first enters the gas-liquid separation device 6, is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6, and then the gaseous refrigerant enters the first heat exchanger 3 to absorb the heat of the refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2.

[0059] In the prior art, the gas-liquid separation device is usually arranged at the inlet of the compressor, that is, after the refrigerant returning to the compressor passes through the gas-liquid separation device for gas-liquid separation, the gaseous refrigerant returns to the compressor again. However, since a small amount of liquid refrigerant will still be carried in the gaseous refrigerant separated by the gas-liquid separation device, the liquid refrigerant entering the compressor will cause liquid hammer in the compressor. Therefore, in the prior art, the superheat of the refrigerant at the inlet of the compressor is usually controlled so that the superheat of the refrigerant at the compressor inlet is 0, that is, the refrigerant at the compressor inlet is located on the refrigerant saturated vapor line, so as to avoid liquid hammer caused by the refrigerant to the compressor. However, the control of the superheat of the refrigerant will increase the control complexity of the heat pump air-conditioning system.

[0060] In the present disclosure, the gas-liquid separation device 6 is not arranged at the inlet of the compressor 1, that is, downstream of the first heat exchanger 3 and upstream of the compressor 1, but is arranged at the second refrigerant inlet C of the first heat exchanger 3. Since the gaseous refrigerant flowing out of the gas outlet of the gas-liquid separation device 6 will absorb heat and obtain enthalpy after entering the first heat exchanger 3, the refrigerant can cross the saturated vapor line and enter the superheated steam region (as shown by the arrow 300b in Figure 6 ). The refrigerant in the superheated steam region is pure gas, and the pure gas refrigerant entering the compressor 1 will not cause liquid hammer to the compressor 1. That is to say, even if a small amount of liquid refrigerant is carried in the gaseous refrigerant flowing out of the gas outlet of the gas-liquid separation device 6, the liquid refrigerant can also absorb heat and evaporate into gas in the first heat exchanger 3, so that the refrigerant entering the compressor 1 is pure gas refrigerant, and there is no need to control the superheat anymore, thereby reducing the control complexity of the heat pump air-conditioning system.

[0061] To enable the heat pump air-conditioning system provided by the present disclosure to have more working modes and stronger functionality, optionally, in the first implementation manner provided by the present disclosure, as Figure 2As shown, the heat pump air conditioning system may further include an indoor condenser 7, a flow-through passage 8, and a throttling passage 9. Among them, the outlet of the compressor 1 is connected to the inlet of the flow-through passage 8 and the inlet of the indoor condenser 7. The outlet of the indoor condenser 7 is connected to the inlet of the throttling passage 9. The outlet of the flow-through passage 8 and the outlet of the throttling passage 9 are connected to the inlet of the outdoor heat exchanger 2. The outlet of the outdoor heat exchanger 2 is further connected to the inlet of the gas-liquid separation device 6 via a first flow passage 10 that can be selectively opened or closed. In the above first embodiment, by controlling the corresponding opening and closing of the flow-through passage 8, the throttling passage 9, and the first flow passage 10, and the opening and closing of the first expansion valve 4, the heat pump air conditioning system can have a heat pump heating mode and a first dehumidification mode. Specifically, by cutting off the flow-through passage 8, opening the throttling passage 9 and the first flow passage 10, and closing the first expansion valve 4, the heat pump heating mode as shown in Figure 11 can be realized. In this mode, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 enters the indoor condenser 7 and releases heat to the passenger compartment in the indoor condenser 7, realizing the heating of the passenger compartment; by cutting off the flow-through passage 8 and the first flow passage 10, opening the throttling passage 9, and opening the first expansion valve 4, the first dehumidification mode as shown in Figure 19 can be realized. In this mode, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 enters the indoor condenser 7 and releases heat to the passenger compartment in the indoor condenser 7. The refrigerant flowing out of the indoor condenser 7 loses enthalpy through the outdoor heat exchanger 2 and the first heat exchanger 3, and after being throttled and depressurized by the first expansion valve 4, it becomes a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. This gas-liquid two-phase mixed refrigerant absorbs heat in the indoor evaporator 5. When the relatively warm and humid air in the passenger compartment encounters the relatively cold indoor evaporator 5, it condenses into water droplets on the surface of the indoor evaporator 5, forming condensate water, thereby reducing the air humidity in the passenger compartment. Since the indoor condenser 7 is in a working state, it can release heat to the passenger compartment and balance the temperature of the passenger compartment, ensuring that the temperature of the passenger compartment will not be too low due to the opening of the indoor evaporator 5.

[0062] In the above first embodiment, when the heat pump air conditioning system is in the refrigeration mode, the refrigerant flowing out of the outlet of the compressor 1 may enter the indoor condenser 7. At this time, the vehicle's air door mechanism can be controlled to make the air blown by the fan flow only through the indoor evaporator 5 and not through the indoor condenser 7. In this way, even if there is high-temperature and high-pressure gaseous refrigerant in the indoor condenser 7, this high-temperature and high-pressure gaseous refrigerant will not exchange heat with the air in the passenger compartment, thus avoiding the problem that the temperature in the passenger compartment cannot be reduced due to the heat exchange between the refrigerant in the indoor condenser 7 and the passenger compartment.

[0063] In the second embodiment provided by the present disclosure, as shown in Figure 1As shown, based on the above first embodiment, the outlet of the compressor 1 can be connected to the inlet of the indoor condenser 7 via a second flow path 11 that can be selectively opened or closed. That is to say, by controlling the flow path 8 and the second flow path 11, the refrigerant flowing out of the outlet of the compressor 1 can be selectively made to directly flow into the indoor condenser 7 or directly flow into the outdoor heat exchanger 2. Thus, as Figure 5 shown, in the refrigeration mode, by controlling the second flow path 11 to be closed, the refrigerant flowing out of the outlet of the compressor 1 can be made to directly flow into the outdoor heat exchanger 2 without flowing into the indoor condenser 7, thereby avoiding the heat in the indoor condenser 7 being transferred to the air in the passenger compartment by means of heat radiation due to the presence of high-temperature and high-pressure gaseous refrigerant, which affects the refrigeration effect and efficiency of the indoor evaporator 5.

[0064] In the third embodiment provided by the present disclosure, as Figure 3 shown, the heat pump air-conditioning system may further include an indoor condenser 7, a flow path 8, and a throttling flow path 9. The outlet of the compressor 1 is connected to the inlet of the indoor condenser 7, and the outlet of the indoor condenser 7 is selectively connected to the inlet of the outdoor heat exchanger 2 via the flow path 8 or the throttling flow path 9. The outlet of the outdoor heat exchanger 2 is further connected to the inlet of the gas-liquid separation device 6 via a first flow path 10 that can be selectively opened or closed. Here, it should be noted that the outlet of the indoor condenser 7 being selectively connected to the inlet of the outdoor heat exchanger 2 via the flow path 8 or the throttling flow path 9 means that the outlet of the indoor condenser 7 can be selectively connected to the inlet of the outdoor heat exchanger 2 via the flow path 8 or the throttling flow path 9, that is, the refrigerant flowing out of the outlet of the indoor condenser 7 can selectively flow into the inlet of the outdoor heat exchanger 2 through the flow path 8 or the throttling flow path 9.

[0065] In the third embodiment, in the refrigeration mode, the throttling flow path 9 is cut off, the through-flow path 8 is turned on, and the first flow path 10 is cut off. At this time, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 sequentially passes through the indoor condenser 7 and the through-flow path 8 and then enters the outdoor heat exchanger 2. By controlling the air door mechanism, the air blown by the fan can only flow through the indoor evaporator 5 and not through the indoor condenser 7. That is to say, at this time, although the high-temperature and high-pressure gaseous refrigerant flows through the indoor condenser 7, since there is no air passing through the indoor condenser 7, the refrigerant does not exchange heat with the air in the passenger compartment in the indoor condenser 7, and the indoor condenser 7 is used as a through-flow channel. In the heat pump heating mode, the through-flow path 8 is cut off, the throttling flow path 9 is turned on, and the first flow path 10 is turned on. In this way, the refrigerant that has released heat to the passenger compartment in the indoor condenser 7 can pass through the throttling flow path 9 to be throttled and depressurized and then enter the outdoor heat exchanger 2, so that the refrigerant can absorb the heat of the outside atmosphere in the outdoor heat exchanger 2. In the first dehumidification mode, the through-flow path 8 is cut off, the throttling flow path 9 is turned on, and the first flow path 10 is cut off. The refrigerant that has released heat to the passenger compartment in the indoor condenser 7 can pass through the throttling flow path 9 to be throttled and depressurized and then enter the outdoor heat exchanger 2. The refrigerant absorbs the heat of the outside atmosphere in the outdoor heat exchanger 2, then releases heat in the first heat exchanger 3, and then passes through the first expansion valve 4 to be throttled and depressurized and enters the indoor evaporator 5, so that the wet air in the passenger compartment condenses into condensed water on the surface of the indoor evaporator 5.

[0066] The difference between the above-mentioned third embodiment and the second embodiment is that whether in the refrigeration mode or the heat pump heating mode, in the third embodiment, the refrigerant discharged from the outlet of the compressor 1 will flow through the indoor condenser 7. In the refrigeration mode, there is no air passing through the indoor condenser 7, and the indoor condenser 7 only plays a role of through-flow, and the refrigerant does not exchange heat with the air in the passenger compartment in the indoor condenser 7; while in the heat pump heating mode, there is air passing through the indoor condenser 7, and at this time, the refrigerant in the indoor condenser 7 exchanges heat with the air in the passenger compartment. In the second embodiment, in the refrigeration mode, the refrigerant discharged from the outlet of the compressor 1 flows through the indoor condenser 7 and directly enters the outdoor heat exchanger 2; in the heating mode, the refrigerant discharged from the outlet of the compressor 1 directly flows into the indoor condenser 7.

[0067] Optionally, for the above-mentioned first embodiment and second embodiment, as Figure 1 and Figure 2 shown, a first stop valve 12 is provided on the first flow path 10, a second stop valve 13 is provided on the second flow path 11, a third stop valve 14 is provided on the through-flow path 8, and a second expansion valve 15 is provided on the throttling flow path 9, so as to be able to selectively turn on or cut off the first flow path 10 and the second flow path 11, directly turn on or cut off the through-flow path 8 for the refrigerant, and throttle or cut off the throttling flow path 9 for the refrigerant.

[0068] Optionally, for the above-mentioned third implementation manner, in one implementation manner, as Figure 3 shown, a first stop valve 12 is provided on the first flow path 10, a third stop valve 14 is provided on the through-flow path 8, and a second expansion valve 15 is provided on the throttling flow path 9.

[0069] In another implementation manner, a first stop valve 12 is provided on the first flow path 10, and the heat pump air-conditioning system further includes an expansion switch valve 16. The outlet of the indoor condenser 7 is connected to the inlet of the outdoor heat exchanger 2 via the expansion switch valve 16. The through-flow path 8 is the through-flow channel inside the expansion switch valve 16, and the throttling flow path 9 is the throttling channel inside the expansion switch valve 16. Here, the expansion switch valve 16 is equivalent to the integration of an expansion valve and a switch valve. The expansion switch valve 16 has a throttling channel and a through-flow channel inside. A throttle valve port and a throttle valve core are provided in the throttling channel, and a through-flow valve port and a through-flow valve core are provided in the through-flow channel. It is possible to select and control the opening of the throttle valve core or the opening of the through-flow valve core according to the working mode of the heat pump air-conditioning system, so that the refrigerant has a throttling state of being throttled and depressurized and a through-flow state of not being throttled and being directly conducted when passing through the expansion switch valve 16.

[0070] In other implementation manners, a first switch valve may be provided on the above-mentioned first flow path 10, a second switch valve may be provided on the second flow path 11, and a third switch valve may be provided on the through-flow path 8.

[0071] In addition, it should be noted here that the type of the expansion valve in the present disclosure may be an electronic expansion valve or an electromagnetic cut-off expansion valve, and the present disclosure does not limit the specific type of the expansion valve.

[0072] Since the heat pump air-conditioning system is easily affected by the ambient temperature during use, in order to enable the heat pump air-conditioning system to have different dehumidification modes at different ambient temperatures, in addition to the above-mentioned first dehumidification mode, the heat pump air-conditioning system provided by the present disclosure may also have a second dehumidification mode and a third dehumidification mode. As one implementation manner, the outlet of the indoor condenser 7 is further connected to the inlet of the first expansion valve 4 via a third flow path 17 that can be selectively conducted or cut off, and the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 through a check valve 18. As Figure 21 and Figure 23 shown, by controlling the conduction or cut-off of the third flow path 17, the heat pump air-conditioning system can have a second dehumidification mode and a third dehumidification mode.

[0073] In the second dehumidification mode, as Figure 21 shown, the throttling flow path 9 is closed, the third flow path 17 is conducted, and the refrigerant that has released heat and flows out from the outlet of the indoor condenser 7 can directly enter the indoor evaporator 5 after being throttled and depressurized by the first expansion valve 4. In the third dehumidification mode, as Figure 23As shown, the throttling flow path 9 is connected, the third flow path 17 is connected, and the refrigerant after heat release flowing out from the outlet of the indoor condenser 7 is divided into two streams, one stream flows into the outdoor heat exchanger 2 after throttling and reducing the pressure through the throttling flow path 9, and the other stream flows into the indoor evaporator 5 after throttling and reducing the pressure through the first expansion valve 4. The refrigerant flowing out of the indoor evaporator 5 and the refrigerant flowing out of the outdoor heat exchanger 2 converge and finally return to the compressor 1.

[0074] Here, it should be noted that Figure 23 As shown, in the third dehumidification mode, since the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 through the one-way valve 18, the refrigerant flowing out of the outlet of the indoor condenser 7 can only flow into the first expansion valve 4, and cannot flow back to the first heat exchanger 3 through the first one-way valve 18. In addition, since the pressure of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 (such as Figure 24 The pressure corresponding to the arrow 200 is less than the pressure of the refrigerant flowing out of the outlet of the indoor condenser 7 (such as Figure 24 Therefore, the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 cannot pass through the first heat exchanger 3 and the first one-way valve 18 and flow into the first expansion valve 4.

[0075] like Figures 19 to 24 As shown, one of the main differences among the first dehumidification mode, the second dehumidification mode and the third dehumidification mode is whether the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2, absorbs the heat of the outside atmosphere in the outdoor heat exchanger 2, and thus transports the heat in the environment. Specifically, in the first dehumidification mode, Figure 19 As shown, the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2, absorbs heat in the outdoor heat exchanger 2, flows into the first heat exchanger 3, releases heat in the first heat exchanger 3, and then passes through the first expansion valve 4 to throttle and reduce pressure to enter the indoor evaporator 5; in the second dehumidification mode, the refrigerant flowing out of the indoor condenser 7 flows into the indoor evaporator 5 without flowing through the outdoor heat exchanger 2; in the third dehumidification mode, part of the refrigerant flowing out of the indoor condenser 7 flows directly into the outdoor heat exchanger 2, and the other part flows directly into the indoor evaporator 5. Based on this, the first dehumidification mode can be applied to the situation where the ambient temperature is low, such as the situation where the ambient temperature is less than 5°C; the second dehumidification mode can be applied to the situation where the ambient temperature is higher than the ambient temperature applied to the first dehumidification mode, for example, the ambient temperature is 10°C-15°C; the ambient temperature applied to the third dehumidification mode can be between the ambient temperatures applied to the first dehumidification mode and the second dehumidification mode, for example, 5°C-10°C.

[0076] In addition, another difference among the first dehumidification mode, the second dehumidification mode, and the third dehumidification mode is as follows: In the first dehumidification mode, the refrigerant flowing out of the outlet of the gas-liquid separation device 6 absorbs the heat of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3. However, in the second dehumidification mode and the third dehumidification mode, no refrigerant flows into the first refrigerant inlet A of the first heat exchanger 3. Therefore, the refrigerant flowing out of the outlet of the gas-liquid separation device 6 cannot exchange heat in the first heat exchanger 3. That is to say, in the second dehumidification mode and the third dehumidification mode, the first heat exchanger 3 is used as a flow-through channel, and the refrigerant does not exchange heat in the first heat exchanger 3. As mentioned above, when the refrigerant flowing out of the outlet of the gas-liquid separation device 6 exchanges heat in the first heat exchanger 3, superheat adjustment is not required. Therefore, in the first dehumidification mode, superheat adjustment of the refrigerant flowing into the compressor 1 is not required, while in the second dehumidification mode and the third dehumidification mode, superheat adjustment of the refrigerant flowing into the compressor 1 is required to make the refrigerant on the saturated vapor line, that is, as Figure 22 and Figure 24 shown, the starting point of the arrow 100 is located on the saturated vapor line.

[0077] In addition, in order to improve the heating capacity of the heat pump air conditioning system in a low-temperature environment, the heat pump air conditioning system provided by the present disclosure may further include a second heat exchanger 19 and a third expansion valve 20. The first refrigerant outlet B of the first heat exchanger 3 is also connected to the refrigerant inlet of the second heat exchanger 19 via the third expansion valve 20. The refrigerant outlet of the second heat exchanger 19 is connected to the inlet of the gas-liquid separation device 6. The first coolant outlet of the second heat exchanger 19 is used to connect to the inlet of the vehicle's electronic device, and the first coolant inlet of the second heat exchanger 19 is used to connect to the outlet of the electronic device.

[0078] Since the first refrigerant outlet B of the first heat exchanger 3 is also connected to the refrigerant inlet of the second heat exchanger 19 via the third expansion valve 20, the refrigerant can exchange heat with the coolant that enters the second heat exchanger 19 after absorbing heat at the electronic device in the second heat exchanger 19, thereby recovering the heat dissipated by the electronic device into the heat pump air conditioning system.

[0079] Specifically, as Figure 15As shown, the heat pump air conditioning system provided by the present disclosure also has a first heat pump heating mode with waste heat recovery. In this mode, the through-flow path 8 is cut off, the second flow path 11 is conducted, the throttling flow path 9 is conducted, the first expansion valve 4 is closed, the first flow path 10 is cut off, and the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the indoor condenser 7 and releases heat to the passenger compartment in the indoor condenser 7 to increase the temperature of the passenger compartment. The refrigerant flowing out from the outlet of the indoor condenser 7 is throttled and depressurized through the throttling flow path 9 and then flows into the outdoor heat exchanger 2, and absorbs the heat of the external atmosphere in the outdoor heat exchanger 2 to transfer the heat in the outdoor environment, so that the enthalpy value of the refrigerant increases. The refrigerant flowing out from the outlet of the outdoor heat exchanger 2 releases heat and loses enthalpy in the first heat exchanger 3 and then is throttled and depressurized by the second expansion valve 15 to become a low-temperature refrigerant. This low-temperature refrigerant enters the second heat exchanger 19. In the second heat exchanger 19, the high-temperature coolant after absorbing heat from the electronic device releases heat to this low-temperature refrigerant, and the low-temperature refrigerant obtains enthalpy, thereby achieving the purpose of recovering the heat of the electronic device into the heat pump air conditioning system and solving the problem that the heat absorption of the refrigerant at the outdoor heat exchanger 2 is insufficient when the ambient temperature is low. The refrigerant after absorbing heat flowing out from the outlet of the second heat exchanger 19 can increase the suction temperature and suction pressure at the inlet of the compressor 1, which is beneficial to improving the heating capacity of the heat pump air conditioning system in a low-temperature environment. That is to say, in the above-mentioned first heat pump heating mode with waste heat recovery, the refrigerant can transfer the heat of the external atmosphere through the outdoor heat exchanger 2 and transfer the heat of the electronic device through the second heat exchanger 19.

[0080] Optionally, the outlet of the indoor condenser 7 is also connected to the inlet of the first expansion valve 4 and the inlet of the third expansion valve 20 via a selectively conductive or cut-off third flow path 17, and the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 and the inlet of the third expansion valve 20 through a one-way valve 18. Since the outlet of the indoor condenser 7 is also connected to the inlet of the third expansion valve 20 via the third flow path 17, the heat pump air conditioning system provided by the present disclosure can also have a second heat pump heating mode with waste heat recovery.

[0081] Specifically, as Figure 17As shown, the control flow path 8 is closed, the second flow path 11 is turned on, the third flow path 17 is turned on, the throttling flow path 9 is turned on, the first flow path 10 is turned on, and the third expansion valve 20 is opened, so that the heat pump air conditioning system has a second heat pump with waste heat recovery heating mode. In this mode, the refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams, one stream enters the outdoor heat exchanger 2 after throttling and reducing pressure through the throttling flow path 9, and absorbs the heat of the outside atmosphere, and the other stream enters the second heat exchanger 19 after throttling and reducing pressure through the third expansion valve 20, and absorbs the heat of the high-temperature coolant after absorbing heat at the electronic device in the second heat exchanger 19, and the refrigerant after absorbing heat flowing out of the refrigerant outlet of the second heat exchanger 19 and the refrigerant after absorbing heat flowing out of the outlet of the outdoor heat exchanger 2 converge and return to the compressor 1 together. In the second heat pump with waste heat recovery heating mode, since the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the third expansion valve 20 through the one-way valve 18, the refrigerant flowing out of the outlet of the indoor condenser 7 cannot be diverted back to the first heat exchanger 3, and the pressure of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 (refer to Figure 18 The pressure of the refrigerant flowing out of the outlet of the indoor condenser 7 (as shown by the arrow 200 in FIG. Figure 18 As shown by the arrow 700 in FIG. 1 , the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 cannot flow through the first heat exchanger 3 and enter the third expansion valve 20.

[0082] The difference between the above-mentioned first heat pump with waste heat recovery heating mode and the second heat pump with waste heat recovery heating mode is that in the first heat pump with waste heat recovery heating mode, all the refrigerant flowing out of the outlet of the indoor condenser 7 enters the outdoor heat exchanger 2, first absorbs heat in the outdoor heat exchanger 2, then flows through the first heat exchanger 3 and then absorbs heat in the second heat exchanger 19; in the second heat pump with waste heat recovery heating mode, part of the refrigerant flowing out of the outlet of the indoor condenser 7 absorbs heat in the outdoor heat exchanger 2, and the other part absorbs heat in the second heat exchanger 19. Based on this, if Figure 15 As shown, in the first heat pump with waste heat recovery heating mode, the refrigerant flowing out of the outlet of the gas-liquid separation device 6 absorbs the heat of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3. Therefore, in the first heat pump with waste heat recovery heating mode, there is no need to control the superheat of the refrigerant about to enter the compressor 1, and the superheat of the refrigerant about to enter the compressor 1 is controlled to 0. In the second heat pump with waste heat recovery heating mode, as Figure 17 As shown, in this mode, the refrigerant does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a flow passage, so it is necessary to adjust the superheat of the refrigerant flowing into the compressor 1 so that the refrigerant is on the saturated steam line, that is, Figure 18 As shown, the starting point of arrow 100 is located on the saturated steam line.

[0083] In addition, since the outlet of the indoor condenser 7 is also connected to the inlet of the third expansion valve 20 via the third flow path 17, the heat pump air-conditioning system provided by the present disclosure can also have a waste heat recovery heating mode. In this mode, the refrigerant flowing out of the outlet of the indoor condenser 7 does not flow through the outdoor heat exchanger 2 to transfer the heat of the external atmosphere, but directly flows into the second heat exchanger 19 to transfer the heat of the electronic devices in the second heat exchanger 19.

[0084] Specifically, in the waste heat recovery heating mode, as Figure 13 shown, the through-flow path 8 is cut off, the second flow path 11 is conducted, the throttling flow path 9 is cut off, the first flow path 10 is cut off, the third flow path 17 is conducted, the third expansion valve 20 is opened, and the compressor 1, the indoor condenser 7, the third expansion valve 20, the second heat exchanger 19, the gas-liquid separation device 6, and the first heat exchanger 3 are sequentially connected in series to form a loop. The refrigerant flowing out of the outlet of the indoor condenser 7 is throttled and depressurized by the third expansion valve 20 and then flows into the second heat exchanger 19, and absorbs the heat of the high-temperature coolant that has absorbed heat from the electronic devices in the second heat exchanger 19. The refrigerant that has absorbed heat and obtained enthalpy flows out of the refrigerant outlet of the second heat exchanger 19 and finally returns to the compressor 1.

[0085] Here, the electronic devices refer to devices that need to use electricity to work and generate heat during the working process. For example, the electronic devices may include at least one of a motor, a charger, a motor controller, and a DC-DC converter. When the heat pump air-conditioning system is used in an electric vehicle, when the battery pack is in a charging state, the charger, the DC-DC converter, etc. will generate heat due to being in a working state, that is, the charger, the DC-DC converter, etc. have a heat dissipation requirement. At this time, if there is a heating requirement in the passenger compartment, the heat pump air-conditioning system can be set to the waste heat recovery mode, the first heat pump with waste heat recovery mode, or the second heat pump with waste heat recovery mode, so as to recycle the heat of the charger, the DC-DC converter, etc. into the heat pump air-conditioning system while meeting the heat dissipation requirements of the charger, the DC-DC converter, etc., and improve the heating capacity of the heat pump air-conditioning system. When the electric vehicle is in a driving state, the motor converts the electrical energy of the battery pack into mechanical energy to drive the vehicle, and the motor and the like will generate heat. If there is a heating requirement in the passenger compartment at this time, the heat pump air-conditioning system can be set to the waste heat recovery mode, the first heat pump with waste heat recovery mode, or the second heat pump with waste heat recovery mode, so as to recycle the heat of the motor into the heat pump air-conditioning system while realizing the heat dissipation and cooling of the motor.

[0086] Optionally, a fourth cut-off valve 21 may be provided on the above-mentioned third flow path 17, and the third flow path 17 is conducted or cut off by controlling the opening or closing of the fourth cut-off valve 21. In other embodiments, a fourth switching valve may also be provided on the third flow path 17.

[0087] In the field of electric vehicle technology, vehicle manufacturers strive to continuously shorten the charging time of the battery pack when designing electric vehicles. The shortened charging time of the battery pack means that the battery pack releases more heat during charging and the battery pack temperature is higher. The battery pack needs to be cooled quickly to shorten the charging time of the battery pack while keeping the battery pack temperature within its appropriate operating temperature range.

[0088] In order to meet the requirement of rapid cooling of the battery pack during fast charging, the second coolant outlet of the second heat exchanger 19 can be used to connect to the inlet of the battery pack of the vehicle, and the second coolant inlet of the second heat exchanger 19 can be used to connect to the outlet of the battery pack. In this way, the battery pack can be quickly cooled by the heat pump air conditioning system provided by the present invention.

[0089] Specifically, Figure 9 As shown, in the battery pack cooling mode, the through-flow path 8 is turned on, the second flow path 11, the throttling flow path 9, and the first flow path 10 are all turned off, the first expansion valve 4 is closed, and the third expansion valve 20 is opened. In this way, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the outdoor heat exchanger 2, and dissipates heat to the outside atmosphere in the outdoor heat exchanger 2. The refrigerant loses enthalpy in the outdoor heat exchanger 2, that is, the enthalpy value decreases (such as Figure 10 As shown by the arrow 200 in FIG. 1 , the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 through the first refrigerant inlet A of the first heat exchanger 3, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 3 in the first heat exchanger 3. The refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. 1 ). Figure 10 As shown by the arrow 300a in the figure, the refrigerant after losing enthalpy flowing out from the first refrigerant outlet B of the first heat exchanger 3 becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure through the third expansion valve 20. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature coolant after absorbing heat at the battery pack in the second heat exchanger 19, so that the second coolant outlet of the second heat exchanger 19 flows out the low-temperature coolant, and the low-temperature coolant can continue to cool the battery pack.

[0090] Because in the battery pack cooling mode provided in the present invention, the refrigerant releases heat twice through the outdoor heat exchanger 2 and the first heat exchanger 3 before entering the second heat exchanger 19, it is beneficial to increase the supercooling of the refrigerant entering the second heat exchanger 19. The higher the supercooling, the more heat the refrigerant absorbs in the second heat exchanger 19, making the temperature of the coolant lower. The lower the temperature of the coolant, the more conducive it is to rapid cooling of the battery pack.

[0091] When the battery pack has a cooling requirement and the passenger compartment has a refrigeration requirement, the first expansion valve 4 can be opened on the basis of the battery pack cooling mode, so that the heat pump air conditioning system provided by the present disclosure can have a refrigeration and battery pack cooling mode. In this mode, as Figure 7 shown, the refrigerant flowing out from the first refrigerant outlet B of the first heat exchanger 3 is divided into two streams. One stream enters the indoor evaporator 5 after throttling and pressure reduction by the first expansion valve 4, absorbs the heat of the passenger compartment, and realizes the refrigeration of the passenger compartment. The other stream enters the second heat exchanger 19 after throttling and pressure reduction by the third expansion valve 20, absorbs the heat of the battery pack, and realizes the cooling of the battery pack.

[0092] The following will take the Figure 1 embodiment in Figures 5 to 24 as an example, and in combination with Figures 2 to 4 to describe the cycle process and principle in the main working mode of the heat pump air conditioning system provided by the present disclosure. The cycle process and principle of the system under other embodiments (for example, Figures 2 to 4 ) are similar to Figure 1 and will not be elaborated one by one here.

[0093] For easy understanding, before describing the main working mode of the heat pump air conditioning system provided by the present disclosure, the pressure-enthalpy diagram shown in FIG. 6 is first described. In this pressure-enthalpy diagram, the abscissa is the enthalpy of the refrigerant, and from the left end to the right end of the abscissa, the enthalpy gradually increases. The ordinate is the pressure of the refrigerant, and from the lower end to the upper end of the ordinate, the pressure gradually increases. The pressure-enthalpy diagram has a saturated liquid line and a saturated vapor line. The left side of the saturated liquid line is the liquid region, and the refrigerant in this region is in a liquid state; the right side of the saturated vapor line is the superheated vapor region, and the refrigerant in this region is in a gaseous state; the region between the saturated liquid line and the saturated vapor line is the wet vapor region, that is, the gas-liquid coexistence region, and the refrigerant in this region is in a gas-liquid two-phase mixed state.

[0094] Mode 1: Refrigeration mode. In this mode, as Figure 5 shown, the first shut-off valve 12 is closed, the second shut-off valve 13 is closed, the third shut-off valve 14 is opened, the fourth shut-off valve 21 is closed, the first expansion valve 4 is opened, and the second expansion valve 15 and the third expansion valve 20 are closed. As Figure 5 and Figure 6 shown, the refrigerant entering the compressor 1 is gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as shown by the arrow 100 in Figure 6 ), and this high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 2 and releases enthalpy to the external atmosphere in the outdoor heat exchanger 2 (as shown by the arrow 200 in Figure 6 ), and the refrigerant after losing enthalpy flowing out from the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 and continues to release enthalpy in the first heat exchanger 3 (as shown by the arrow in Figure 6As shown by arrow 300a in [Figure], liquid refrigerant flows out from the first refrigerant outlet B of the first heat exchanger 3. This liquid refrigerant undergoes an isenthalpic pressure drop in the first expansion valve 4 and crosses the saturated liquid line (as Figure 6 shown by arrow 400 in [Figure]). A two-phase refrigerant of low temperature and low pressure flows out from the outlet of the first expansion valve 4. This two-phase refrigerant of low temperature and low pressure absorbs heat from the passenger compartment in the indoor evaporator 5 and gains enthalpy (as Figure 6 shown by arrow 500 in [Figure]) to lower the temperature of the passenger compartment and achieve refrigeration of the passenger compartment. The two-phase refrigerant mixture flowing out from the outlet of the indoor evaporator 5 flows into the gas-liquid separation device 6, where it is separated into liquid and gas states. The gaseous refrigerant flows out from the gas outlet of the gas-liquid separation device 6 (as Figure 6 shown by point 600 in [Figure]) and flows into the first heat exchanger 3, where it absorbs heat and gains the enthalpy lost by the refrigerant flowing out from the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3 (as Figure 6 shown by arrow 300b in [Figure]). Thus, a small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separation device 6 is further evaporated into gaseous refrigerant, so that the refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 is in the superheated steam region. The gaseous refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1. In the above refrigeration mode, the refrigerant first releases heat to the external atmosphere through the outdoor heat exchanger 2 and loses enthalpy, and then releases heat again in the first heat exchanger 3 and loses enthalpy, so that this refrigeration mode can provide refrigerant with a relatively high degree of subcooling to the indoor evaporator 5, and further enables the heat pump air-conditioning system to have good refrigeration effect and refrigeration efficiency in a high-temperature environment.

[0095] Mode 2: Refrigeration and battery pack cooling mode. In this mode, as Figure 7 shown, the first shut-off valve 12 is closed, the second shut-off valve 13 is closed, the third shut-off valve 14 is opened, the fourth shut-off valve 21 is closed, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As Figure 7 and Figure 8 shown, the refrigerant entering the compressor 1 is gaseous refrigerant. The compressor 1 compresses the gaseous refrigerant so that high-temperature and high-pressure gaseous refrigerant is discharged from the outlet of the compressor 1 (as Figure 8 shown by arrow 100 in [Figure]). This high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 2 and releases heat to the external atmosphere and loses enthalpy in the outdoor heat exchanger 2 (as Figure 8 shown by arrow 200 in [Figure]). The refrigerant after losing enthalpy flowing out from the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 and continues to release heat and lose enthalpy in the first heat exchanger 3 (as Figure 8 shown by arrow 300a in [Figure]). The liquid refrigerant flowing out from the first refrigerant outlet B of the first heat exchanger 3 is divided into two streams. One stream undergoes an isenthalpic pressure drop in the first expansion valve 4 and crosses the saturated liquid line (asFigure 8 As shown by the arrow 400 in [reference], a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out from the outlet of the first expansion valve 4. This low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the passenger compartment in the indoor evaporator 5 and obtains enthalpy (as Figure 8 shown by the arrow 500 in [reference]), so as to reduce the temperature of the passenger compartment and achieve the refrigeration of the passenger compartment; another stream undergoes an isenthalpic pressure drop in the third expansion valve 20 and passes through the saturated liquid line (as Figure 8 shown by the arrow 2000 in [reference]). A low-temperature and low-pressure gas-liquid two-phase refrigerant flows out from the outlet of the third expansion valve 20. This low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature coolant after absorbing heat at the battery pack in the second heat exchanger 19 and obtains enthalpy (as Figure 8 shown by the arrow 190 in [reference]), so that a low-temperature coolant for cooling the battery pack can flow out from the second coolant outlet of the second heat exchanger 19, achieving the cooling of the battery pack. The gas-liquid two-phase mixed refrigerant flowing out from the outlet of the indoor evaporator 5 and the gas-liquid two-phase mixed refrigerant flowing out from the refrigerant outlet of the second heat exchanger 19 converge and then flow into the gas-liquid separation device 6. In the gas-liquid separation device 6, it is separated into liquid and gas. The gaseous refrigerant flows out from the gas outlet of the gas-liquid separation device 6 (as Figure 8 shown by the dot 600 in [reference]) and flows into the first heat exchanger 3, where it absorbs heat and obtains the enthalpy lost by the refrigerant flowing out from the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3 (as Figure 8 shown by the arrow 300b in [reference]), thereby further evaporating the small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separation device 6 into gaseous refrigerant, so that the refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 is in the superheated steam region. The gaseous refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1. In the above refrigeration mode, the refrigerant first releases heat to the external atmosphere through the outdoor heat exchanger 2 and loses enthalpy, and then releases heat again in the first heat exchanger 3 and loses enthalpy. Thus, this refrigeration mode can provide a refrigerant with a relatively high degree of subcooling to the indoor evaporator 5, and further enable the heat pump air-conditioning system to have good refrigeration effect and refrigeration efficiency in a high-temperature environment, and at the same time can achieve the rapid cooling of the battery pack, which is beneficial to realizing the rapid charging of the battery pack.

[0096] Mode 3: Battery pack cooling mode. In this mode, as Figure 9 shown, the first cut-off valve 12 is closed, the second cut-off valve 13 is closed, the third cut-off valve 14 is opened, the fourth cut-off valve 21 is closed, the first expansion valve 4 is closed, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As Figure 9 and Figure 10 shown, the refrigerant entering the compressor 1 is gaseous refrigerant. The compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 10As shown by arrow 100 in [figure], the high-temperature and high-pressure gaseous refrigerant enters outdoor heat exchanger 2, and releases heat to the external atmosphere in outdoor heat exchanger 2 to lose enthalpy (as Figure 10 shown by arrow 200 in [figure]). The refrigerant after losing enthalpy flowing out from the outlet of outdoor heat exchanger 2 flows into first heat exchanger 3, and continues to release heat and lose enthalpy in first heat exchanger 3 (as Figure 10 shown by arrow 300a in [figure]). The liquid refrigerant flowing out from the first refrigerant outlet B of first heat exchanger 3 undergoes an isenthalpic pressure drop in third expansion valve 20 and crosses the saturated liquid line (as Figure 10 shown by arrow 2000 in [figure]). The low-temperature and low-pressure gaseous two-phase refrigerant flowing out from the outlet of third expansion valve 20 absorbs the heat of the high-temperature coolant after absorbing heat at the battery pack in second heat exchanger 19 and gains enthalpy (as Figure 10 shown by arrow 190 in [figure]), so that the second coolant outlet of second heat exchanger 19 can flow out low-temperature coolant for cooling the battery pack, realizing the cooling of the battery pack. The gas-liquid two-phase mixed refrigerant flowing out from the refrigerant outlet of second heat exchanger 19 flows into gas-liquid separation device 6, and is separated into liquid and gas in gas-liquid separation device 6. The gaseous refrigerant flows out from the gas outlet of gas-liquid separation device 6 (as Figure 10 shown by dot 600 in [figure]) and flows into first heat exchanger 3, and absorbs heat in first heat exchanger 3, gaining the enthalpy lost by the refrigerant flowing out from the outlet of outdoor heat exchanger 2 in first heat exchanger 3 (as Figure 10 shown by arrow 300b in [figure]), thereby further evaporating the small amount of liquid refrigerant carried in the gaseous refrigerant separated by gas-liquid separation device 6 into gaseous refrigerant, so that the refrigerant flowing out from the second refrigerant outlet D of first heat exchanger 3 is in the superheated steam region. The gaseous refrigerant flowing out from the second refrigerant outlet D of first heat exchanger 3 returns to compressor 1. In the above refrigeration mode, the refrigerant first releases heat to the external atmosphere through outdoor heat exchanger 2 to lose enthalpy, and then releases heat again in first heat exchanger 3, so that this refrigeration mode can provide refrigerant with a higher degree of subcooling to indoor evaporator 5. The higher the degree of subcooling of the refrigerant, the more heat it absorbs, which is more conducive to shortening the cooling time of the battery pack and realizing the rapid cooling of the battery pack.

[0097] Mode 4: Heat pump heating mode. In this mode, as Figure 11 shown, first shut-off valve 12 is opened, second shut-off valve 13 is opened, third shut-off valve 14 is closed, fourth shut-off valve 21 is closed, first expansion valve 4 is closed, second expansion valve 15 is opened, and third expansion valve 20 is closed. As Figure 11 and Figure 12 shown, the refrigerant entering compressor 1 is gaseous refrigerant, and compressor 1 compresses the gaseous refrigerant so that the outlet of compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 12as indicated by arrow 100 in [figure], the high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7, and releases heat to the passenger compartment in the indoor condenser 7 and loses enthalpy (as Figure 12 indicated by arrow 700 in [figure]) to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The refrigerant after heat release flowing out of the outlet of the indoor condenser 7 undergoes an isenthalpic pressure drop in the second expansion valve 15 and crosses the saturated liquid line (as Figure 12 indicated by arrow 150 in [figure]), and a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out of the outlet of the second expansion valve 15. The low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat from the outside atmosphere in the outdoor heat exchanger 2 and gains enthalpy (as Figure 12 indicated by arrow 200 in [figure]). The gas-liquid two-phase mixed refrigerant with increased temperature flowing out of the outlet of the outdoor heat exchanger 2 is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6. The gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as Figure 12 indicated by point 600 in [figure]) and returns to the compressor 1 via the first heat exchanger 3. In this mode, since no heat exchange occurs in the first heat exchanger 3 for the gaseous refrigerant flowing out of the gas outlet of the gas-liquid separation device 6, that is, the first heat exchanger 3 serves as a flow-through channel, it is necessary to control the superheat of the refrigerant before the refrigerant returns to the compressor 1 to make the superheat of the refrigerant 0, that is, to make Figure 12 the starting point of arrow 100 in [figure] located on the saturated vapor line.

[0098] Mode Five: Waste Heat Recovery Heating Mode. In this mode, as Figure 13 shown, the first shut-off valve 12 is closed, the second shut-off valve 13 is opened, the third shut-off valve 14 is closed, the fourth shut-off valve 21 is opened, the first expansion valve 4 is closed, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As Figure 13 and Figure 14 shown, the refrigerant entering the compressor 1 is gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that a high-temperature and high-pressure gaseous refrigerant is discharged from the outlet of the compressor 1 (as Figure 14 indicated by arrow 100 in [figure]), and the high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7, and releases heat to the passenger compartment in the indoor condenser 7 and loses enthalpy (as Figure 14 indicated by arrow 700 in [figure]) to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The refrigerant after heat release flowing out of the outlet of the indoor condenser 7 undergoes an isenthalpic pressure drop in the third expansion valve 20 and crosses the saturated liquid line (as Figure 14 indicated by arrow 2000 in [figure]), and a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out of the outlet of the third expansion valve 20. The low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat from the high-temperature coolant after absorbing heat at the electronic device in the second heat exchanger 19 and gains enthalpy (as Figure 14as indicated by arrow 190 in [description], thus recovering the heat dissipated by the electronic device into the air-conditioning system. The gas-liquid two-phase refrigerant with increased temperature flowing out of the refrigerant outlet of the second heat exchanger 19 is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6. The gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as Figure 14 indicated by point 600 in [description]) and returns to the compressor 1 via the first heat exchanger 3.

[0099] Mode 6: The first heat pump heating mode with waste heat recovery. In this mode, as Figure 15 shown, the first shut-off valve 12 is closed, the second shut-off valve 13 is opened, the third shut-off valve 14 is closed, the fourth shut-off valve 21 is closed, the first expansion valve 4 is closed, the second expansion valve 15 is opened, and the third expansion valve 20 is opened. As Figure 15 and Figure 16 shown, the refrigerant entering the compressor 1 is gaseous refrigerant. The compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 16 indicated by arrow 100 in [description]). This high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7 and releases heat and loses enthalpy in the indoor condenser 7 (as Figure 16 indicated by arrow 700 in [description]) to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The refrigerant flowing out of the outlet of the indoor condenser 7 undergoes an isenthalpic pressure drop in the second expansion valve 15 and crosses the saturated liquid line (as Figure 16 indicated by arrow 150 in [description]). The low-temperature and low-pressure gas-liquid two-phase refrigerant flowing out of the outlet of the second expansion valve 15 absorbs heat from the outside atmosphere and gains enthalpy in the outdoor heat exchanger 2 (as Figure 16 indicated by arrow 200 in [description]). The refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 and releases heat and loses enthalpy in the first heat exchanger 3 (as Figure 16 indicated by arrow 300a in [description]). The refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 undergoes an isenthalpic pressure drop in the third expansion valve 20 (as Figure 16 indicated by arrow 2000 in [description]). The low-temperature and low-pressure gas-liquid two-phase refrigerant flowing out of the outlet of the third expansion valve 20 absorbs heat from the high-temperature coolant that has absorbed heat at the electronic device and gains enthalpy (as Figure 16 indicated by arrow 190 in [description]), thus recovering the heat dissipated by the electronic device into the air-conditioning system. The gas-liquid two-phase refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6. The gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as Figure 16as indicated by the dot 600) and enters the first heat exchanger 3, where the gaseous refrigerant absorbs heat and obtains the enthalpy lost by the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3 (as Figure 16 indicated by the arrow 300b in), thereby further evaporating the small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separation device 6 into gaseous refrigerant, so that the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 is in the superheated steam region, and the gaseous refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1.

[0100] Mode Seven: The second heat pump heating mode with waste heat recovery. In this mode, as Figure 17 shown, the first shut-off valve 12 is opened, the second shut-off valve 13 is opened, the third shut-off valve 14 is closed, the fourth shut-off valve 21 is opened, the first expansion valve 4 is closed, the second expansion valve 15 is opened, and the third expansion valve 20 is opened. As Figure 17 and Figure 18 shown, the refrigerant entering the compressor 1 is gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 18 indicated by the arrow 100 in), and the high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7 and releases heat and loses enthalpy to the passenger compartment in the indoor condenser 7 (as Figure 18 indicated by the arrow 700 in) to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams. One stream flows into the second expansion valve 15 and undergoes an isenthalpic pressure drop and crosses the saturated liquid line in the second expansion valve 15 (as Figure 18 indicated by the arrow 150 in), and the outlet of the second expansion valve 15 flows out low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. The low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs the heat of the external atmosphere and obtains enthalpy in the outdoor heat exchanger 2 (as Figure 18 indicated by the arrow 200 in); the other stream flows into the third expansion valve 20 and undergoes an isenthalpic pressure drop and crosses the saturated liquid line in the third expansion valve 20 (as Figure 18 indicated by the arrow 2000 in), and the outlet of the third expansion valve 20 flows out low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. The low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs the heat of the high-temperature coolant after absorbing heat from the electronic device in the second heat exchanger 19 and obtains enthalpy (as Figure 18 indicated by the arrow 190 in), thereby recovering the heat of the electronic device into the air-conditioning system. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and the gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 converge and then enter the gas-liquid separation device 6, and are separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6. The gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as Figure 18as indicated by point 600 in [reference] and flows back into compressor 1 through the first heat exchanger 3. In this mode, the refrigerant flowing out of the gas-liquid separation device 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a flow channel in this mode.

[0101] Mode Eight: The first dehumidification mode. In this mode, as Figure 19 shown, the first shut-off valve 12 is closed, the second shut-off valve 13 is opened, the third shut-off valve 14 is closed, the fourth shut-off valve 21 is closed, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As Figure 19 and Figure 20 shown, the refrigerant entering the compressor 1 is gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 20 indicated by arrow 100 in [reference]), and this high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7 and releases enthalpy by heating the passenger compartment in the indoor condenser 7 (as Figure 20 indicated by arrow 700 in [reference]) to balance the temperature in the passenger compartment. The refrigerant flowing out of the outlet of the indoor condenser 7 undergoes an isenthalpic pressure drop in the second expansion valve 15 and crosses the saturated liquid line (as Figure 20 indicated by arrow 150 in [reference]), and the outlet of the second expansion valve 15 discharges low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. This low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat from the outside atmosphere and obtains enthalpy in the outdoor heat exchanger 2 (as Figure 20 indicated by arrow 200 in [reference]), and the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 and releases enthalpy by heating in the first heat exchanger 3 (as Figure 20 indicated by arrow 300a in [reference]). The refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 undergoes an isenthalpic pressure drop in the first expansion valve 4 (as Figure 20 indicated by arrow 400 in [reference]), and the outlet of the first expansion valve 4 discharges low-temperature and low-pressure gas-liquid two-phase refrigerant. This low-temperature and low-pressure gas-liquid two-phase refrigerant flows into the indoor evaporator 5 and absorbs heat and obtains enthalpy (as Figure 20 indicated by arrow 500 in [reference]). When the moist air in the passenger compartment encounters the relatively low-temperature indoor evaporator 5, condensate will form on the surface of the indoor evaporator 5, thereby reducing the humidity of the air in the passenger compartment and realizing the dehumidification function of the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the indoor evaporator 5 is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6, and the gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as Figure 20 indicated by point 600 in [reference]) and enters the first heat exchanger 3. This gaseous refrigerant absorbs heat in the first heat exchanger 3 and obtains the enthalpy lost by the refrigerant flowing out of the outlet of the outdoor heat exchanger 3 in the first heat exchanger 3 (as Figure 20as shown by arrow 300b in [FIGURE], thereby further evaporating the small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separation device 6 into gaseous refrigerant, so that the refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 is in the superheated steam region, and the gaseous refrigerant flowing out from the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1.

[0102] Mode Nine: The second dehumidification mode. In this mode, as Figure 21 shown, the first stop valve 12 is closed, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is closed. As Figure 21 and 22 shown, the refrigerant entering the compressor 1 is gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as Figure 22 shown by arrow 100 in [FIGURE]), and this high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7 and releases enthalpy to the passenger compartment in the indoor condenser 7 (as Figure 22 shown by arrow 700 in [FIGURE]) to balance the temperature in the passenger compartment. The refrigerant after releasing heat flowing out from the outlet of the indoor condenser 7 undergoes an isenthalpic pressure drop in the first expansion valve 4 and crosses the saturated liquid line (as Figure 22 shown by arrow 400 in [FIGURE]), and the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out from the outlet of the first expansion valve 4 and flows into the indoor evaporator 5, and absorbs heat and obtains enthalpy in the indoor evaporator 5 (as Figure 22 shown by arrow 500 in [FIGURE]). When the moist air in the passenger compartment encounters the indoor evaporator 5 with a lower temperature, condensed water will form on the surface of the indoor evaporator 5, thereby reducing the humidity of the air in the passenger compartment and realizing the dehumidification function of the passenger compartment. The gas-liquid two-phase mixed refrigerant with an increased temperature flowing out from the outlet of the indoor evaporator 5 is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6, and the gaseous refrigerant flows out from the gas outlet of the gas-liquid separation device 6 (as Figure 22 shown by point 600 in [FIGURE]) and returns to the compressor 1 via the first heat exchanger 3. In this mode, the refrigerant flowing out from the gas outlet of the gas-liquid separation device 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a through-flow channel in this mode.

[0103] Mode Ten: The third dehumidification mode. In this mode, as Figure 23 shown, the first stop valve 12 is opened, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is opened, the second expansion valve 15 is opened, and the third expansion valve 20 is closed. As Figure 23 and Figure 24As shown, the refrigerant entering the compressor 1 is gaseous refrigerant. The compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges high-temperature and high-pressure gaseous refrigerant (as shown by the arrow 100 in Figure 24 ). This high-temperature and high-pressure gaseous refrigerant flows into the indoor condenser 7 and releases heat and loses enthalpy to the passenger compartment in the indoor condenser 7 (as shown by the arrow 700 in Figure 24 ) to balance the temperature in the passenger compartment. The refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams. One stream flows into the second expansion valve 15 and undergoes an isenthalpic pressure drop and passes through the saturated liquid line in the second expansion valve 15 (as shown by the arrow 150 in Figure 24 ). The outlet of the second expansion valve 15 discharges a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. This low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat from the outside atmosphere and gains enthalpy in the outdoor heat exchanger 2 (as shown by the arrow 200 in Figure 24 ). The other stream flows into the first expansion valve 4 and undergoes an isenthalpic pressure drop and passes through the saturated liquid line in the first expansion valve 4 (as shown by the arrow 400 in Figure 24 ). The outlet of the first expansion valve 4 discharges a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant. This low-temperature and low-pressure gas-liquid two-phase mixed refrigerant enters the indoor evaporator 5 and absorbs heat and gains enthalpy in the indoor evaporator 5 (as shown by the arrow 500 in Figure 24 ). When the moist air in the passenger compartment encounters the indoor evaporator 5 with a lower temperature, condensate will form on the surface of the indoor evaporator 5, thereby reducing the humidity of the air in the passenger compartment and realizing the dehumidification function of the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the indoor evaporator 5 converge and then enter the gas-liquid separation device 6, and are separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separation device 6. The gaseous refrigerant flows out of the gas outlet of the gas-liquid separation device 6 (as shown by the dot 600 in Figure 24 ) and flows through the first heat exchanger 3 back to the compressor 1. In this mode, the refrigerant flowing out of the gas outlet of the gas-liquid separation device 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a flow-through channel in this mode.

[0104] It should be noted that the above mode is the main working mode of the vehicle thermal management system provided by the present disclosure. For the working modes not mentioned in the present disclosure but that can be achieved by the vehicle thermal management system provided by the present disclosure also fall within the protection scope of the present disclosure.

[0105] According to another aspect of the present disclosure, a vehicle is also provided, including the above-mentioned heat pump air conditioning system.

[0106] The preferred embodiments of the present disclosure have been described in detail above in conjunction with the accompanying drawings. However, the present disclosure is not limited to the specific details in the above embodiments. Within the scope of the technical concept of the present disclosure, various simple modifications can be made to the technical solutions of the present disclosure, and these simple modifications all fall within the protection scope of the present disclosure.

[0107] In addition, it should be noted that, in the various specific technical features described in the above specific embodiments, they can be combined in any appropriate manner without conflict. To avoid unnecessary repetition, the present disclosure will not separately describe various possible combination manners.

[0108] Furthermore, any combination can be made between various different embodiments of the present disclosure as long as it does not violate the idea of the present disclosure, and it should also be regarded as the content disclosed by the present disclosure.

Claims

1. A heat pump air conditioning system, characterized in that, It includes a compressor (1), an outdoor heat exchanger (2), a first heat exchanger (3), a first expansion valve (4), and an indoor evaporator (5). The outlet of the compressor (1) is connected to the inlet of the outdoor heat exchanger (2), the outlet of the outdoor heat exchanger (2) is connected to the first refrigerant inlet (A) of the first heat exchanger (3), the first refrigerant outlet (B) of the first heat exchanger (3) is connected to the inlet of the indoor evaporator (5) via the first expansion valve (4), the outlet of the indoor evaporator (5) is connected to the second refrigerant inlet (C) of the first heat exchanger (3), and the second refrigerant outlet (D) of the first heat exchanger (3) is connected to the inlet of the compressor (1). The heat pump air conditioning system further includes a gas-liquid separation device (6). The outlet of the indoor evaporator (5) is connected to the inlet of the gas-liquid separation device (6), and the gas outlet of the gas-liquid separation device (6) is connected to the second refrigerant inlet (C) of the first heat exchanger (3). The heat pump air conditioning system further includes an indoor condenser (7), a through-flow path (8), and a throttling path (9). A third stop valve (14) is provided on the through-flow path (8), and a second expansion valve (15) is provided on the throttling path (9). The second expansion valve (15) is an electronic expansion valve or an electromagnetic stop expansion valve. The outlet of the compressor (1) is connected to the inlet of the through-flow path (8) and the inlet of the indoor condenser (7). The outlet of the indoor condenser (7) is connected to the inlet of the throttling path (9). The outlet of the through-flow path (8) and the outlet of the throttling path (9) are connected to the inlet of the outdoor heat exchanger (2). The outlet of the outdoor heat exchanger (2) is further connected to the inlet of the gas-liquid separation device (6) via a first flow path (10) that can be selectively conducted or cut off.

2. The heat pump air conditioning system according to claim 1, characterized in that, The outlet of the compressor (1) is connected to the inlet of the indoor condenser (7) via a second flow path (11) that can be selectively conducted or cut off.

3. The heat pump air conditioning system according to claim 2, characterized in that, A first stop valve (12) is provided on the first flow path (10), and a second stop valve (13) is provided on the second flow path (11).

4. The heat pump air conditioning system according to any one of claims 1-3, characterized in that, The outlet of the indoor condenser (7) is further connected to the inlet of the first expansion valve (4) via a third flow path (17) that can be selectively conducted or cut off. The first refrigerant outlet (B) of the first heat exchanger (3) is connected to the inlet of the first expansion valve (4) through a check valve (18).

5. The heat pump air-conditioning system according to any one of claims 1-3, characterized in that The heat pump air conditioning system further includes a second heat exchanger (19) and a third expansion valve (20). The first refrigerant outlet (B) of the first heat exchanger (3) is further connected to the refrigerant inlet of the second heat exchanger (19) via the third expansion valve (20). The refrigerant outlet of the second heat exchanger (19) is connected to the inlet of the gas-liquid separation device (6). The first coolant outlet of the second heat exchanger (19) is used to connect to the inlet of the vehicle's electronic device, and the first coolant inlet of the second heat exchanger (19) is used to connect to the outlet of the electronic device.

6. The heat pump air conditioning system according to claim 5, characterized in that, The outlet of the indoor condenser (7) is also connected to the inlets of the first expansion valve (4) and the third expansion valve (20) via a selectively openable or closable third flow path (17). The first refrigerant outlet (B) of the first heat exchanger (3) is connected to the inlets of the first expansion valve (4) and the third expansion valve (20) through a check valve (18).

7. The heat pump air conditioning system according to claim 6, wherein, A fourth shut-off valve (21) is provided on the third flow path (17).

8. The heat pump air conditioning system according to claim 5, characterized in that, The electronic device includes at least one of a motor, a charger, a motor controller, and a DC-DC converter.

9. The heat pump air conditioning system according to claim 5, characterized in that The second coolant outlet of the second heat exchanger (19) is used to connect to the inlet of the vehicle's battery pack, and the second coolant inlet of the second heat exchanger (19) is used to connect to the outlet of the battery pack.

10. A vehicle, characterized in that, A heat pump air conditioning system according to any one of claims 1-9 is included.

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