CN114683810A

CN114683810A - Heat pump air conditioning system and vehicle

Info

Publication number: CN114683810A
Application number: CN202011630354.6A
Authority: CN
Inventors: 尤古塔纳·贝努利
Original assignee: Mind Electronics Appliance Co Ltd
Current assignee: Mind Electronics Appliance Co Ltd
Priority date: 2020-12-31
Filing date: 2020-12-31
Publication date: 2022-07-01

Abstract

The utility model relates to a heat pump air conditioning system and vehicle, this system includes the compressor, outdoor heat exchanger, first gas-liquid separation device, first heat exchanger, first expansion valve and indoor evaporimeter, the export of compressor and the first mouth connection of outdoor heat exchanger, the second mouth of outdoor heat exchanger and the entry linkage of first gas-liquid separation device, the liquid outlet of first gas-liquid separation device and the first refrigerant entry linkage of first heat exchanger, the first refrigerant export of first heat exchanger is via the entry linkage of first expansion valve with indoor evaporimeter, the export of indoor evaporimeter and the second refrigerant entry linkage of first heat exchanger, the second refrigerant export of first heat exchanger and the entry linkage of compressor. Liquid refrigerants flow out of a liquid outlet of the first gas-liquid separation device, and the supercooling degree of the refrigerants flowing out of the outdoor heat exchanger in the refrigeration mode can be improved; in addition, the refrigerant can release heat twice in the outdoor heat exchanger and the first heat exchanger, and the supercooling degree of the refrigerant entering the indoor evaporator is further improved.

Description

Heat pump air conditioning system and vehicle

Technical Field

The present disclosure relates to the field of air conditioning technology, and in particular, to a heat pump air conditioning system and a vehicle using the same.

Background

In the refrigeration working condition of the existing vehicle heat pump air-conditioning system, high-temperature and high-pressure gaseous refrigerant discharged by a compressor releases heat to the outside atmosphere at an outdoor heat exchanger, and the refrigerant after heat release absorbs the heat of a passenger compartment in an indoor evaporator after being throttled and depressurized by a throttle valve, so that the effect of cooling the passenger compartment is realized. Because the refrigerant needs to release heat to the outside atmosphere through the outdoor heat exchanger before entering the evaporator, the heat exchange amount of the refrigerant and the outside atmosphere in the outdoor heat exchanger can be influenced by the ambient temperature, for example, when the outside ambient temperature is higher, the heat release amount of the refrigerant to the outside atmosphere in the outdoor heat exchanger is limited, so that the refrigeration effect and the refrigeration efficiency of the vehicle heat pump air-conditioning system can be influenced.

Disclosure of Invention

An object of the present disclosure is to provide a heat pump air conditioning system and a vehicle using the same to overcome the problems in the related art.

In order to achieve the above objects, the present disclosure provides a heat pump air conditioning system including a compressor, an outdoor heat exchanger, a first gas-liquid separating device, a first heat exchanger, a first expansion valve, and an indoor evaporator,

the outlet of the compressor is connected with the first port of the outdoor heat exchanger, the second port of the outdoor heat exchanger is connected with the inlet of the first gas-liquid separating device, the liquid outlet of the first gas-liquid separating device is connected with the first refrigerant inlet of the first heat exchanger, the first refrigerant outlet of the first heat exchanger is connected with the inlet of the indoor evaporator through the first expansion valve, the outlet of the indoor evaporator is connected with the second refrigerant inlet of the first heat exchanger, and the second refrigerant outlet of the first heat exchanger is connected with the inlet of the compressor.

Optionally, the heat pump air conditioning system further comprises an indoor condenser, a first flow path selectively opened or closed, a second flow path selectively opened or closed, a third flow path selectively opened or closed, and a second expansion valve,

an outlet of the compressor is connected with a first port of the outdoor heat exchanger through the first flow path and is connected with an inlet of the indoor condenser through the second flow path, an outlet of the indoor condenser is connected with a second port of the outdoor heat exchanger through the second expansion valve, and the first port of the outdoor heat exchanger is also connected with a second refrigerant inlet of the first heat exchanger through the third flow path.

Optionally, the outlet of the indoor condenser is further connected to the inlet of the first gas-liquid separation device.

Optionally, the heat pump air conditioning system further includes a first check valve and a second check valve, the second port of the outdoor heat exchanger is connected to the inlet of the first check valve, the outlet of the first check 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 check valve, and the outlet of the second check valve is connected to the inlet of the second expansion valve and the inlet of the first gas-liquid separation device.

Optionally, the heat pump air conditioning system further includes a second gas-liquid separation device, the first port of the outdoor heat exchanger is connected to an inlet of the second gas-liquid separation device through the third flow path, and the gas 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.

Optionally, the heat pump air conditioning system further includes a second heat exchanger and a third expansion valve, the first refrigerant outlet of the first heat exchanger is further connected to the refrigerant inlet of the second heat exchanger via the third expansion valve, the refrigerant outlet of the second heat exchanger is connected to the second refrigerant inlet of the first heat exchanger, the first coolant outlet of the second heat exchanger is used for connecting to an inlet of an electronic device of a vehicle, and the first coolant inlet of the second heat exchanger is used for connecting to an outlet of the electronic device.

Optionally, the electronic device comprises at least one of a motor, a charger, a motor controller, and a DC-DC converter.

Optionally, the second coolant outlet of the second heat exchanger is configured to be connected to an inlet of a battery pack of the vehicle, and the second coolant inlet of the second heat exchanger is configured to be connected to an outlet of the battery pack.

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

Optionally, a first stop valve is disposed on the first flow path, a second stop valve is disposed on the second flow path, and a third stop valve is disposed on the third flow path.

According to another aspect of the present disclosure, a vehicle is provided that includes the heat pump air conditioning system described above.

Compared with the technical scheme that the refrigerant before entering the indoor evaporator releases heat to the outside only through the outdoor heat exchanger and loses enthalpy, the heat pump air-conditioning system provided by the disclosure exchanges heat in the first heat exchanger by arranging the first heat exchanger, so that the refrigerant flowing out of the second port of the outdoor heat exchanger and the refrigerant flowing out of the outlet of the indoor evaporator perform heat exchange in the first heat exchanger, and the refrigerant flowing out of the second port of the outdoor heat exchanger further performs heat dissipation and cooling, namely, the refrigerant can release heat twice through the outdoor heat exchanger and the first heat exchanger before entering the indoor evaporator, and the problem that the heat release quantity of the refrigerant at the outdoor heat exchanger is insufficient due to the influence of the ambient temperature under the condition of higher ambient temperature is solved, so that the lost enthalpy value and the released heat of the refrigerant before entering the indoor evaporator are more, and the supercooling degree of the refrigerant entering the indoor evaporator is favorably improved, and be favorable to flowing into the lower refrigerant of temperature in the interior evaporimeter to make the vehicle thermal management system that this disclosure provided still have better refrigeration effect and refrigeration efficiency under high temperature environment, realize the quick cooling of passenger cabin. In other words, the first heat exchanger is arranged, and the refrigerant flowing out of the second port of the outdoor heat exchanger releases heat in the first heat exchanger, so that the problem that the heat release amount of the refrigerant in the outdoor heat exchanger is limited in a high-temperature environment can be solved.

In addition, because the first gas-liquid separation device is arranged on the flow path between the second port of the outdoor heat exchanger and the first refrigerant inlet of the first heat exchanger, and the first gas-liquid separation device is used for enabling 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, the supercooling degree of the refrigerant entering the first refrigerant inlet of the first heat exchanger can be improved, the heat release quantity of the refrigerant in the first heat exchanger is improved, the temperature of the refrigerant entering the indoor evaporator can be lower, and the passenger compartment can be cooled quickly.

Additional features and advantages of the disclosure will be set forth in the detailed description which follows.

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description serve to explain the disclosure without limiting the disclosure. In the drawings:

fig. 1 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure;

fig. 2 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a cooling mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the cooling mode;

fig. 3 is a refrigerant pressure enthalpy diagram of the heat pump air conditioning system in a cooling mode according to an embodiment of the present disclosure;

fig. 4 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure, wherein the heat pump air conditioning system is in a cooling mode and a battery pack cooling mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the cooling mode;

fig. 5 is a pressure-enthalpy diagram of the refrigerant in the cooling and battery pack cooling modes of the heat pump air conditioning system according to an embodiment of the present disclosure;

fig. 6 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a battery pack cooling mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the battery pack cooling mode;

fig. 7 is a refrigerant pressure-enthalpy diagram of a heat pump air conditioning system in a battery pack cooling mode according to an embodiment of the present disclosure;

fig. 8 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure, wherein the heat pump air conditioning system is in a heat pump heating mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a coolant in the heat pump heating mode;

fig. 9 is a pressure-enthalpy diagram of a refrigerant in a heat pump heating mode of the heat pump air conditioning system according to an embodiment of the present disclosure;

fig. 10 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a waste heat recovery heating mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the waste heat recovery heating mode;

fig. 11 is a pressure-enthalpy diagram of a refrigerant in a waste heat recovery heating mode of the heat pump air conditioning system according to an embodiment of the present disclosure;

fig. 12 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a heat pump heating mode with waste heat recovery, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the heat pump heating mode;

fig. 13 is a pressure-enthalpy diagram of a refrigerant of a heat pump air conditioning system in a heat pump heating mode with waste heat recovery according to an embodiment of the present disclosure;

fig. 14 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure, wherein the heat pump air conditioning system is in a first dehumidification mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the first dehumidification mode;

fig. 15 is a pressure-enthalpy diagram of a refrigerant of the heat pump air conditioning system in the first dehumidification mode according to an embodiment of the present disclosure;

fig. 16 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a second dehumidification mode, and thick solid lines and arrows in the diagram indicate flow paths and flow directions of a refrigerant and a cooling liquid in the second dehumidification mode;

fig. 17 is a pressure-enthalpy diagram of a refrigerant in the second dehumidification mode of the heat pump air conditioning system according to the embodiment of the present disclosure.

Description of the reference numerals

1-a compressor; 2-outdoor heat exchanger; 3-a first gas-liquid separation device; 4-a first heat exchanger; 5-a first expansion valve; 6-indoor evaporator; 7-indoor condenser; 8-first flow path; 9-a second flow path; 10-a third flow path; 11-a second expansion valve; 12-a second gas-liquid separation device; 13-a first one-way valve; 14-a second one-way valve; 15-a second heat exchanger; 16-a first stop valve; 17-a second stop valve; 18-a third stop valve; 19-a third expansion valve; e-first port; f-a second port; a-a first refrigerant inlet; b-a first refrigerant outlet; c-a second refrigerant inlet; d-a second refrigerant outlet.

Detailed Description

The following detailed description of specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.

In the present disclosure, unless stated to the contrary, the "connection" referred to in the present disclosure may be a direct connection between two devices or apparatuses, or may be an indirect connection.

As shown in fig. 1 to 17, 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. An outlet of the compressor 1 is connected with a first port E of the outdoor heat exchanger 2, a second port F of the outdoor heat exchanger 2 is connected with an inlet of the first gas-liquid separating device 3, a liquid outlet of the first gas-liquid separating device 3 is connected with a first refrigerant inlet a of the first heat exchanger 4, a first refrigerant outlet B of the first heat exchanger 4 is connected with an inlet of the indoor evaporator 6 through the first expansion valve 5, an outlet of the indoor evaporator 6 is connected with a second refrigerant inlet C of the first heat exchanger 4, and a second refrigerant outlet D of the first heat exchanger 4 is connected with an inlet of the compressor 1. In other words, the heat pump air conditioning system has a cooling mode by the connection relationship among the compressor 1, the outdoor heat exchanger 2, the first gas-liquid separation device 3, the first heat exchanger 4, the first expansion valve 5, and the indoor evaporator 6, in the refrigeration mode, the gas-liquid two-phase mixed refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is subjected to gas-liquid separation by the first gas-liquid separation device 3, and the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device 3, thereby improving the supercooling degree of the refrigerant flowing out of the first port E of the outdoor heat exchanger 2, leading the liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 to lose enthalpy in the first heat exchanger 4 and then enter the indoor evaporator 6, the first heat exchanger 4 can further increase the supercooling degree of the refrigerant that is about to enter the interior evaporator 6, thereby improving the heat absorption capacity of the refrigerant in the interior evaporator 6.

Specifically, in the cooling mode, as shown in fig. 2, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the outdoor heat exchanger 2, and radiates 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 by an arrow 200 in fig. 3), 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 separator 3 and is separated into the gaseous refrigerant and the liquid refrigerant in the first gas-liquid separator 3, and the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separator 3, so that the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is increased. 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, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 3), the refrigerant which flows out of the first refrigerant outlet B of the first heat exchanger 4 and loses enthalpy is throttled and depressurized by the first expansion valve 5 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, and the low-temperature low-pressure two-phase gas-liquid refrigerant absorbs the heat of the air in the passenger compartment in the indoor evaporator 6, reduces the temperature in the passenger compartment, and realizes the refrigeration of the passenger compartment. The heat-absorbed refrigerant flowing out of the indoor evaporator 6 flows into the first heat exchanger 4, 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, and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

Compared with the prior art in which the refrigerant before entering the indoor evaporator 6 releases heat to the outside only through the outdoor heat exchanger 2 and loses enthalpy, the heat pump air-conditioning system provided by the present disclosure performs heat exchange between 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 in the first heat exchanger 4 by arranging 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, 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, and the problem of insufficient heat release amount of the refrigerant at the outdoor heat exchanger 2 due to the influence of the ambient temperature under the condition of high ambient temperature is solved, so that the lost enthalpy and the released heat of the refrigerant before entering the indoor evaporator 6 are more, the supercooling degree of the refrigerant entering the indoor evaporator 6 is improved, and the refrigerant with lower temperature flows into the indoor evaporator 6, so that the vehicle heat management system provided by the disclosure can still have better refrigeration effect and refrigeration efficiency in a high-temperature environment, and the passenger compartment is cooled quickly. In other words, by providing the first heat exchanger 4 and allowing the refrigerant flowing out of the second port F of the exterior heat exchanger 2 to release heat in the first heat exchanger 4, the problem that the amount of heat released by the refrigerant in the exterior heat exchanger 2 is limited in a high-temperature environment can be solved.

In addition, because the first gas-liquid separation device 3 is arranged on 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 for enabling 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, the supercooling degree of the refrigerant entering the first refrigerant inlet a of the first heat exchanger 4 can be improved, and the heat release quantity of the refrigerant in the first heat exchanger 4 is improved, so that the temperature of the refrigerant entering the indoor evaporator 6 can be lower, and the passenger compartment can be cooled quickly.

Further, the heat pump air conditioning system further 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 an 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 to an inlet of the indoor condenser 7 via the second flow path 9, an 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 further connected to the second refrigerant inlet C of the first heat exchanger 4 via the third flow path 10. The heat pump air conditioning system can be placed in a cooling mode or a heat pump heating mode by controlling the conduction or the cutoff of the first flow path 8, the second flow path 9, and the third flow path 10, and as shown in fig. 2, when the first flow path 8 is conducted and the second flow path 9 and the third flow path 10 are cut off, the cooling mode can be realized; as shown in fig. 8, when the first flow path 8 is closed and the second flow path 9 and the third flow path 10 are opened, the heat pump heating mode can be realized.

In the heat pump heating mode, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 enters the indoor condenser 7, releases heat to the passenger compartment in the indoor condenser 7 and loses enthalpy, so that the temperature of the passenger compartment is increased, and the passenger compartment is heated. The refrigerant flowing out of the outlet of the indoor condenser 7 is throttled and depressurized by the second expansion valve 11, then flows into the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2, absorbs the heat of the outside atmosphere in the outdoor heat exchanger 2, and finally flows back to the compressor 1 from the refrigerant flowing out of the outdoor heat exchanger 2 from the first port E of the outdoor heat exchanger 2.

Here, in the 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, in the heat pump heating mode, the refrigerant flowing out of the outlet of the interior condenser 7 flows into the exterior heat exchanger 2 through the second port F of the exterior heat exchanger 2, and flows out of the exterior heat exchanger 2 through the first port E of the exterior heat exchanger 2, that is, in the cooling mode, the first port E of the outdoor heat exchanger 2 is an inlet for the inflow of the cooling medium, the second port F of the outdoor heat exchanger 2 is an outlet for the outflow of the cooling medium, in the heat pump heating mode, the second port F of the outdoor heat exchanger 2 is an inlet through which cooling medium flows in, and the first port E of the outdoor heat exchanger 2 is an outlet through which cooling medium flows out.

The outdoor heat exchanger 2 has a plurality of flow paths (i.e., a plurality of heat transfer areas) through which the refrigerant flows in sequence while flowing through the outdoor heat exchanger 2, and the flow areas of each of the plurality of flow paths are different, for example, the flow areas of the plurality of flow paths may be gradually decreased in a direction from the first port E to the second port F of the outdoor heat exchanger 2. In the prior art, 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 in both the cooling mode and the heat pump heating mode, that is, the paths through which the refrigerant absorbs (condenses) or dissipates (evaporates) heat in the outdoor heat exchanger 2 are the same in both the cooling mode and the heat pump heating mode, that is, the sequence of the refrigerant flowing through the plurality of flow paths is the same. Because condensation and evaporation are the physical process of phase reversal, under refrigeration mode and heat pump heating mode, the state change of refrigerant in outdoor heat exchanger 2 is different, and the same flow path can make the flow area of every flow mismatch with the state change of refrigerant to influence the heat exchange performance when condensing or evaporating in refrigerant outdoor heat exchanger 2.

In the present disclosure, since the refrigerant enters the outdoor heat exchanger 2 from different ports of the outdoor heat exchanger 2 in the cooling mode and the heat pump heating mode, the flow paths of the refrigerant in the outdoor heat exchanger 2 are different in the cooling mode and the heat pump heating mode, in other words, the sequence of the plurality of flows through which the refrigerant passes in the outdoor heat exchanger 2 is different. In this way, the change of the flow area of each flow path can be adapted to the state change of the refrigerant in the exterior heat exchanger 2 regardless of the cooling mode or the heat pump heating mode.

For example, under the condition that the flow areas of a plurality of flows are gradually reduced from the first port E to the second port F of the outdoor heat exchanger 2, because the refrigerant is subjected to heat release condensation in the outdoor heat exchanger 2 in the cooling mode and changes from a gas state to a liquid state, the pressure, the specific volume and the flow speed of the refrigerant entering the outdoor heat exchanger 2 are high, more refrigerants are favorably subjected to heat exchange through the flow near the first port E of the outdoor heat exchanger 2 due to the large flow area of the flow near the first port E of the outdoor heat exchanger 2, the heat exchange efficiency is improved, the heat release of the refrigerant is favorably realized and the refrigerant is changed from the gas state to the liquid state, in the two-phase region of the refrigerant, as the refrigerant is gradually changed from the gas state to the liquid state, the pressure, the specific volume and the flow speed are gradually reduced, and the flow area of the flow is gradually reduced according to the state change of the refrigerant, that is, the refrigerant is made to enter the outdoor heat exchanger 2 from the first port E of the outdoor heat exchanger 2 and flow out from the second port F in the cooling mode, the heat exchange capacity of the refrigerant in the outdoor heat exchanger 2 during heat release and condensation is more uniform, and the heat release effect is better. Similarly, because the refrigerant absorbs heat and evaporates in the outdoor heat exchanger 2 under the heat pump heating mode, become gaseous from the liquid state, therefore the pressure when the refrigerant gets into the outdoor heat exchanger 2 is little, the specific volume is little, the velocity of flow is little, along with the going on of evaporation, the pressure of refrigerant, the specific volume constantly increases, the velocity of flow becomes fast, consequently make the refrigerant get into the outdoor heat exchanger 2 and flow out from first mouthful E from the second mouth F of outdoor heat exchanger 2 under the heat mode of heating, be favorable to making the through-flow area of refrigerant constantly increase along with its in-process that becomes gaseous from the liquid state, thereby it is more even to do benefit to the heat transfer ability that makes the refrigerant absorb heat and evaporate in the outdoor heat exchanger 2, the heat absorption effect is better.

Therefore, in the heat pump air conditioning system provided by the present disclosure, in the cooling mode, the first port E of the outdoor heat exchanger 2 is an inlet through which the cooling medium flows in, the second port F of the outdoor heat exchanger 2 is an outlet through which the cooling medium flows out, in the heat pump heating mode, the second port F of the outdoor heat exchanger 2 is an inlet through which the cooling medium flows in, and the first port E of the outdoor heat exchanger 2 is an outlet through which the cooling medium flows out, so that the refrigerant has a good heat exchange effect in the outdoor heat exchanger 2 no matter in the cooling mode or in the heat pump heating mode, and the heat exchange performance of the refrigerant during condensation or evaporation in the outdoor heat exchanger 2 is prevented from being affected.

Alternatively, in order to selectively connect or disconnect the first flow path 8, the second flow path 9, and the third flow path 10, in an embodiment, a first stop valve 16 may be disposed on the first flow path 8, a second stop valve 17 may be disposed on the second flow path 9, and a third stop valve 18 may be disposed on the third flow path 10, and the first stop valve 16, the second stop valve 17, and the third stop valve 18 are opened or closed to selectively connect or disconnect the first flow path 8, the second flow path 9, and the third flow path 10, respectively. In another embodiment, the first flow path 8 may be provided with a first on-off valve, the second flow path 9 may be provided with a second on-off valve, and the third flow path 10 may be provided with a third on-off valve.

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

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, as shown in fig. 14, the first flow path 8 is closed, the second flow path 9 is open, the third flow path 10 is open, 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, 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 portions, one portion enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2 after being throttled and depressurized by the second expansion valve 11, absorbs heat of the outside air in the outdoor heat exchanger 2, the other portion is subjected to gas-liquid separation by the first gas-liquid separation device 3, the liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 enters the first heat exchanger 4, releases heat and loses enthalpy, the refrigerant flowing out of the first outlet B of the first heat exchanger 4 flows into the indoor evaporator 6 after being throttled and depressurized by 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 started, when humid air with higher temperature in the passenger compartment meets the indoor evaporator 6 with lower temperature, moisture in the humid air is condensed into condensed water on the surface of the indoor evaporator 6, so that the humidity in the humid air is reduced, the indoor condenser 7 releases heat to the passenger compartment to balance the temperature of the passenger compartment, and the condition that the temperature of the passenger compartment is too low due to the starting of the indoor evaporator 6 is avoided. The refrigerant flowing out of the outlet of the interior evaporator 6 and the refrigerant flowing out of the first port E of the exterior heat exchanger 2 converge and flow into the first heat exchanger 4, enthalpy lost in the first heat exchanger 4 by the refrigerant flowing out of the liquid outlet of the first gas-liquid separation device 3 is obtained in the first heat exchanger 4, and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

In the second dehumidification mode, as shown in fig. 16, the first flow path 8 is closed, the second flow path 9 is opened, the third flow path 10 is closed, and the first expansion valve 5 is opened, so that the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the indoor condenser 7, heat is released to the passenger compartment in the indoor condenser 7, the refrigerant flowing out of the outlet of the indoor condenser 7 sequentially passes through the first gas-liquid separation device 3, the first heat exchanger 4, and the first expansion valve 5 to enter 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, and the refrigerant flowing out of the outlet of the indoor evaporator 6 returns to the compressor 1 through the first heat exchanger 4.

The first dehumidification mode and the second dehumidification mode are different in that: whether or not the refrigerant flowing out of the interior condenser 7 partially flows into the outdoor heat exchanger 2 absorbs heat of the outside air in the outdoor heat exchange, and transfers heat in the environment. Specifically, in the first dehumidification mode, as shown in fig. 14, a part of the refrigerant flowing out of the interior condenser 7 flows into the exterior heat exchanger 2, and the other part flows into the interior evaporator 6; in the second dehumidification mode, as shown in fig. 16, all of the refrigerant flowing out of the exterior condenser flows into the interior evaporator 6, and does not flow through the exterior heat exchanger 2. Since a part of the refrigerant flowing out of the interior condenser 7 flows into the exterior heat exchanger 2 and carries the heat of the outside atmosphere in the exterior heat exchanger 2 in the first dehumidification mode, the first dehumidification mode is applicable to a case where the ambient temperature is low, for example, the ambient temperature is less than 10 ℃, and the second dehumidification mode is applicable to a case where the ambient temperature is higher than the ambient temperature applied in the first dehumidification mode, for example, the ambient temperature is greater than 10 ℃, since the refrigerant does not flow through the exterior heat exchanger 2, that is, does not carry the heat of the outside atmosphere in the exterior heat exchanger 2.

Alternatively, the heat pump air conditioning system may further include a first check valve 13 and a second check valve 14, the second port F of the outdoor heat exchanger 2 is connected to an inlet of the first check valve 13, an outlet of the first check valve 13 is connected to an inlet of the first gas-liquid separation device 3, an outlet of the indoor condenser 7 is connected to an inlet of the second check valve 14, and an outlet of the second check valve 14 is connected to an inlet of the second expansion valve 11 and an inlet of the first gas-liquid separation device 3. Thus, under the heat pump heating mode, the first dehumidification mode, the second dehumidification mode, 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 to the outdoor heat exchanger 2 from the inlet of the first gas-liquid separation device 3; in the cooling mode, as well as the battery pack cooling mode and the cooling and battery pack cooling mode mentioned below, the second check valve 14 prevents the refrigerant at the inlet of the first gas-liquid separation device 3 from flowing back to the indoor condenser 7.

Alternatively, 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 an inlet of the second gas-liquid separation device 12 via the third flow path 10, and a gas outlet of the second gas-liquid separation device 12 and an outlet of the interior evaporator 6 are connected to the second refrigerant inlet C of the first heat exchanger 4. Thus, the gas-liquid two-phase mixed refrigerant flowing out of the first port E of the outdoor heat exchanger 2 is first separated into a gas phase and a liquid phase by the second gas-liquid separator 12, and the gas-phase refrigerant flows into the first heat exchanger 4.

Because 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 directly returns to the compressor 1, the small amount of liquid droplets carried in the gaseous refrigerant may cause liquid impact on the compressor 1, and for this situation, superheat degree control needs to be performed on the refrigerant at the inlet of the compressor 1, so that the superheat degree 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 a saturated vapor line of the refrigerant, thereby preventing the refrigerant from causing liquid impact on the compressor 1. However, the control of the superheat degree of the refrigerant inevitably increases the control complexity of the heat pump air conditioning system.

In the present disclosure, the gas outlet of the second gas-liquid separator 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 separator 12 first passes through the first heat exchanger 4 and then returns 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 of the refrigerant flowing into the first heat exchanger 4 from 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 a small amount of liquid refrigerant carried in the gaseous refrigerant can be evaporated into the gaseous refrigerant, and the refrigerant to be introduced into the compressor 1 passes through a saturated vapor line to be changed into pure gas, so that superheat degree control of the refrigerant to be introduced into the compressor 1 is not required, and control complexity of the heat pump air conditioning system is reduced. In other words, it is not necessary to control the degree of superheat of the refrigerant to be introduced into the inlet of the compressor 1, if the refrigerant flows into both the first refrigerant inlet a and the second refrigerant inlet C of the first heat exchanger 4 (for example, in the cooling mode, the battery pack cooling mode, the cooling and battery pack cooling mode, the first dehumidification mode, the second dehumidification mode, the waste heat recovery heating mode, and the heat pump waste heat recovery heating mode).

A heat mailbox which can be absorbed by the refrigerant at the outdoor heat exchanger 2 under the condition of low outdoor environment temperature, thereby easily influencing the heat release effect of the refrigerant at the indoor condenser 7 and influencing the heating capacity of the passenger compartment, so that the heat pump air conditioning system can realize the heating function of the passenger compartment under the condition of not carrying the external heat through the outdoor heat exchanger 2, in an embodiment provided by the present disclosure, the heat pump air conditioning system further includes a second heat exchanger 15 and a third expansion valve 19, the first refrigerant outlet B of the first heat exchanger 4 is further connected to a 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 for connecting to an inlet of an electronic device of the vehicle, and the first coolant inlet of the second heat exchanger 15 is used for connecting to an outlet of the electronic device.

By opening the third expansion valve 19, and by closing both the first flow path 8 and the third flow path 10 and opening 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 which the passenger compartment is heated by the heat dissipated by the refrigerant carrying electronics. Specifically, in the waste heat recovery heating mode, as shown in fig. 10, the refrigerant flowing out of the outlet of the interior condenser 7 enters the first heat exchanger 4 through the first gas-liquid separation device 3, 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 depressurized through the third expansion valve 19 and flows into the second heat exchanger 15, the refrigerant absorbs heat of the high-temperature coolant absorbed at the electronic device in the second heat exchanger 15, so that heat dissipated when the electronic device operates is recovered to the heat pump air conditioning system, and the heat-absorbed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15 absorbs 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 returns to the compressor 1.

By opening the third expansion valve 19 and closing the first flow path 8, and by opening both 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 waste heat recovery heating mode in which the passenger compartment is heated by the heat emitted from the refrigerant carrying electronics and the heat in the external environment. Specifically, in the heat pump waste heat recovery heating mode, as shown in fig. 12, the refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams, one stream flows into the outdoor heat exchanger 2 to absorb heat in the external environment, 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 the heat emitted by the electronic device is absorbed in the second heat exchanger 15, so that the purpose of transporting the heat emitted by the electronic device and the heat in the external environment to heat the passenger compartment is achieved.

Here, it should be noted that the electronic device refers to a device that needs to operate using electric power and generates heat during operation, and for example, the electronic device may include at least one of a motor, a charger, a motor controller, and a DC-DC converter. When the heat pump air-conditioning system is used for an electric vehicle, when a battery pack is in a charging state, the charger, the DC-DC converter and the like can emit heat due to the fact that the battery pack is in a working state, namely, the charger, the DC-DC converter and the like have heat dissipation requirements, and at the moment, if the passenger compartment has a heating requirement, the heat pump air-conditioning system can be in a waste heat recovery heating mode or a heat pump heating mode with waste heat recovery, so that the heat dissipation requirements of the charger, the DC-DC converter and the like are met, meanwhile, the heat of the charger, the DC-DC converter and the like is recovered to the heat pump air-conditioning system, and the heating capacity of the heat pump air-conditioning system is improved. When the electric vehicle is in a running state, the electric energy of the battery pack is converted into mechanical energy by the motor to drive the vehicle to run, the motor and the like can emit heat, if the passenger compartment has a heating requirement at the moment, the heat pump air-conditioning system can be in a waste heat recovery heating mode or a heat pump heating mode with waste heat recovery, and therefore the heat of the motor is recovered into the heat pump air-conditioning system while the heat dissipation and cooling of the motor are realized.

In the technical field of electric vehicles, vehicle manufacturers seek to continuously shorten the charging time of a battery pack when designing the electric vehicle, and the shortening of the charging time of the battery pack means that the heat release amount of the battery pack is larger during charging, the temperature of the battery pack is higher, and the battery pack needs to be rapidly cooled so as to moderately keep the temperature of the battery pack within a proper working temperature range while shortening the charging time of the battery pack.

In order to meet the requirement that the battery pack needs to be cooled quickly when being charged quickly, the second cooling liquid outlet of the second heat exchanger 15 can be used for being connected with the inlet of the additional battery pack of the vehicle, and the second cooling liquid inlet of the second heat exchanger 15 can be used for being connected with the outlet of the battery pack, so that the heat pump air conditioning system provided by the disclosure can be used for cooling the battery pack quickly.

Specifically, as shown in fig. 6, the heat pump air conditioning system provided by the present disclosure can be made to have a battery pack cooling mode by opening the third expansion valve 19, turning on the first flow path 8, and turning off both the second flow path 9 and the third flow path 10. 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 radiates 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 is reduced (as shown by an arrow 200 in fig. 7), 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 the gaseous refrigerant and the liquid refrigerant in the first gas-liquid separation device 3, and the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device 3, so that the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is increased. The liquid refrigerant flowing out from the liquid outlet of the first gas-liquid separating 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 separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 7), the refrigerant after enthalpy loss flowing out from the first refrigerant outlet B of the first heat exchanger 4 is throttled and depressurized by the third expansion valve 19 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, the low-temperature low-pressure gas-liquid two-phase refrigerant flows into the second heat exchanger 15, and absorbs the heat of the high-temperature cooling liquid absorbing the heat of the battery pack in the second heat exchanger 15, so that the low-temperature cooling liquid for absorbing the heat of the battery pack can flow out from the second cooling liquid outlet of the second heat exchanger 15, therefore, the purpose of cooling the battery pack by using the refrigerant of the heat pump air conditioning system is achieved. The heat-absorbed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15 flows into the first heat exchanger 4, the lost enthalpy of 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, and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

Because under the battery package cooling mode that this disclosure provided, the refrigerant has carried out heat release twice through outdoor heat exchanger 2 and first heat exchanger 4 before getting into second heat exchanger 15, is favorable to increasing the super-cooling degree of the refrigerant that gets into in second heat exchanger 15, and the super-cooling degree is higher, and the refrigerant is more in the heat absorption in second heat exchanger 15 for the temperature of coolant liquid is lower, and the lower the temperature of coolant liquid is more favorable to the quick cooling of battery package. In addition, since the first gas-liquid separation device 3 is disposed on 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, and the first gas-liquid separation device 3 is used for enabling the liquid refrigerant in the gas-liquid two-phase mixed refrigerant flowing out from the second port F of the outdoor heat exchanger 2 to flow into the first heat exchanger 4, the supercooling degree of the refrigerant entering the first refrigerant inlet a of the first heat exchanger 4 can be improved, the heat release amount of the refrigerant in the first heat exchanger 4 is improved, and thus the temperature of the refrigerant entering the second heat exchanger 15 can be lower.

When the battery pack has a cooling demand and the passenger compartment has a cooling demand, the first expansion valve 5 can be opened on the basis of the battery pack coolant mode, so that the cooling and battery pack cooling modes can be realized. In this mode, as shown in fig. 5, the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 is divided into two streams, one stream enters the indoor evaporator 6 after being throttled and depressurized by the first expansion valve 5 to absorb heat of the passenger compartment to cool the passenger compartment, and the other stream enters the second heat exchanger 15 after being throttled and depressurized by the third expansion valve 19 to absorb heat of the battery pack to cool the battery pack.

Alternatively, 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 an inlet of the second gas-liquid separation device 12 via the third flow path 10, and a gas outlet of the second gas-liquid separation device 12, an outlet of the interior evaporator 6, and a refrigerant outlet of the second heat exchanger 15 are connected to the second refrigerant inlet C of the first heat exchanger 4. Thus, in the refrigeration mode, the battery pack cooling mode, the refrigeration and battery pack cooling mode, the first dehumidification mode, the second dehumidification mode, the waste heat recovery heating mode and the heat pump waste heat recovery heating mode, the gaseous refrigerant flowing out of the air 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 a small amount of liquid refrigerant carried in the gaseous refrigerant can be evaporated into the gaseous refrigerant, the refrigerant to enter the compressor 1 passes through a saturated steam line to become pure gaseous, the refrigerant to enter the compressor 1 does not need to be subjected to superheat degree control, and the control complexity of the heat pump air conditioning system is reduced.

The cycle process and principle of the main operation mode of the heat pump air conditioning system provided by the present disclosure will be described with reference to fig. 2 to 17 by taking the embodiment in fig. 1 as an example.

For ease of understanding, a pressure-enthalpy diagram such as that shown in fig. 2 will be described prior to describing the primary modes of operation of the heat pump air conditioning system provided by the present disclosure. In the pressure-enthalpy diagram, the abscissa represents enthalpy of the refrigerant, the enthalpy gradually increases from the left end to the right end of the abscissa, the ordinate represents pressure of the refrigerant, and the pressure gradually increases from the lower end to the upper end of the ordinate. The pressure-enthalpy diagram is provided with a saturated liquid line and a saturated steam line, the left side of the saturated liquid line is a liquid region, and a refrigerant in the region is in a liquid state; the right side of the saturated steam line is used for removing superheated steam, and the refrigerant in the region is in a gaseous state; the region between the saturated liquid line and the saturated steam line is a wet steam region, namely a gas-liquid coexisting region, and the refrigerant in the region is in a gas-liquid two-phase mixed state.

The first mode is as follows: a cooling mode. In this mode, as shown in fig. 2, the first stop valve 16 is opened, the second stop valve 17 is closed, the third stop valve 18 is closed, the first expansion valve 5 is opened, the second expansion valve 11 is closed, and the third expansion valve 19 is closed. As shown in fig. 2 and 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant (shown by an arrow 100 in fig. 3) from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 2, releases heat to the outside atmosphere in the outdoor heat exchanger 2 and loses enthalpy (shown by an arrow 200 in fig. 3), 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 separator 3 and is separated into the gaseous refrigerant and the liquid refrigerant in the first gas-liquid separator 3, and the liquid refrigerant flows out of a liquid outlet of the first gas-liquid separator 3 (shown by a point 300 in fig. 3), so that the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is increased. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separating device 3 flows into the first heat exchanger 4 through the first refrigerant inlet a of the first heat exchanger 4, 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 separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 3), the enthalpy-lost refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 has an equal enthalpy pressure reduced in the first expansion valve 5 and passes through a saturated liquid line (as shown by an arrow 500 in fig. 3), and is throttled and reduced in pressure by the first expansion valve 5 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, which absorbs the heat of the air in the passenger compartment in the indoor evaporator 6 and obtains the enthalpy (as shown by an arrow 600 in fig. 3), thereby reducing the temperature in the passenger compartment and realizing the refrigeration of the passenger compartment. The heat-absorbed refrigerant flowing out of the outlet of the interior evaporator 6 flows into the first heat exchanger 4, and obtains the lost enthalpy of 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 by an arrow 400b in fig. 3), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

And a second mode: cooling and battery pack cooling modes. In this mode, as shown in fig. 4, the first stop valve 16 is opened, the second stop valve 17 is closed, the third stop valve 18 is closed, the first expansion valve 5 is opened, the second expansion valve 11 is closed, and the third expansion valve 19 is opened. As shown in fig. 4 and 5, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant (shown by an arrow 100 in fig. 5) from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 2, releases heat to the outside atmosphere in the outdoor heat exchanger 2 and loses enthalpy (shown by an arrow 200 in fig. 5), 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 separator 3 and is separated into the gaseous refrigerant and the liquid refrigerant in the first gas-liquid separator 3, and the liquid refrigerant flows out of a liquid outlet of the first gas-liquid separator 3 (shown by a point 300 in fig. 5), so that the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is increased. 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, 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, loses enthalpy again in the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separation device 3, the enthalpy value is further decreased (as shown by an arrow 400a in fig. 5), the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 after losing enthalpy is divided into two streams, one stream is decreased in enthalpy pressure in the first expansion valve 5 and passes through a saturated liquid line (as shown by an arrow 500 in fig. 5), and is throttled and decompressed by the first expansion valve 5 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, which absorbs heat of air of a passenger in the interior evaporator 6 and obtains enthalpy (as shown by an arrow 600 in fig. 5), thereby reducing the temperature in the passenger compartment and realizing the refrigeration of the passenger compartment; the other branch of the refrigerant is subjected to pressure drop in the third expansion valve 19 with equal enthalpy and passes through a saturated liquid line (as shown by an arrow 190 in fig. 5), and is throttled and depressurized by the third expansion valve 19 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of high-temperature coolant absorbed at the battery pack in the second heat exchanger 15 and obtains enthalpy (as shown by an arrow 150 in fig. 5), so that low-temperature coolant flows out of a second coolant outlet of the second heat exchanger 15, and the low-temperature coolant can be used for cooling the battery pack, thereby achieving the purpose of cooling the battery pack by using cold energy of the refrigerant. The heat-absorbed refrigerant flowing out of the outlet of the interior evaporator 6 and the heat-absorbed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15 converge and flow into the first heat exchanger 4, enthalpy (shown by an arrow 400b in fig. 5) 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, and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

And a third mode: battery pack cooling mode. In this mode, as shown in fig. 6, the first stop valve 16 is opened, 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 opened. As shown in fig. 6 and 7, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant (shown by an arrow 100 in fig. 7) from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 2, releases heat to the outside atmosphere in the outdoor heat exchanger 2 and loses enthalpy (shown by an arrow 200 in fig. 7), 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 separator 3 and is separated into the gaseous refrigerant and the liquid refrigerant in the first gas-liquid separator 3, and the liquid refrigerant flows out of a liquid outlet of the first gas-liquid separator 3 (shown by a point 300 in fig. 7), so that the supercooling degree of the refrigerant flowing out of the second port F of the outdoor heat exchanger 2 is increased. The liquid refrigerant flowing out of the liquid outlet of the first gas-liquid separating device 3 flows into the first heat exchanger 4 through the first refrigerant inlet a of the first heat exchanger 4, 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 separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 7), the enthalpy-lost refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 decreases in enthalpy pressure in the third expansion valve 19 and passes through a saturated liquid line (as shown by an arrow 190 in fig. 7), and is throttled and reduced in pressure by the third expansion valve 19 to become a low-temperature low-pressure gas-liquid two-phase refrigerant, which absorbs heat of the high-temperature cooling liquid absorbing heat at the battery pack in the second low-temperature low-pressure heat exchanger 15 and obtains enthalpy (as shown by an arrow 150 in fig. 7), the low-temperature cooling liquid flows out of the second cooling liquid outlet of the second heat exchanger 15 and can be used for cooling the battery pack, so that the purpose of cooling the battery pack by using the cold energy of the refrigerant is achieved. The heat-absorbed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 15 flows into the first heat exchanger 4, and obtains the lost enthalpy of 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 by an arrow 400b in fig. 7), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

And a fourth mode: and (4) a heat pump heating mode. In this mode, as shown in fig. 8, 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. As shown in fig. 8 and 9, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant (as indicated by arrow 100 in fig. 9), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 7, and releases heat to the passenger compartment in the interior condenser 7 to lose enthalpy (as indicated by arrow 700 in fig. 9), thereby increasing the temperature of the passenger compartment and heating the passenger compartment. The refrigerant flowing out of the outlet of the interior condenser 7 has an equal enthalpy pressure drop in the second expansion valve 11 and passes through a saturated liquid line (as indicated by an arrow 110 in fig. 9), the refrigerant throttled and depressurized by the second expansion valve 11 enters the outdoor heat exchanger 2 from the second port F of the outdoor heat exchanger 2, absorbs heat from the external environment in the outdoor heat exchanger 2 and obtains enthalpy (as indicated by an arrow 200 in fig. 9), the gas-liquid two-phase mixed refrigerant flowing out of the first port E of the outdoor heat exchanger 2 after absorbing heat is separated into a gas refrigerant and a liquid refrigerant in the second gas-liquid separating device 12, and the gas refrigerant (as indicated by a point 120 in fig. 9) returns to the compressor 1 through the first heat exchanger 4. In the heat pump heating mode, no refrigerant flows into the first refrigerant inlet a of the first heat exchanger 4, and therefore, the gaseous refrigerant flowing out of the gas outlet of the second gas-liquid separator 12 does not exchange heat in the first heat exchanger 4, that is, in this mode, the first heat exchanger 4 is used as a through flow passage.

And a fifth mode: and a waste heat recovery heating mode. In this mode, as shown in fig. 10, the first stop valve 16 is closed, the second stop valve 17 is opened, 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 opened. As shown in fig. 10 and 11, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant (as indicated by an arrow 100 in fig. 11), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 7, and releases heat to the passenger compartment in the interior condenser 7 to lose enthalpy (as indicated by an arrow 700 in fig. 11), thereby increasing the temperature of the passenger compartment and heating the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior condenser 7 flows into the first gas-liquid separating device 3 and is separated into a gas refrigerant and a liquid refrigerant in the first gas-liquid separating device 3, the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separating device 3 (as shown by a point 300 in fig. 11), 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 separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 11), the enthalpy pressure of the enthalpy-lost refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 is reduced in the third expansion valve 19 and passes through a saturated liquid line (as shown by an arrow 190 in fig. 11), the refrigerant is throttled and depressurized by the third expansion valve 19 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature cooling liquid absorbed from the electronic device in the third heat exchanger and obtains enthalpy (as shown by an arrow 150 in fig. 11), so that the purpose of recovering the heat emitted by the electronic device during operation into the heat pump air conditioning system is achieved, and the heat of the electronic device is utilized to heat the passenger compartment. The heat-absorbed refrigerant flowing out of the outlet of the third heat exchanger flows into the first heat exchanger 4, and obtains the lost enthalpy of 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 by an arrow 400b in fig. 11), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

Mode six: the heat pump comprises a waste heat recovery heating mode. In this mode, as shown in fig. 12, 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 opened. As shown in fig. 12 and 13, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant (as indicated by an arrow 100 in fig. 13), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 7, and releases heat to the passenger compartment in the interior condenser 7 to lose enthalpy (as indicated by an arrow 700 in fig. 13), thereby increasing the temperature of the passenger compartment and heating the passenger compartment. The refrigerant flowing out of the outlet of the interior condenser 7 is divided into two streams, one stream is subjected to an equal enthalpy pressure drop in the second expansion valve 11 and passes through a saturated liquid line (as indicated by an arrow 110 in fig. 13), the refrigerant after passing through the second expansion valve 11 and being throttled and depressurized enters the exterior heat exchanger 2 from the second port F of the exterior heat exchanger 2, absorbs heat in the external environment and obtains enthalpy in the exterior heat exchanger 2 (as indicated by an arrow 200 in fig. 13), the other stream flows into the first gas-liquid separation device 3 and is separated into a gaseous refrigerant and a liquid refrigerant in the first gas-liquid separation device 3, the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device 3 (as indicated by a point 300 in fig. 13), 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 the first heat exchanger 4 from the second refrigerant inlet C of the first heat exchanger 4, the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 13), the refrigerant after enthalpy loss flowing out of the first refrigerant outlet B of the first heat exchanger 4 has equal enthalpy pressure in the third expansion valve 19, passes through a saturated liquid line (as shown by an arrow 190 in fig. 13), is throttled and depressurized by the third expansion valve 19, and then becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature cooling liquid absorbing heat from the electronic device in the third heat exchanger and obtains enthalpy (as shown by an arrow 150 in fig. 13), so that the purpose of recovering the heat dissipated by the electronic device during operation into the heat pump air conditioning system is achieved. The gas-liquid two-phase refrigerant in the gas-liquid two-phase mixture state after absorbing heat flowing out of the first port E of the outdoor heat exchanger 2 is separated into the gas-phase refrigerant and the liquid-phase refrigerant in the second gas-liquid separating device 12, the gas-phase refrigerant flows out of the gas outlet of the second gas-liquid separating device 12 (as shown by a point 120 in fig. 13), the gas-phase refrigerant and the gas-liquid two-phase refrigerant in the gas-liquid two-phase mixture state flowing out of the refrigerant outlet of the third heat exchanger converge and flow into the first heat exchanger 4, enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separating device 3 is obtained in the first heat exchanger 4 (as shown by an arrow 400b in fig. 13), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

A seventh mode: a first dehumidification mode. In this mode, as shown in fig. 14, 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 opened, the second expansion valve 11 is opened, and the third expansion valve 19 is closed. As shown in fig. 14 and 15, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 15), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 7, releases heat to the passenger compartment in the interior condenser 7, loses enthalpy (indicated by an arrow 700 in fig. 15), and balances the temperature of the passenger compartment. The refrigerant flowing out of the outlet of the interior condenser 7 is divided into two streams, one stream is subjected to an equal enthalpy pressure drop in the second expansion valve 11 and passes through a saturated liquid line (as indicated by an arrow 110 in fig. 15), the refrigerant after passing through the second expansion valve 11 and being throttled and depressurized enters the exterior heat exchanger 2 from the second port F of the exterior heat exchanger 2, absorbs heat in the external environment and obtains enthalpy in the exterior heat exchanger 2 (as indicated by an arrow 200 in fig. 15), the other stream flows into the first gas-liquid separation device 3 and is separated into a gaseous refrigerant and a liquid refrigerant in the first gas-liquid separation device 3, the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device 3 (as indicated by a point 300 in fig. 15), 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 the first heat exchanger 4 from the second refrigerant inlet C of the first heat exchanger 4, the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separating device 3 loses enthalpy again, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 15), the refrigerant after enthalpy loss flowing out of the first refrigerant outlet B of the first heat exchanger 4 has medium enthalpy pressure reduced in the first expansion valve 5 and passes through a saturated liquid line (as shown by an arrow 500 in fig. 15), the refrigerant is throttled and depressurized by the first expansion valve 5 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat in the indoor evaporator 6 and obtains enthalpy (as shown by an arrow 600 in fig. 15), so that the humid air in the passenger compartment is condensed into condensed water on the surface of the indoor evaporator 6, and the purpose of dehumidifying the passenger compartment is achieved. The gas-liquid two-phase mixed refrigerant flowing out of the first port E of the outdoor heat exchanger 2 after absorbing heat is separated into a gas-phase refrigerant and a liquid-phase refrigerant in the second gas-liquid separating device 12, the gas-phase refrigerant flows out of the gas outlet of the second gas-liquid separating device 12 (as indicated by a point 120 in fig. 15), the gas-phase refrigerant and the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the indoor evaporator 6 converge and flow into the first heat exchanger 4, enthalpy lost by the refrigerant flowing into the first heat exchanger 4 from the liquid outlet of the first gas-liquid separating device 3 is obtained in the first heat exchanger 4 (as indicated by an arrow 400b in fig. 15), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

And a mode eight: and a second dehumidification mode. In this mode, as shown in fig. 16, the first stop valve 16 is closed, the second stop valve 17 is opened, the third stop valve 18 is closed, the first expansion valve 5 is opened, the second expansion valve 11 is closed, and the third expansion valve 19 is closed. As shown in fig. 15 and 16, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 16), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 7, releases heat to the passenger compartment in the interior condenser 7, loses enthalpy (indicated by an arrow 700 in fig. 16), and balances the temperature of the passenger compartment. Flows out of the outlet of the interior condenser 7 into the first gas-liquid separation device 3 and is separated into a gas refrigerant and a liquid refrigerant in the first gas-liquid separation device 3, the liquid refrigerant flows out of the liquid outlet of the first gas-liquid separation device 3 (as shown by a point 300 in fig. 16), 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, the enthalpy value is further reduced (as shown by an arrow 400a in fig. 16), the enthalpy-lost refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 4 drops in enthalpy pressure in the first expansion valve 5 and passes through a saturated liquid line (as shown by an arrow 500 in fig. 16), the refrigerant is throttled and depressurized by the first expansion valve 5 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat in the indoor evaporator 6 and obtains enthalpy (as shown by an arrow 600 in fig. 16), so that humid air in the passenger compartment is condensed into condensed water on the surface of the indoor evaporator 6, and the purpose of dehumidifying the passenger compartment is achieved. The refrigerant flowing out of the outlet of the interior evaporator 6 flows into the first heat exchanger 4, and obtains the lost enthalpy of 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 by an arrow 400b in fig. 16), and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 4 finally returns to the compressor 1.

It should be noted that the above modes provide the main operation modes of the vehicle thermal management system for the present disclosure, and the operation modes that are not mentioned in the present disclosure, but the operation modes that can be realized by the vehicle thermal management system provided by the present disclosure also belong to the protection scope of the present disclosure.

According to another aspect of the present disclosure, there is also provided a vehicle including the heat pump air conditioning system described above.

The preferred embodiments of the present disclosure are described in detail with reference to the accompanying drawings, however, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solution of the present disclosure within the technical idea of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.

It should be noted that, in the foregoing embodiments, various features described in the above embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, various combinations that are possible in the present disclosure are not described again.

In addition, any combination of various embodiments of the present disclosure may be made, and the same should be considered as the disclosure of the present disclosure as long as it does not depart from the gist of the present disclosure.

Claims

1. A heat pump air conditioning system is characterized by comprising 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 with the first port (E) of the outdoor heat exchanger (2), the second port (F) of the outdoor heat exchanger (2) is connected with the inlet of the first gas-liquid separation device (3), the liquid outlet of the first gas-liquid separation device (3) is connected with the first refrigerant inlet (A) of the first heat exchanger (4), the first refrigerant outlet (B) of the first heat exchanger (4) is connected with the inlet of the indoor evaporator (6) through the first expansion valve (5), the outlet of the indoor evaporator (6) is connected with 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 with the inlet of the compressor (1).

2. The heat pump air conditioning system according to claim 1, further comprising an indoor condenser (7), a first flow path (8) selectively opened or closed, a second flow path (9) selectively opened or closed, a third flow path (10) selectively opened or closed, and a second expansion valve (11),

an outlet of the compressor (1) is connected with a first port (E) of the outdoor heat exchanger (2) through the first flow path (8), and is connected with an inlet of the indoor condenser (7) through the second flow path (9), an outlet of the indoor condenser (7) is connected with a second port (F) of the outdoor heat exchanger (2) through the second expansion valve (11), and the first port (E) of the outdoor heat exchanger (2) is further connected with a second refrigerant inlet (C) of the first heat exchanger (4) through the third flow path (10).

3. A heat pump air conditioning system according to claim 2, characterized in that the outlet of the indoor condenser (7) is also connected to the inlet of the first gas-liquid separating device (3).

4. The heat pump air conditioning system according to claim 3, further comprising a first check valve (13) and a second check valve (14), wherein the second port (F) of the outdoor heat exchanger (2) is connected to an inlet of the first check valve (13), an outlet of the first check valve (13) is connected to an inlet of the first gas-liquid separating device (3), an outlet of the indoor condenser (7) is connected to an inlet of the second check valve (14), and an outlet of the second check valve (14) is connected to an inlet of the second expansion valve (11) and an inlet of the first gas-liquid separating device (3).

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

6. The heat pump air-conditioning system according to claim 3, further comprising a second heat exchanger (15) and a third expansion valve (19), wherein the first refrigerant outlet (B) of the first heat exchanger (4) is further connected to a 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 for connecting to an inlet of an electronic device of a vehicle, and the first coolant inlet of the second heat exchanger (15) is used for connecting to an outlet of the electronic device.

7. The heat pump air conditioning system of claim 6, wherein the electronics comprise at least one of a motor, a charger, a motor controller, a DC-DC converter.

8. The heat pump air conditioning system of claim 6, wherein the second coolant outlet of the second heat exchanger (15) is adapted to be connected to an inlet of a battery pack of the vehicle, and the second coolant inlet of the second heat exchanger (15) is adapted to be connected to an outlet of the battery pack.

9. The heat pump air conditioning system according to any one of claims 6 to 8, further comprising a second gas-liquid separation device (12), wherein the first port (E) of the outdoor heat exchanger (2) is connected to an inlet of the second gas-liquid separation device (12) via the third flow path (10), and wherein a gas outlet of the second gas-liquid separation device (12), an outlet of the indoor evaporator (6), and a refrigerant outlet of the second heat exchanger (15) are connected to a second refrigerant inlet (C) of the first heat exchanger (4).

10. The heat pump air conditioning system according to claim 2, wherein a first shut-off valve (16) is provided in the first flow path (8), a second shut-off valve (17) is provided in the second flow path (9), and a third shut-off valve (18) is provided in the third flow path (10).

11. A vehicle comprising a heat pump air conditioning system according to any one of claims 1 to 10.