Heat pump air conditioning systems and vehicles

Abstract

The present disclosure relates to a heat pump air conditioning system and a vehicle. The system includes a compressor, an outdoor heat exchanger, a first gas-liquid separation device, a first heat exchanger, a first expansion valve, and an indoor evaporator. The compressor outlet is connected to a first port of the outdoor heat exchanger, a second port of the outdoor heat exchanger is connected to an inlet of the first gas-liquid separation device, a liquid outlet of the first gas-liquid separation device is connected to a first refrigerant inlet of the first heat exchanger, the first refrigerant outlet of the first heat exchanger is connected to an inlet of the indoor evaporator via a first expansion valve, the outlet of the indoor evaporator is connected to a 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. Liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device, which can increase the subcooling degree of the refrigerant flowing out of the outdoor heat exchanger in cooling mode. In addition, the refrigerant can release heat twice in the outdoor heat exchanger and the first heat exchanger, further increasing the subcooling degree of the refrigerant entering the indoor evaporator.

Description

Technical Field

[0001] The present disclosure relates to the technical field of air conditioning, and in particular to a heat pump air conditioning system and a vehicle using the same. Background Art

[0002] In existing vehicle heat pump air conditioning systems, during cooling operation, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor releases heat to the outside atmosphere at an outdoor heat exchanger. After being throttled and reduced in pressure by a throttle valve, the refrigerant absorbs heat from the passenger compartment in the indoor evaporator, thereby cooling the passenger compartment. Because the refrigerant must release heat to the outside atmosphere through the outdoor heat exchanger before entering the evaporator, the amount of heat exchanged between the refrigerant and the outside atmosphere in the outdoor heat exchanger is affected by the ambient temperature. For example, when the ambient temperature is high, the amount of heat released by the refrigerant to the outside atmosphere in the outdoor heat exchanger is limited, which can affect the cooling effect and efficiency of the vehicle heat pump air conditioning system. Summary of the Invention

[0003] An object of the present disclosure is to provide a heat pump air conditioning system and a vehicle using the same, so as to overcome the problems existing in the related art.

[0004] In order to achieve the above objectives, the present disclosure provides a heat pump air conditioning system, including a compressor, an outdoor heat exchanger, a first gas-liquid separation device, a first heat exchanger, a first expansion valve and an indoor evaporator.

[0005] The outlet of the compressor is connected to the first port of the outdoor heat exchanger, the second port of the outdoor heat exchanger is connected to the inlet of the first gas-liquid separation device, the liquid outlet of the first gas-liquid separation device 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.

[0006] Optionally, the heat pump air conditioning system further includes an indoor condenser, a first flow path that is selectively opened or closed, a second flow path that is selectively opened or closed, a third flow path that is selectively opened or closed, and a second expansion valve.

[0007] The outlet of the compressor is connected to the first port of the outdoor heat exchanger via the first flow path, and is connected to the inlet of the indoor condenser via the second flow path. The outlet of the indoor condenser is connected to the second port of the outdoor heat exchanger through the second expansion valve. The first port of the outdoor heat exchanger is also connected to the second refrigerant inlet of the first heat exchanger via the third flow path.

[0008] Optionally, the outlet of the indoor condenser is also connected to the inlet of the first gas-liquid separation device.

[0009] Optionally, the heat pump air-conditioning system also includes a first one-way valve and a second one-way valve, the second port of the outdoor heat exchanger is connected to the inlet of the first one-way valve, the outlet of the first one-way valve is connected to the inlet of the first gas-liquid separation device, the outlet of the indoor condenser is connected to the inlet of the second one-way valve, and the outlet of the second one-way valve is connected to the inlet of the second expansion valve and the inlet of the first gas-liquid separation device.

[0010] Optionally, the heat pump air-conditioning system also includes a second gas-liquid separation device, the first port of the outdoor heat exchanger is connected to the inlet of the second gas-liquid separation device via the third flow path, and the air outlet of the second gas-liquid separation device and the outlet of the indoor evaporator are connected to the second refrigerant inlet of the first heat exchanger.

[0011] Optionally, the heat pump air-conditioning system also includes a second heat exchanger and a third expansion valve, the first refrigerant outlet of the first heat exchanger is also 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 second refrigerant inlet of the first heat exchanger, the first coolant outlet of the second heat exchanger is used to be connected to the inlet of the vehicle's electronic device, and the first coolant inlet of the second heat exchanger is used to be connected to the outlet of the electronic device.

[0012] Optionally, the electronic device includes at least one of a motor, a charger, a motor controller, and a DC-DC converter.

[0013] Optionally, the second coolant outlet of the second heat exchanger is used to be connected to the inlet of the battery pack of the vehicle, and the second coolant inlet of the second heat exchanger is used to be connected to the outlet of the battery pack.

[0014] Optionally, the heat pump air-conditioning system also includes a second gas-liquid separation device, the first port of the outdoor heat exchanger is connected to the inlet of the second gas-liquid separation device via the third flow path, and the air outlet of the second gas-liquid separation device, the outlet of the indoor evaporator, and the refrigerant outlet of the second heat exchanger are connected to the second refrigerant inlet of the first heat exchanger.

[0015] Optionally, a first stop valve is provided on the first flow path, a second stop valve is provided on the second flow path, and a third stop valve is provided on the third flow path.

[0016] According to another aspect of the present disclosure, a vehicle is provided, comprising the above-mentioned heat pump air-conditioning system.

[0017] Compared with the technical solution in the prior art in which the refrigerant only releases heat to the outside and loses enthalpy through the outdoor heat exchanger before entering the indoor evaporator, the heat pump air-conditioning system provided by the present disclosure sets a first heat exchanger, so that the refrigerant flowing out from the second port of the outdoor heat exchanger and the refrigerant flowing out from the indoor evaporator outlet exchange heat in the first heat exchanger, so that the refrigerant flowing out from the second port of the outdoor heat exchanger further dissipates heat and cools down, that is, the refrigerant can release heat twice through the outdoor heat exchanger and the first heat exchanger before entering the indoor evaporator, solving the problem of insufficient heat release of the refrigerant at the outdoor heat exchanger due to the influence of the ambient temperature when the ambient temperature is high. In this way, the refrigerant loses more enthalpy and releases more heat before entering the indoor evaporator, which is beneficial to improving the supercooling of the refrigerant entering the indoor evaporator, and is beneficial to the refrigerant with lower temperature flowing into the indoor evaporator, so that the vehicle thermal management system provided by the present disclosure can still have good cooling effect and cooling efficiency in high temperature environment, and realize rapid cooling of the passenger compartment. In other words, by providing the first heat exchanger and allowing the refrigerant flowing out of the second port of the outdoor heat exchanger to release heat in the first heat exchanger, the problem of limited heat release of the refrigerant in the outdoor heat exchanger in a high temperature environment can be solved.

[0018] Furthermore, since the heat pump air-conditioning system provided by the present invention is provided with a first gas-liquid separation device in the flow path between the second port of the outdoor heat exchanger and the first refrigerant inlet of the first heat exchanger, the first gas-liquid separation device is used to allow the liquid refrigerant in the gas-liquid two-phase mixed refrigerant flowing out of the second port of the outdoor heat exchanger to flow into the first heat exchanger, which can increase the supercooling of the refrigerant entering the first refrigerant inlet of the first heat exchanger and increase the heat release of the refrigerant in the first heat exchanger, thereby making the temperature of the refrigerant entering the indoor evaporator lower, which is more conducive to rapid cooling of the passenger compartment.

[0019] Other features and advantages of the present disclosure will be described in detail in the following detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The accompanying drawings are used to provide a further understanding of the present disclosure and constitute a part of the specification. Together with the following detailed description, they are used to explain the present disclosure but do not constitute a limitation of the present disclosure. In the accompanying drawings:

[0021] Figure 1 is a structural diagram of a heat pump air conditioning system provided by an embodiment of the present disclosure;

[0022] Figure 2 1 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 cooling mode, and the thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode;

[0023] Figure 3 is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in cooling mode provided by one embodiment of the present disclosure;

[0024] Figure 4 2 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 cooling and battery pack cooling mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0025] Figure 5 is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in cooling and battery pack cooling modes, provided by one embodiment of the present disclosure;

[0026] Figure 6 2 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 battery pack cooling mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0027] Figure 7 is a refrigerant pressure-enthalpy diagram of a heat pump air conditioning system in a battery pack cooling mode provided by an embodiment of the present disclosure;

[0028] Figure 8 1 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 heat pump heating mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0029] Figure 9 is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in a heat pump heating mode provided by one embodiment of the present disclosure;

[0030] Figure 10 1 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 waste heat recovery heating mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0031] Figure 11 This is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in a waste heat recovery heating mode provided by an embodiment of the present disclosure;

[0032] Figure 12 1 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 heat pump heating mode with waste heat recovery. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0033] Figure 13This is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in a heat pump heating mode with waste heat recovery, provided by one embodiment of the present disclosure;

[0034] Figure 14 2 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 first dehumidification mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0035] Figure 15 is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in a first dehumidification mode provided by an embodiment of the present disclosure;

[0036] Figure 16 2 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 second dehumidification mode. The thick solid lines and arrows in the figure represent the flow paths and flow directions of the refrigerant and coolant in this mode.

[0037] Figure 17 This is a refrigerant pressure-enthalpy diagram of a heat pump air-conditioning system in a second dehumidification mode provided by an embodiment of the present disclosure.

[0038] Description of Reference Numerals

[0039] 1- compressor; 2- outdoor heat exchanger; 3- first gas-liquid separation device; 4- first heat exchanger; 5- first expansion valve; 6- indoor evaporator; 7- indoor condenser; 8- first flow path; 9- second flow path; 10- third flow path; 11- second expansion valve; 12- second gas-liquid separation device; 13- first one-way valve; 14- second one-way valve; 15- second heat exchanger; 16- first stop valve; 17- second stop valve; 18- third stop valve; 19- third expansion valve; E- first port; F- second port; A- first refrigerant inlet; B- first refrigerant outlet; C- second refrigerant inlet; D- second refrigerant outlet. DETAILED DESCRIPTION

[0040] The following describes the specific embodiments of the present disclosure in detail with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present disclosure and are not intended to limit the present disclosure.

[0041] In this disclosure, unless otherwise stated, the “connection” mentioned in this disclosure may be a direct connection between two devices or apparatuses, or may be an indirect connection.

[0042] like Figures 1 to 17As shown, the present disclosure provides a heat pump air conditioning system, including a compressor 1, an outdoor heat exchanger 2, a first gas-liquid separation device 3, a first heat exchanger 4, a first expansion valve 5, and an indoor evaporator 6. The outlet of the compressor 1 is connected to the first port E of the outdoor heat exchanger 2, the second port F of the outdoor heat exchanger 2 is connected to the inlet of the first gas-liquid separation device 3, the liquid outlet of the first gas-liquid separation device 3 is connected to the first refrigerant inlet A of the first heat exchanger 4, the first refrigerant outlet B of the first heat exchanger 4 is connected to the inlet of the indoor evaporator 6 via the first expansion valve 5, the outlet of the indoor evaporator 6 is connected to the second refrigerant inlet C of the first heat exchanger 4, and the second refrigerant outlet D of the first heat exchanger 4 is connected to the inlet of the compressor 1. In other words, through the connection relationship between the above-mentioned compressor 1, outdoor heat exchanger 2, first gas-liquid separation device 3, first heat exchanger 4, first expansion valve 5 and indoor evaporator 6, the above-mentioned heat pump air-conditioning system has a cooling mode. In the cooling mode, the gas-liquid two-phase mixed refrigerant flowing out from the second port F of the outdoor heat exchanger 2 first passes through the first gas-liquid separation device 3 for gas-liquid separation, and the liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3, thereby increasing the supercooling of the refrigerant flowing out of the first port E of the outdoor heat exchanger 2. The liquid refrigerant flowing out from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy in the first heat exchanger 4 and then enters the indoor evaporator 6. The supercooling of the refrigerant about to enter the indoor evaporator 6 can be further increased through the first heat exchanger 4, thereby improving the heat absorption capacity of the refrigerant in the indoor evaporator 6.

[0043] Specifically, in cooling mode, if Figure 2 As shown, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 outlet 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 shown in FIG. Figure 3 As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 flows into the first gas-liquid separation device 3, and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3, thereby increasing the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. 1 ). Figure 3(as indicated by arrow 400a in the figure), the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4, after losing enthalpy, passes through the first expansion valve 5 and is throttled and reduced in pressure to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. This low-temperature, low-pressure gas-liquid two-phase refrigerant absorbs heat from the air in the passenger compartment in the indoor evaporator 6, reducing the temperature inside the passenger compartment and achieving passenger compartment cooling. The refrigerant flowing out of the outlet of the indoor evaporator 6, after absorbing heat, flows into the first heat exchanger 4, where it recovers the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separator 3. The refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 ultimately returns to the compressor 1.

[0044] Compared with the technical solution in the prior art in which the refrigerant only releases heat to the outside and loses enthalpy through the outdoor heat exchanger 2 before entering the indoor evaporator 6, the heat pump air-conditioning system provided by the present disclosure sets a first heat exchanger 4, so that the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 and the refrigerant flowing out of the outlet of the indoor evaporator 6 exchange heat in the first heat exchanger 4, so that the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 further dissipates heat and cools down, that is, the refrigerant can release heat twice through the outdoor heat exchanger 2 and the first heat exchanger 4 before entering the indoor evaporator 6, solving the problem of insufficient heat release of the refrigerant at the outdoor heat exchanger 2 due to the influence of the ambient temperature when the ambient temperature is high. In this way, the refrigerant loses more enthalpy and releases more heat before entering the indoor evaporator 6, which is beneficial to improving the supercooling of the refrigerant entering the indoor evaporator 6, and is beneficial to the flow of refrigerant with lower temperature into the indoor evaporator 6, so that the vehicle thermal management system provided by the present disclosure can still have good cooling effect and cooling efficiency in a high temperature environment, thereby achieving rapid cooling of the passenger compartment. In other words, by providing the first heat exchanger 4 and allowing the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 to release heat in the first heat exchanger 4, the problem of limited heat release of the refrigerant in the outdoor heat exchanger 2 in a high temperature environment can be solved.

[0045] Furthermore, since the heat pump air-conditioning system provided by the present invention is provided with a first gas-liquid separation device 3 in the flow path between the second port F of the outdoor heat exchanger 2 and the first refrigerant inlet A of the first heat exchanger 4, the first gas-liquid separation device 3 is used to allow the liquid refrigerant in the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 to flow into the first heat exchanger 4, which can increase the supercooling of the refrigerant entering the first refrigerant inlet A of the first heat exchanger 4 and increase the heat release of the refrigerant in the first heat exchanger 4, thereby making the temperature of the refrigerant entering the indoor evaporator 6 lower, which is more conducive to rapid cooling of the passenger compartment.

[0046] Furthermore, the heat pump air conditioning system also includes an indoor condenser 7, a first flow path 8 that is selectively opened or closed, a second flow path 9 that is selectively opened or closed, a third flow path 10 that is selectively opened or closed, and a second expansion valve 11, wherein the outlet of the compressor 1 is connected to the first port E of the outdoor heat exchanger 2 via the first flow path 8, and is connected to the inlet of the indoor condenser 7 via the second flow path 9, the outlet of the indoor condenser 7 is connected to the second port F of the outdoor heat exchanger 2 via the second expansion valve 11, and the first port E of the outdoor heat exchanger 2 is also connected to the second refrigerant inlet C of the first heat exchanger 4 via the third flow path 10. By controlling the opening or closing of the first flow path 8, the second flow path 9, and the third flow path 10, the heat pump air conditioning system can be placed in cooling mode or heat pump heating mode, such as Figure 2 As shown, when the first flow path 8 is turned on and the second flow path 9 and the third flow path 10 are turned off, the above-mentioned cooling mode can be achieved; Figure 8 As shown, when the first flow path 8 is cut off and the second flow path 9 and the third flow path 10 are connected, the heat pump heating mode can be achieved.

[0047] In heat pump heating mode, the high-temperature, high-pressure gaseous refrigerant discharged from compressor 1 enters indoor condenser 7, where it releases heat and loses enthalpy to the passenger compartment, thereby raising the passenger compartment temperature and heating it. The refrigerant flowing out of indoor condenser 7 is throttled and reduced in pressure by second expansion valve 11 before flowing into outdoor heat exchanger 2 through second port F, where it absorbs heat from the outside air. The refrigerant then flows out of outdoor heat exchanger 2 through first port E, ultimately returning to compressor 1.

[0048] Here, it should be noted that, in the above-mentioned cooling mode, the refrigerant discharged from the outlet of the compressor 1 flows into the outdoor heat exchanger 2 through the first port E of the outdoor heat exchanger 2, and flows out of the outdoor heat exchanger 2 through the second port F of the outdoor heat exchanger 2, while in the above-mentioned heat pump heating mode, the refrigerant flowing out of the outlet of the indoor condenser 7 flows into the outdoor heat exchanger 2 through the second port F of the outdoor heat exchanger 2, and flows out of the outdoor heat exchanger 2 through the first port E of the outdoor heat exchanger 2. That is to say, in the cooling mode, the first port E of the outdoor heat exchanger 2 is the inlet for the inflow of refrigerant, and the second port F of the outdoor heat exchanger 2 is the outlet for the outflow of refrigerant. In the heat pump heating mode, the second port F of the outdoor heat exchanger 2 is the inlet for the inflow of refrigerant, and the first port E of the outdoor heat exchanger 2 is the outlet for the outflow of refrigerant.

[0049] The outdoor heat exchanger 2 has multiple processes (i.e., multiple heat exchange zones). When the refrigerant flows in the outdoor heat exchanger 2, it will flow through the multiple processes in sequence. The flow area of ​​each of the multiple processes is different. For example, the flow area of ​​the multiple processes can be gradually reduced in the direction from the first port E to the second port F of the outdoor heat exchanger 2. In the prior art, whether in cooling mode or heat pump heating mode, the refrigerant enters the outdoor heat exchanger 2 from the same inlet of the outdoor heat exchanger 2 and flows out of the heat exchanger from the same outlet of the outdoor heat exchanger 2. That is to say, whether in cooling mode or heat pump heating mode, the path of the refrigerant when absorbing heat (condensing) or dissipating heat (evaporating) in the outdoor heat exchanger 2 is the same, that is, the order of flowing through the multiple processes is the same. Since condensation and evaporation are opposite physical processes, the state changes of the refrigerant in the outdoor heat exchanger 2 are different in the cooling mode and the heat pump heating mode. The same flow path will cause the flow area of ​​each process to not match the state changes of the refrigerant, thereby affecting the heat exchange performance of the refrigerant in the outdoor heat exchanger 2 during condensation or evaporation.

[0050] In the present disclosure, however, since the refrigerant enters the outdoor heat exchanger 2 from different ports in the cooling mode and the heat pump heating mode, the refrigerant has different flow paths in the outdoor heat exchanger 2 in the cooling mode and the heat pump heating mode. In other words, the order of the multiple flows through which the refrigerant passes in the outdoor heat exchanger 2 is different. In this way, whether in the cooling mode or the heat pump heating mode, the change in the flow area of ​​each flow path can be adapted to the change in the state of the refrigerant in the outdoor heat exchanger 2.

[0051] For example, when the flow area of ​​multiple processes in the direction from the first port E to the second port F of the outdoor heat exchanger 2 gradually decreases, since the refrigerant releases heat and condenses in the outdoor heat exchanger 2 in the cooling mode, and changes from gas to liquid, the pressure, specific volume and flow rate of the refrigerant when entering the outdoor heat exchanger 2 are high, the specific volume is large and the flow rate is fast. The large flow area of ​​the process near the first port E of the outdoor heat exchanger 2 is conducive to more refrigerant to exchange heat through the process near the first port E of the outdoor heat exchanger 2, thereby improving the heat exchange efficiency and facilitating the refrigerant to release heat and change from gas to liquid. In the two-phase region of the refrigerant, as the refrigerant gradually changes from gas to liquid, its pressure and specific volume gradually decrease, and the flow rate decreases. The flow area of ​​the process adapts to the gradually decreasing state change of the refrigerant. That is to say, in the cooling mode, the refrigerant enters the outdoor heat exchanger 2 from the first port E of the outdoor heat exchanger 2 and flows out from the second port F, which can make the heat exchange capacity of the refrigerant more uniform and the heat release effect better when releasing heat and condensing in the outdoor heat exchanger 2. Similarly, since the refrigerant absorbs heat and evaporates in the outdoor heat exchanger 2 in the heat pump heating mode, changing from liquid to gas, the pressure, specific volume and flow rate of the refrigerant when entering the outdoor heat exchanger 2 are small. As evaporation proceeds, the pressure and specific volume of the refrigerant continue to increase, and the flow rate becomes faster. Therefore, in the hot heating mode, the refrigerant enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2 and flows out from the first port E, which is beneficial to the flow area of ​​the refrigerant continuing to increase as it changes from liquid to gas, thereby making the heat exchange capacity of the refrigerant absorbing heat and evaporating in the outdoor heat exchanger 2 more uniform and the heat absorption effect better.

[0052] Therefore, in the above-mentioned heat pump air-conditioning system provided in the present invention, since in the cooling mode, the first port E of the outdoor heat exchanger 2 is the inlet for the refrigerant to flow in, and the second port F of the outdoor heat exchanger 2 is the outlet for the refrigerant to flow out, in the heat pump heating mode, the second port F of the outdoor heat exchanger 2 is the inlet for the refrigerant to flow in, and the first port E of the outdoor heat exchanger 2 is the outlet for the refrigerant to flow out, therefore, regardless of whether it is in the cooling mode or the heat pump heating mode, the refrigerant has a good heat exchange effect in the outdoor heat exchanger 2, avoiding the heat exchange performance of the refrigerant during condensation or evaporation in the outdoor heat exchanger 2 being affected.

[0053] Optionally, to achieve selective opening or shutoff of the first flow path 8, the second flow path 9, and the third flow path 10, in one embodiment, a first shutoff valve 16 may be provided on the first flow path 8, a second shutoff valve 17 may be provided on the second flow path 9, and a third shutoff valve 18 may be provided on the third flow path 10. The first flow path 8, the second flow path 9, and the third flow path 10 are selectively opened or shutoff by opening and closing the first shutoff valve 16, the second shutoff valve 17, and the third shutoff valve 18, respectively. In another embodiment, a first on-off valve may be provided on the first flow path 8, a second on-off valve may be provided on the second flow path 9, and a third on-off valve may be provided on the third flow path 10.

[0054] Furthermore, to enable the heat pump air conditioning system provided by the present disclosure to also have a dehumidification mode and improve the functionality of the heat pump air conditioning system, in one embodiment provided by the present disclosure, the outlet of the indoor condenser 7 is also connected to the inlet of the first gas-liquid separation device 3. In this way, the refrigerant flowing out of the outlet of the indoor condenser 7 can also pass through the first gas-liquid separation device 3, the first heat exchanger 4, and the first expansion valve 5 in sequence and enter the indoor evaporator 6, thereby enabling the heat pump air conditioning system to have a dehumidification mode.

[0055] Here, the heat pump air conditioning system provided by the present disclosure can have at least two dehumidification modes. Specifically, in the first dehumidification mode, Figure 14 As shown, the first flow path 8 is cut off, the second flow path 9 is connected, the third flow path 10 is connected and the first expansion valve 5 is opened. 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. 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 from the second port F of the outdoor heat exchanger 2 after throttling and reducing the pressure through the second expansion valve 11, and absorbs heat from the external atmosphere in the outdoor heat exchanger 2. The other stream first passes through the first gas-liquid separation device 3 for gas-liquid separation. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 enters the first heat exchanger 4, and releases heat and loses enthalpy in the first heat exchanger 4. The refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 flows into the indoor evaporator 6 after throttling and reducing the pressure through the first expansion valve 5, and absorbs heat in the passenger compartment in the indoor evaporator 6. In the first dehumidification mode, the indoor condenser 7 and the indoor evaporator 6 are simultaneously activated. When the warmer, humid air in the passenger compartment encounters the cooler indoor evaporator 6, the moisture in the humid air condenses on the surface of the indoor evaporator 6, thereby reducing the humidity in the humid air. The heat released by the indoor condenser 7 to the passenger compartment balances the passenger compartment temperature and prevents the passenger compartment from becoming too cold due to the activation of the indoor evaporator 6. The refrigerant flowing out of the outlet of the indoor evaporator 6 merges with the refrigerant flowing out of the first port E of the outdoor heat exchanger 2 and flows into the first heat exchanger 4. There, the refrigerant flowing out of the liquid outlet of the first gas-liquid separator 3 recovers the enthalpy lost in the first heat exchanger 4. The refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 ultimately returns to the compressor 1.

[0056] In the second dehumidification mode, if Figure 16As shown, the first flow path 8 is cut off, the second flow path 9 is connected, the third flow path 10 is cut off and the first expansion valve 5 is opened. 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. The refrigerant flowing out of the outlet of the indoor condenser 7 passes through the first gas-liquid separation device 3, the first heat exchanger 4, and the first expansion valve 5 in sequence and enters the indoor evaporator 6, so that the humid air in the passenger compartment is condensed into condensed water on the surface of the indoor evaporator 6. The refrigerant flowing out of the outlet of the indoor evaporator 6 returns to the compressor 1 via the first heat exchanger 4.

[0057] The difference between the first dehumidification mode and the second dehumidification mode is whether the refrigerant flowing out of the indoor condenser 7 partially flows into the outdoor heat exchanger 2, absorbs the heat of the outside atmosphere during the outdoor heat exchange, and thus transports the heat in the environment. Specifically, in the first dehumidification mode, if Figure 14 As shown, part of the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2, and the other part flows into the indoor evaporator 6; and in the second dehumidification mode, as shown Figure 16 As shown, all the refrigerant flowing out of the outdoor condenser flows into the indoor evaporator 6 and does not flow through the outdoor heat exchanger 2. Since in the first dehumidification mode, a portion of the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2 and transports heat from the outside atmosphere in the outdoor heat exchanger 2, the first dehumidification mode can be applied to situations where the ambient temperature is relatively low, such as situations where the ambient temperature is less than 10°C. In the second dehumidification mode, the refrigerant does not flow through the outdoor heat exchanger 2, that is, does not transport heat from the outside atmosphere in the outdoor heat exchanger 2. Therefore, the second dehumidification mode can be applied to situations where the ambient temperature is higher than the ambient temperature applied to the first dehumidification mode, such as situations where the ambient temperature is greater than 10°C.

[0058] Optionally, the heat pump air conditioning system may further include a first one-way valve 13 and a second one-way valve 14. The second port F of the outdoor heat exchanger 2 is connected to the inlet of the first one-way valve 13, the outlet of the first one-way valve 13 is connected to the inlet of the first gas-liquid separation device 3, the outlet of the indoor condenser 7 is connected to the inlet of the second one-way valve 14, and the outlet of the second one-way valve 14 is connected to the inlet of the second expansion valve 11 and the inlet of the first gas-liquid separation device 3. In this way, in the heat pump heating mode, the first dehumidification mode, the second dehumidification mode, and the waste heat recovery heating mode and the heat pump heating mode with waste heat recovery mentioned below, the refrigerant can be prevented from directly flowing back from the inlet of the first gas-liquid separation device 3 to the outdoor heat exchanger 2. In the cooling mode, the battery pack cooling mode, and the cooling and battery pack cooling mode mentioned below, the second one-way valve 14 can prevent the refrigerant at the inlet of the first gas-liquid separation device 3 from flowing back to the indoor condenser 7.

[0059] Optionally, the heat pump air conditioning system may further include a second gas-liquid separation device 12. The first port E of the outdoor heat exchanger 2 is connected to the inlet of the second gas-liquid separation device 12 via the third flow path 10. The gas outlet of the second gas-liquid separation device 12 and the outlet of the indoor evaporator 6 are connected to the second refrigerant inlet C of the first heat exchanger 4. In this way, the gas-liquid two-phase mixed refrigerant flowing out of the first port E of the outdoor heat exchanger 2 is first separated into gas and liquid by the second gas-liquid separation device 12, and the gaseous refrigerant flows into the first heat exchanger 4.

[0060] Since the gaseous refrigerant separated by the second gas-liquid separation device 12 may carry a small amount of liquid droplets, if the gaseous refrigerant separated by the second gas-liquid separation device 12 is directly returned to the compressor 1, the small amount of liquid droplets carried in the gaseous refrigerant may cause liquid hammer in the compressor 1. In this case, it is necessary to control the superheat of the refrigerant at the inlet of the compressor 1 so that the superheat of the refrigerant at the inlet of the compressor 1 is 0, that is, the refrigerant at the inlet of the compressor 1 is located on the saturated vapor line of the refrigerant, thereby avoiding liquid hammer caused by the refrigerant to the compressor 1. However, the superheat control of the refrigerant is bound to increase the control complexity of the heat pump air-conditioning system.

[0061] In the present disclosure, the gas outlet of the second gas-liquid separation device 12 is connected to the second refrigerant inlet C of the first heat exchanger 4. That is, the gaseous refrigerant flowing out of the gas outlet of the second gas-liquid separation device 12 first passes through the first heat exchanger 4 before returning to the compressor 1. In the first heat exchanger 4, the refrigerant flowing into the first heat exchanger 4 from the second refrigerant inlet C of the first heat exchanger 4 absorbs heat from the refrigerant flowing into the first refrigerant inlet A of the first heat exchanger 4. That is, the gaseous refrigerant flowing out of the gas outlet of the second gas-liquid separation device 12 can absorb heat in the first heat exchanger 4 before returning to the compressor 1, so that the small amount of liquid refrigerant carried in the gaseous refrigerant can evaporate into gaseous refrigerant, thereby allowing the refrigerant about to enter the compressor 1 to pass through the saturated vapor line and become pure gas. Therefore, there is no need to control the superheat of the refrigerant about to enter the compressor 1, thereby reducing the control complexity of the heat pump air conditioning system. In other words, as long as refrigerant flows into both the first refrigerant inlet A and the second refrigerant inlet C of the first heat exchanger 4 (for example, in cooling mode, battery pack cooling mode, cooling and battery pack cooling mode, first dehumidification mode, second dehumidification mode, waste heat recovery heating mode, heat pump with waste heat recovery heating mode), there is no need to control the superheat of the refrigerant about to enter the inlet of the compressor 1.

[0062] When the outdoor ambient temperature is low, the heat that the refrigerant can absorb at the outdoor heat exchanger 2 is insufficient, which can easily affect the heat release effect of the refrigerant at the indoor condenser 7 and affect the heating capacity of the passenger compartment. In order to enable the heat pump air-conditioning system to achieve the passenger compartment heating function without transporting external heat through the outdoor heat exchanger 2, in one embodiment provided in the present disclosure, the heat pump air-conditioning system also includes a second heat exchanger 15 and a third expansion valve 19, and the first refrigerant outlet B of the first heat exchanger 4 is also connected to the refrigerant inlet of the second heat exchanger 15 via the third expansion valve 19, and the refrigerant outlet of the second heat exchanger 15 is connected to the second refrigerant inlet C of the first heat exchanger 4, and the first coolant outlet of the second heat exchanger 15 is used to be connected to the inlet of the vehicle's electronic device, and the first coolant inlet of the second heat exchanger 15 is used to be connected to the outlet of the electronic device.

[0063] By opening the third expansion valve 19, closing both the first flow path 8 and the third flow path 10, and connecting the second flow path 9, the heat pump air conditioning system provided by the present disclosure can have a waste heat recovery heating mode. In this waste heat recovery heating mode, the refrigerant transports the heat emitted by the electronic device to heat the passenger compartment. Specifically, in the waste heat recovery heating mode, Figure 10 As shown, the refrigerant flowing out from the outlet of the indoor condenser 7 enters the first heat exchanger 4 through the first gas-liquid separation device 3, and releases heat and loses enthalpy in the first heat exchanger 4. The refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 is throttled and reduced in pressure by the third expansion valve 19 and then flows into the second heat exchanger 15. The refrigerant absorbs the heat of the high-temperature coolant after absorbing heat at the electronic components in the second heat exchanger 15, thereby recovering the heat dissipated when the electronic components are working to the heat pump air-conditioning system. The refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15 after absorbing heat absorbs the heat of the refrigerant flowing into the first heat exchanger 4 from the first gas-liquid separation device 3 again in the first heat exchanger 4 and then returns to the compressor 1.

[0064] By opening the third expansion valve 19 and closing the first flow path 8, and connecting the second flow path 9 and the third flow path 10, the heat pump air conditioning system provided by the present disclosure can have a heat pump with waste heat recovery heating mode. In this mode, the refrigerant transports the heat emitted by the electronic components and the heat in the external environment to heat the passenger compartment. Specifically, in the heat pump with waste heat recovery heating mode, if Figure 12 As shown, the refrigerant flowing out from the outlet of the indoor condenser 7 is divided into two streams, one stream flows into the outdoor heat exchanger 2 to absorb heat from the external environment, and the other stream flows into the second heat exchanger 15 through the first gas-liquid separation device 3, the first heat exchanger 4, and the third expansion valve 19, and absorbs the heat emitted by the electronic devices in the second heat exchanger 15, thereby achieving the purpose of transporting the heat emitted by the electronic devices and the heat in the external environment to heat the passenger compartment.

[0065] It should be noted that the aforementioned electronic components refer to components that require electricity to operate and generate heat during operation. For example, the electronic components may include at least one of a motor, a charger, a motor controller, and a DC-DC converter. When a heat pump air conditioning system is used in an electric vehicle, while the battery pack is charging, the charger, DC-DC converter, and other components will dissipate heat due to their operation. In other words, the charger, DC-DC converter, and other components require heat dissipation. If the passenger compartment requires heating at this time, the heat pump air conditioning system can be operated in a waste heat recovery heating mode or a heat pump heating mode with waste heat recovery. This allows the heat from the charger, DC-DC converter, and other components to be recovered into the heat pump air conditioning system while the heat dissipation requirements of the charger, DC-DC converter, and other components are met, thereby improving the heating capacity of the heat pump air conditioning system. When an electric vehicle is in motion, the motor converts the electrical energy of the battery pack into mechanical energy to drive the vehicle. The motor will emit heat. If the passenger compartment needs heating at this time, the heat pump air-conditioning system can be put into waste heat recovery heating mode or heat pump with waste heat recovery heating mode, so as to achieve motor heat dissipation cooling while recovering the heat of the motor into the heat pump air-conditioning system.

[0066] In the field of electric vehicle technology, vehicle manufacturers strive to continuously shorten the charging time of battery packs 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.

[0067] In order to meet the requirement that the battery pack needs to be quickly cooled during fast charging, the second coolant outlet of the second heat exchanger 15 can be used to connect to the inlet of the vehicle's battery pack, and the second coolant inlet of the second heat exchanger 15 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.

[0068] Specifically, if Figure 6 As shown, by opening the third expansion valve 19, connecting the first flow path 8, and closing the second flow path 9 and the third flow path 10, the heat pump air conditioning system provided by the present disclosure can be made to have a battery pack cooling mode. In this mode, 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 shown in FIG. Figure 7As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 flows into the first gas-liquid separation device 3, and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3, thereby increasing the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. 1 ). Figure 7 As shown by arrow 400a in the figure, the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4, after losing enthalpy, passes through the third expansion valve 19 and is throttled and reduced in pressure to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. This low-temperature, low-pressure gas-liquid two-phase refrigerant flows into the second heat exchanger 15, where it absorbs heat from the high-temperature coolant that has absorbed heat from the battery pack. This allows the second coolant outlet of the second heat exchanger 15 to flow out low-temperature coolant that has absorbed heat from the battery pack, thereby achieving the purpose of using the refrigerant of the heat pump air conditioning system to cool the battery pack. The refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15, after absorbing heat, flows into the first heat exchanger 4, where it recovers the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separator 3. The refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 ultimately returns to the compressor 1.

[0069] Because the refrigerant in the battery pack cooling mode provided by the present disclosure releases heat twice through the outdoor heat exchanger 2 and the first heat exchanger 4 before entering the second heat exchanger 15, this helps increase the supercooling of the refrigerant entering the second heat exchanger 15. The higher the supercooling, the more heat the refrigerant absorbs in the second heat exchanger 15, resulting in a lower coolant temperature. The lower the coolant temperature, the more conducive to rapid cooling of the battery pack. Furthermore, because the heat pump air conditioning system provided by the present disclosure is provided with a first gas-liquid separator 3 in the flow path between the second port F of the outdoor heat exchanger 2 and the first refrigerant inlet A of the first heat exchanger 4, the first gas-liquid separator 3 is used to allow the liquid refrigerant in the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 to flow into the first heat exchanger 4. This can increase the supercooling of the refrigerant entering the first refrigerant inlet A of the first heat exchanger 4, increase the amount of heat released by the refrigerant in the first heat exchanger 4, and thus lower the temperature of the refrigerant entering the second heat exchanger 15.

[0070] When the battery pack needs to be cooled and the passenger compartment needs to be cooled, the first expansion valve 5 can be opened on the basis of the battery pack coolant mode, so as to realize the cooling and battery pack cooling mode. Figure 5As shown, the refrigerant flowing out from the first refrigerant outlet B of the first heat exchanger 4 is divided into two streams. One stream enters the indoor evaporator 6 after throttling and reducing the pressure through the first expansion valve 5, absorbs the heat of the passenger compartment, and realizes the cooling of the passenger compartment. The other stream enters the second heat exchanger 15 after throttling and reducing the pressure through the third expansion valve 19, absorbs the heat of the battery pack, and realizes the cooling of the battery pack.

[0071] Optionally, the heat pump air conditioning system may further include a second gas-liquid separation device 12. The first port E of the outdoor heat exchanger 2 is connected to the inlet of the second gas-liquid separation device 12 via the third flow path 10. The gas outlet of the second gas-liquid separation device 12, the outlet of the indoor evaporator 6, and the refrigerant outlet of the second heat exchanger 15 are connected to the second refrigerant inlet C of the first heat exchanger 4. In this way, in cooling mode, battery pack cooling mode, cooling and battery pack cooling mode, first dehumidification mode, second dehumidification mode, waste heat recovery heating mode, and heat pump heating mode with waste heat recovery, the gaseous refrigerant flowing out of the outlet of the second gas-liquid separation device 12 can absorb heat in the first heat exchanger 4 before returning to the compressor 1. This allows the small amount of liquid refrigerant carried in the gaseous refrigerant to evaporate into gaseous refrigerant, thereby allowing the refrigerant about to enter the compressor 1 to pass through the saturated vapor line and become pure gas. This eliminates the need for superheat control of the refrigerant about to enter the compressor 1, thereby reducing the control complexity of the heat pump air conditioning system.

[0072] The following will Figure 1 As an example, combined with Figures 2 to 17 To describe the circulation process and principle of the heat pump air conditioning system provided by the present invention under the main working mode.

[0073] For ease of understanding, before describing the main working modes of the heat pump air conditioning system provided by the present disclosure, for example, Figure 2 The pressure-enthalpy diagram shown in the figure is used to illustrate this. In this pressure-enthalpy diagram, the horizontal axis represents the enthalpy of the refrigerant, which increases gradually from the left end to the right end of the horizontal axis. The vertical axis represents the pressure of the refrigerant, and the pressure increases gradually from the bottom end to the top end of the vertical axis. 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, where the refrigerant is in a liquid state; the right side of the saturated vapor line is the superheated vapor region, where the refrigerant is in a gaseous state; the region between the saturated liquid line and the saturated vapor line is the wet vapor region, i.e., the gas-liquid coexistence region, where the refrigerant is in a gas-liquid two-phase mixed state.

[0074] Mode 1: Cooling mode. In this mode, if Figure 2 As shown, the first stop valve 16 is open, the second stop valve 17 is closed, the third stop valve 18 is closed, the first expansion valve 5 is open, the second expansion valve 11 is closed, and the third expansion valve 19 is closed. Figure 2 and Figure 3As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 3 As shown by the arrow 100 in the figure, the high temperature and high pressure gaseous refrigerant enters the outdoor heat exchanger 2 and releases heat to the outside atmosphere in the outdoor heat exchanger 2, losing enthalpy (as shown in the figure). Figure 3 As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 flows into the first gas-liquid separation device 3 and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in the figure). Figure 3 300 in the figure), thereby increasing the subcooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separator 3 flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separator 3 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. Figure 3 As shown by the arrow 400a in the figure), the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in equal enthalpy pressure in the first expansion valve 5 and passes through the saturated liquid line (as shown in the figure). Figure 3 As shown by the arrow 500 in the figure, it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure of the first expansion valve 5. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the air in the passenger compartment in the indoor evaporator 6 and obtains enthalpy (as shown in the figure). Figure 3 The refrigerant flowing out of the indoor evaporator 6 after absorbing heat flows into the first heat exchanger 4, and in the first heat exchanger 4, the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 is obtained (as shown in the arrow 600 in the figure). Figure 3 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0075] Mode 2: Refrigeration and battery pack cooling mode. In this mode, if Figure 4 As shown, the first stop valve 16 is open, the second stop valve 17 is closed, the third stop valve 18 is closed, the first expansion valve 5 is open, the second expansion valve 11 is closed, and the third expansion valve 19 is open. Figure 4 and Figure 5 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 5As shown by the arrow 100 in the figure, the high temperature and high pressure gaseous refrigerant enters the outdoor heat exchanger 2 and releases heat to the outside atmosphere in the outdoor heat exchanger 2, losing enthalpy (as shown in the figure). Figure 5 As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 flows into the first gas-liquid separation device 3 and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in the figure). Figure 5 300 in the figure), thereby increasing the subcooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separator 3 flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separator 3 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. Figure 5 As shown by the arrow 400a in the figure, the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 is divided into two streams, one of which drops in equal enthalpy pressure in the first expansion valve 5 and passes through the saturated liquid line (as shown in the figure). Figure 5 As shown by the arrow 500 in the figure, it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure of the first expansion valve 5. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the air in the passenger compartment in the indoor evaporator 6 and obtains enthalpy (as shown in the figure). Figure 5 As shown by the arrow 600 in the figure, the temperature in the passenger compartment is reduced to achieve refrigeration of the passenger compartment; the other stream has an equal enthalpy pressure drop in the third expansion valve 19 and passes through the saturated liquid line (as shown in the figure). Figure 5 As shown by the arrow 190 in the figure, it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure through the third expansion valve 19. 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 15 and obtains enthalpy (as shown in FIG. Figure 5 As shown by the arrow 150 in the figure, the second coolant outlet of the second heat exchanger 15 flows out a low-temperature coolant, which can be used to cool the battery pack, thereby achieving the purpose of using the cooling capacity of the refrigerant to cool the battery pack. The refrigerant after absorbing heat from the outlet of the indoor evaporator 6 and the refrigerant after absorbing heat from the refrigerant outlet of the second heat exchanger 15 merge and flow into the first heat exchanger 4, and the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 is obtained in the first heat exchanger 4 (as shown in the figure). Figure 5 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0076] Mode 3: Battery pack cooling mode. In this mode, if Figure 6As shown, the first stop valve 16 is open, the second stop valve 17 is closed, the third stop valve 18 is closed, the first expansion valve 5 is closed, the second expansion valve 11 is closed, and the third expansion valve 19 is open. Figure 6 and Figure 7 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 7 As shown by the arrow 100 in the figure, the high temperature and high pressure gaseous refrigerant enters the outdoor heat exchanger 2 and releases heat to the outside atmosphere in the outdoor heat exchanger 2, losing enthalpy (as shown in the figure). Figure 7 As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 flows into the first gas-liquid separation device 3 and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in the figure). Figure 7 300 in the figure), thereby increasing the subcooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separator 3 flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separator 3 loses enthalpy again, and the enthalpy value is further reduced (as shown in FIG. Figure 7 As shown by the arrow 400a in the figure, the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in the equal enthalpy pressure in the third expansion valve 19 and passes through the saturated liquid line (as shown in the figure). Figure 7 As shown by the arrow 190 in the figure, it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure through the third expansion valve 19. 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 15 and obtains enthalpy (as shown in FIG. Figure 7 As shown by the arrow 150 in the figure, the second coolant outlet of the second heat exchanger 15 flows out a low-temperature coolant, which can be used to cool the battery pack, thereby achieving the purpose of using the cooling capacity of the refrigerant to cool the battery pack. The refrigerant that has absorbed heat and flows out of the refrigerant outlet of the second heat exchanger 15 flows into the first heat exchanger 4, and obtains the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 in the first heat exchanger 4 (as shown in the figure). Figure 7 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0077] Mode 4: Heat pump heating mode. In this mode, if Figure 8 As shown, the first stop valve 16 is closed, the second stop valve 17 is opened, the third stop valve 18 is opened, the first expansion valve 5 is closed, the second expansion valve 11 is opened, and the third expansion valve 19 is closed. Figure 8 and Figure 9 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 9 As shown by the arrow 100 in the 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, losing enthalpy (as shown in the figure). Figure 9 The refrigerant flowing out of the outlet of the indoor condenser 7 drops in equal enthalpy pressure in the second expansion valve 11 and passes through the saturated liquid line (as shown by the arrow 700 in the figure) to increase the temperature of the passenger compartment and realize heating of the passenger compartment. Figure 9 As shown by the arrow 110 in the figure, the refrigerant after throttling and reducing pressure through the second expansion valve 11 enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2, and absorbs heat from the external environment in the outdoor heat exchanger 2 and obtains enthalpy (as shown in FIG. Figure 9 As shown by the arrow 200 in the figure), the gas-liquid two-phase mixed refrigerant after absorbing heat from the first port E of the outdoor heat exchanger 2 is separated into gaseous refrigerant and liquid refrigerant in the second gas-liquid separation device 12. The gaseous refrigerant (as shown in FIG. Figure 9 The refrigerant gas flows through the first heat exchanger 4 and returns to the compressor 1 (as shown by point 120 in FIG1 ). In the heat pump heating mode, no refrigerant flows into the first refrigerant inlet A of the first heat exchanger 4. Therefore, the gaseous refrigerant flowing out of the gas outlet of the second gas-liquid separation device 12 does not exchange heat in the first heat exchanger 4. That is, in this mode, the first heat exchanger 4 serves as a flow passage.

[0078] Mode 5: Waste heat recovery heating mode. In this mode, if Figure 10 As shown, the first stop valve 16 is closed, the second stop valve 17 is open, the third stop valve 18 is closed, the first expansion valve 5 is closed, the second expansion valve 11 is closed, and the third expansion valve 19 is open. Figure 10 and Figure 11 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 11 As shown by the arrow 100 in the 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, losing enthalpy (as shown in the figure). Figure 11 The gas-liquid two-phase mixed refrigerant flows out of the outlet of the indoor condenser 7 and flows into the first gas-liquid separation device 3, where it is separated into gaseous refrigerant and liquid refrigerant. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown by the arrow 700). Figure 11As shown by point 300 in the figure, the liquid refrigerant flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown by point 300 in the figure). Figure 11 As shown by the arrow 400a in the figure, the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in the equal enthalpy pressure in the third expansion valve 19 and passes through the saturated liquid line (as shown in the figure). Figure 11 As shown by the arrow 190 in the figure, the low-temperature and low-pressure gas-liquid two-phase refrigerant is converted into a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure by the third expansion valve 19. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature coolant after absorbing heat from the electronic device in the third heat exchanger and obtains enthalpy (as shown in FIG. Figure 11 The heat released by the electronic device during operation is recovered into the heat pump air conditioning system, and the heat of the electronic device is used to heat the passenger compartment. The refrigerant flowing out of the outlet of the third heat exchanger after absorbing heat flows into the first heat exchanger 4, and the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 is obtained in the first heat exchanger 4 (as shown in FIG. Figure 11 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0079] Mode 6: Heat pump with waste heat recovery heating mode. In this mode, if Figure 12 As shown, the first stop valve 16 is closed, the second stop valve 17 is open, the third stop valve 18 is open, the first expansion valve 5 is closed, the second expansion valve 11 is open, and the third expansion valve 19 is open. Figure 12 and Figure 13 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 13 As shown by the arrow 100 in the 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, losing enthalpy (as shown in the figure). Figure 13 The refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams. One stream drops in pressure at the same enthalpy in the second expansion valve 11 and passes through the saturated liquid line (as shown by the arrow 700 in the figure). Figure 13 As shown by the arrow 110 in the figure, the refrigerant after throttling and reducing pressure through the second expansion valve 11 enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2, and absorbs heat from the external environment in the outdoor heat exchanger 2 and obtains enthalpy (as shown in FIG. Figure 13As shown by the arrow 200 in the figure), the other flows into the first gas-liquid separation device 3 and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in FIG. Figure 13 As shown by point 300 in the figure, the liquid refrigerant flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown by point 300 in the figure). Figure 13 As shown by the arrow 400a in the figure, the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in the equal enthalpy pressure in the third expansion valve 19 and passes through the saturated liquid line (as shown in the figure). Figure 13 As shown by the arrow 190 in the figure, the low-temperature and low-pressure gas-liquid two-phase refrigerant is converted into a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure by the third expansion valve 19. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature coolant after absorbing heat from the electronic device in the third heat exchanger and obtains enthalpy (as shown in FIG. Figure 13 The heat dissipated by the electronic device during operation is recovered into the heat pump air conditioning system. The gas-liquid two-phase mixed refrigerant after absorbing heat and flowing out of the first port E of the outdoor heat exchanger 2 is separated into gaseous refrigerant and liquid refrigerant in the second gas-liquid separation device 12. The gas outlet of the second gas-liquid separation device 12 flows out the gaseous refrigerant (as shown in FIG. Figure 13 The gaseous refrigerant and the gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the third heat exchanger merge and flow into the first heat exchanger 4, and obtain the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 in the first heat exchanger 4 (as shown in FIG. Figure 13 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0080] Mode 7: First dehumidification mode. In this mode, Figure 14 As shown, the first stop valve 16 is closed, the second stop valve 17 is open, the third stop valve 18 is open, the first expansion valve 5 is open, the second expansion valve 11 is open, and the third expansion valve 19 is closed. Figure 14 and Figure 15 As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 15 As shown by the arrow 100 in the 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, losing enthalpy (as shown in the figure). Figure 15The refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams. One stream drops in pressure at the second expansion valve 11 and passes through the saturated liquid line (as shown by the arrow 700 in FIG. 1 ). Figure 15 As shown by the arrow 110 in the figure, the refrigerant after throttling and reducing pressure through the second expansion valve 11 enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2, and absorbs heat from the external environment in the outdoor heat exchanger 2 and obtains enthalpy (as shown in FIG. Figure 15 As shown by the arrow 200 in the figure), the other flows into the first gas-liquid separation device 3 and is separated into gaseous refrigerant and liquid refrigerant in the first gas-liquid separation device 3. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in FIG. Figure 15 As shown by point 300 in the figure, the liquid refrigerant flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown by point 300 in the figure). Figure 15 As shown by the arrow 400a in the figure), the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in equal enthalpy pressure in the first expansion valve 5 and passes through the saturated liquid line (as shown in the figure). Figure 15 As shown by the arrow 500 in the figure), it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure of the first expansion valve 5. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat and obtains enthalpy in the indoor evaporator 6 (as shown in the figure). Figure 15 The humid air in the passenger compartment is condensed into condensed water on the surface of the indoor evaporator 6, thereby achieving the purpose of dehumidifying the passenger compartment. The gas-liquid two-phase mixed refrigerant after absorbing heat and flowing out of the first port E of the outdoor heat exchanger 2 is separated into gaseous refrigerant and liquid refrigerant in the second gas-liquid separation device 12. The gas outlet of the second gas-liquid separation device 12 flows out the gaseous refrigerant (as shown in FIG. Figure 15 The gaseous refrigerant and the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the indoor evaporator 6 merge and flow into the first heat exchanger 4, and obtain the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 in the first heat exchanger 4 (as shown in FIG. Figure 15 As shown by arrow 400b in FIG, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0081] Mode 8: Second dehumidification mode. In this mode, Figure 16 As shown, the first stop valve 16 is closed, the second stop valve 17 is open, the third stop valve 18 is closed, the first expansion valve 5 is open, the second expansion valve 11 is closed, and the third expansion valve 19 is closed. Figure 15 and Figure 16As shown, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (such as Figure 16 As shown by the arrow 100 in the 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, losing enthalpy (as shown in the figure). Figure 16 The liquid refrigerant flows out from the outlet of the indoor condenser 7 and flows into the first gas-liquid separation device 3, where it is separated into gaseous refrigerant and liquid refrigerant. The liquid refrigerant flows out from the liquid outlet of the first gas-liquid separation device 3 (as shown in FIG. Figure 16 As shown by point 300 in the figure, the liquid refrigerant flows into the first heat exchanger 4 through the first refrigerant inlet A of the first heat exchanger 4, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 4 in the first heat exchanger 4. The refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 loses enthalpy again, and the enthalpy value is further reduced (as shown by point 300 in the figure). Figure 16 As shown by the arrow 400a in the figure), the refrigerant after losing enthalpy flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in equal enthalpy pressure in the first expansion valve 5 and passes through the saturated liquid line (as shown in the figure). Figure 16 As shown by the arrow 500 in the figure), it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant after throttling and reducing the pressure of the first expansion valve 5. The low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat and obtains enthalpy in the indoor evaporator 6 (as shown in the figure). Figure 16 As shown by the arrow 600 in the figure, the humid air in the passenger compartment condenses into condensed water on the surface of the indoor evaporator 6, thereby achieving the purpose of dehumidifying the passenger compartment. The refrigerant flowing out of the outlet of the indoor evaporator 6 flows into the first heat exchanger 4, and obtains the enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3 in the first heat exchanger 4 (as shown in the figure). Figure 16 As shown by arrow 400b, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 eventually returns to the compressor 1.

[0082] It should be noted that the above-mentioned modes are the main working modes of the vehicle thermal management system provided by this disclosure. Working modes not mentioned in this disclosure but that can be achieved by the vehicle thermal management system provided by this disclosure also fall within the scope of protection of this disclosure.

[0083] According to another aspect of the present disclosure, a vehicle is provided, comprising the above-mentioned heat pump air-conditioning system.

[0084] The preferred embodiments of the present disclosure are described in detail above in conjunction with the accompanying drawings. However, the present disclosure is not limited to the specific details of the above embodiments. Within 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 scope of protection of the present disclosure.

[0085] It should also be noted that the various specific technical features described in the above specific embodiments can be combined in any appropriate manner without contradiction. In order to avoid unnecessary repetition, the present disclosure will not further describe various possible combinations.

[0086] In addition, the various embodiments of the present disclosure may be arbitrarily combined, and as long as they do not violate the concept of the present disclosure, they should also be regarded as the contents disclosed by the present disclosure.

Claims

1. A heat pump air conditioning system, characterized in that: It comprises a compressor (1), an outdoor heat exchanger (2), a first gas-liquid separation device (3), a first heat exchanger (4), a first expansion valve (5) and an indoor evaporator (6), The outlet of the compressor (1) is connected to the first port (E) of the outdoor heat exchanger (2), the second port (F) of the outdoor heat exchanger (2) is connected to the inlet of the first gas-liquid separation device (3), the liquid outlet of the first gas-liquid separation device (3) is connected to the first refrigerant inlet (A) of the first heat exchanger (4), the first refrigerant outlet (B) of the first heat exchanger (4) is connected to the inlet of the indoor evaporator (6) via the first expansion valve (5), the outlet of the indoor evaporator (6) is connected to the second refrigerant inlet (C) of the first heat exchanger (4), and the second refrigerant outlet (D) of the first heat exchanger (4) is connected to the inlet of the compressor (1); The heat pump air conditioning system further comprises an indoor condenser (7), a first flow path (8) that is selectively opened or closed, a second flow path (9) that is selectively opened or closed, a third flow path (10) that is selectively opened or closed, and a second expansion valve (11), wherein a first on-off valve is provided on the first flow path (8), a second on-off valve is provided on the second flow path (9), and a third on-off valve is provided on the third flow path (10); The outlet of the compressor (1) is connected to the first port (E) of the outdoor heat exchanger (2) via the first flow path (8), and is connected to the inlet of the indoor condenser (7) via the second flow path (9). The outlet of the indoor condenser (7) is connected to the second port (F) of the outdoor heat exchanger (2) via the second expansion valve (11). The first port (E) of the outdoor heat exchanger (2) is also connected to the second refrigerant inlet (C) of the first heat exchanger (4) via the third flow path (10). The outlet of the indoor condenser (7) is also connected to the inlet of the first gas-liquid separation device (3); the heat pump air-conditioning system also includes a second heat exchanger (15) and a third expansion valve (19), the first refrigerant outlet (B) of the first heat exchanger (4) is also connected to the refrigerant inlet of the second heat exchanger (15) via the third expansion valve (19), the refrigerant outlet of the second heat exchanger (15) is connected to the second refrigerant inlet (C) of the first heat exchanger (4), the first coolant outlet of the second heat exchanger (15) is used to be connected to the inlet of the vehicle's electronic device, and the first coolant inlet of the second heat exchanger (15) is used to be connected to the outlet of the electronic device.

2. The heat pump air conditioning system according to claim 1, characterized in that: The heat pump air-conditioning system further comprises a first one-way valve (13) and a second one-way valve (14); the second port (F) of the outdoor heat exchanger (2) is connected to the inlet of the first one-way valve (13); the outlet of the first one-way valve (13) is connected to the inlet of the first gas-liquid separation device (3); the outlet of the indoor condenser (7) is connected to the inlet of the second one-way valve (14); and the outlet of the second one-way valve (14) is connected to the inlet of the second expansion valve (11) and the inlet of the first gas-liquid separation device (3).

3. The heat pump air conditioning system according to any one of claims 1-2, characterized in that: The heat pump air conditioning system further includes a second gas-liquid separation device (12), the first port (E) of the outdoor heat exchanger (2) is connected to the inlet of the second gas-liquid separation device (12) via the third flow path (10), and the gas outlet of the second gas-liquid separation device (12) and the outlet of the indoor evaporator (6) are connected to the second refrigerant inlet (C) of the first heat exchanger (4).

4. The heat pump air conditioning system according to claim 1, characterized in that: The electronic device includes at least one of a motor, a charger, a motor controller, and a DC-DC converter.

5. The heat pump air conditioning system according to claim 1, characterized in that: The second coolant outlet of the second heat exchanger (15) is used to be connected to the inlet of the battery pack of the vehicle, and the second coolant inlet of the second heat exchanger (15) is used to be connected to the outlet of the battery pack.

6. The heat pump air conditioning system according to any one of claims 1, 4 and 5, characterized in that: The heat pump air conditioning system further includes a second gas-liquid separation device (12), the first port (E) of the outdoor heat exchanger (2) is connected to the inlet of the second gas-liquid separation device (12) via the third flow path (10), and the gas outlet of the second gas-liquid separation device (12), the outlet of the indoor evaporator (6), and the refrigerant outlet of the second heat exchanger (15) are connected to the second refrigerant inlet (C) of the first heat exchanger (4).

7. A vehicle, characterized in that: A heat pump air conditioning system comprising the heat pump air conditioning system according to any one of claims 1 to 6.

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