CN218287372U

CN218287372U - Heat pump air conditioning system and vehicle

Info

Publication number: CN218287372U
Application number: CN202023338442.7U
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: 2023-01-13
Anticipated expiration: 2030-12-31

Abstract

The utility model relates to a heat pump air conditioning system and vehicle, this heat pump air conditioning system includes the compressor, outdoor heat exchanger, first expansion valve and indoor evaporator, the export of compressor and the entry linkage of outdoor heat exchanger, the export of outdoor heat exchanger and the first refrigerant entry linkage of first heat exchanger, the first refrigerant export of first heat exchanger is connected with indoor evaporator entry via first expansion valve, the export of indoor evaporator and the second refrigerant entry linkage of first heat exchanger, the second refrigerant export of first heat exchanger and the entry linkage of compressor. Through setting up first heat exchanger to make the refrigerant can carry out twice in outdoor heat exchanger and first heat exchanger and release heat under the refrigeration mode, improve the super-cooled rate of the refrigerant that gets into indoor evaporator, thereby solve the refrigerant under high temperature environment and release limited problem in outdoor heat exchanger.

Description

Heat pump air conditioning system and vehicle

Technical Field

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

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.

In addition, in the existing vehicle heat pump air conditioning system, the outdoor heat exchanger is used as a condenser in a refrigeration working condition and used as an evaporator in a heating working condition, that is, no matter in the refrigeration working condition or the heating working condition, the refrigerant can flow through the outdoor heat exchanger, paths through which the refrigerant absorbs heat (condenses) or releases heat (evaporates) in the outdoor heat exchanger are the same, and since the condensation and the evaporation are two opposite physical processes, the same flow path can limit the heat exchange performance of the refrigerant when the refrigerant condenses in the outdoor heat exchanger, and the refrigeration effect and the refrigeration efficiency of the vehicle heat pump air conditioning system are affected.

SUMMERY OF THE UTILITY MODEL

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 accomplish the above objects, the present disclosure provides a heat pump air conditioning system including a compressor, an outdoor heat exchanger, a first expansion valve, and an indoor evaporator,

the outlet of the compressor is connected with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger 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 a gas-liquid separation device, an outlet of the indoor evaporator is connected with an inlet of the gas-liquid separation device, and a gas outlet of the gas-liquid separation device is connected with a second refrigerant inlet of the first heat exchanger.

Optionally, the heat pump air conditioning system further comprises an indoor condenser, a through-flow path, and a throttle flow path,

the outlet of the compressor is connected with the inlet of the through-flow path and the inlet of the indoor condenser, the outlet of the indoor condenser is connected with the inlet of the throttling flow path, the outlet of the through-flow path and the outlet of the throttling flow path are connected with the inlet of the outdoor heat exchanger, and the outlet of the outdoor heat exchanger is further connected with the inlet of the gas-liquid separation device through a first flow path which is selectively conducted or cut off.

Optionally, an outlet of the compressor is connected to an inlet of the indoor condenser via a second flow path that is selectively turned on or off.

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

the outlet of the compressor is connected with the inlet of the indoor condenser, the outlet of the indoor condenser is selectively connected with the inlet of the outdoor heat exchanger through the through flow path or the throttling flow path, and the outlet of the outdoor heat exchanger is also connected with the inlet of the gas-liquid separation device through a first flow path which is selectively opened or closed.

Optionally, a first stop valve is disposed on the first flow path, a third stop valve is disposed on the through flow path, and a second expansion valve is disposed on the throttle flow path; or,

the first flow path is provided with a first stop valve, the heat pump air-conditioning system further comprises an expansion switch valve, an outlet of the indoor condenser is connected with an inlet of the outdoor heat exchanger through the expansion switch valve, the through-flow path is a through-flow path in the expansion switch valve, and the throttling flow path is a throttling flow path in the expansion switch valve.

Optionally, an outlet of the indoor condenser is further connected to an inlet of the first expansion valve via a third flow path that is selectively opened or closed, and a first refrigerant outlet of the first heat exchanger is connected to an inlet of the first expansion valve via a check valve.

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

Optionally, an outlet of the indoor condenser is further connected to an inlet of the first expansion valve and an inlet of the third expansion valve via a third flow path that is selectively opened or closed, and a first refrigerant outlet of the first heat exchanger is connected to an inlet of the first expansion valve and an inlet of the third expansion valve via a check valve.

Optionally, a fourth stop valve is disposed on the third flow path.

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.

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

According to the technical scheme, in the refrigeration mode, high-temperature and high-pressure gaseous refrigerant discharged from an outlet of a compressor flows into an outdoor heat exchanger and radiates heat to the outside atmosphere in the outdoor heat exchanger, the refrigerant loses enthalpy in the outdoor heat exchanger, namely, the enthalpy value is reduced, the refrigerant flowing out of the outlet of the outdoor heat exchanger flows into a first heat exchanger through a first refrigerant inlet of the first heat exchanger and exchanges heat with the refrigerant flowing in from a second refrigerant inlet of the first heat exchanger in the first heat exchanger, the refrigerant flowing into the first heat exchanger from the outlet of the outdoor heat exchanger loses enthalpy again, the enthalpy value is further reduced, the refrigerant flowing out of a first refrigerant outlet of the first heat exchanger after losing enthalpy is throttled by a first expansion valve and then becomes low-temperature and low-pressure gas-liquid two-phase refrigerant, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of air in a passenger cabin in an indoor evaporator, the temperature in the passenger cabin is reduced, and the refrigeration of the passenger cabin is realized. The refrigerant which flows out from the outlet of the indoor evaporator and absorbs heat flows into the first heat exchanger, the lost enthalpy of the refrigerant which flows into the first heat exchanger from the outlet of the outdoor heat exchanger is obtained in the first heat exchanger, and the refrigerant which flows out from the second refrigerant outlet of the first heat exchanger finally returns to the compressor.

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 enables the refrigerant flowing out of the outlet of the outdoor heat exchanger and the refrigerant flowing out of the outlet of the indoor evaporator to exchange heat in the first heat exchanger by arranging the first heat exchanger, and enables the refrigerant flowing out of the outlet of the outdoor heat exchanger to further dissipate heat and cool, 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 amount of the refrigerant is insufficient due to the influence of the ambient temperature at the outdoor heat exchanger is solved under the condition of higher ambient temperature, so that the lost enthalpy value and the released heat of the refrigerant before entering the indoor evaporator are more, the supercooling degree of the refrigerant entering the indoor evaporator is improved, and the refrigerant with lower temperature flows into the indoor evaporator is facilitated, and the vehicle heat management system provided by the disclosure can still have better refrigeration effect and refrigeration efficiency under the high-temperature environment, and the rapid cooling of a passenger compartment is realized. In other words, by arranging the first heat exchanger and enabling the refrigerant flowing out of the outlet of the outdoor heat exchanger to release heat in the first heat exchanger, the problems that the heat release amount of the refrigerant in the outdoor heat exchanger is limited in a high-temperature environment and the condensation heat exchange performance is influenced when the outdoor heat exchanger is used as both a condenser and an evaporator can be solved.

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 another embodiment of the present disclosure;

FIG. 3 is a schematic diagram of a heat pump air conditioning system according to yet another embodiment of the present disclosure;

fig. 4 is a schematic structural view of a heat pump air conditioning system according to still another embodiment of the present disclosure;

fig. 5 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. 6 is a refrigerant pressure-enthalpy diagram of a heat pump air conditioning system in a cooling mode according to an embodiment of the present disclosure;

fig. 7 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. 8 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. 9 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. 10 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. 11 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 cooling liquid in the mode;

fig. 12 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. 13 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. 14 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. 15 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, where the heat pump air-conditioning system is in a first 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 mode;

fig. 16 is a pressure-enthalpy diagram of a refrigerant in a first heat pump heating mode with waste heat recovery according to an embodiment of the present disclosure;

fig. 17 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 heat pump 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 coolant in the mode;

fig. 18 is a refrigerant pressure enthalpy diagram of the heat pump air conditioning system in the second heat pump waste heat recovery heating mode according to the embodiment of the present disclosure;

fig. 19 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. 20 is a pressure-enthalpy diagram of the refrigerant of the heat pump air conditioning system in the first dehumidification mode according to an embodiment of the present disclosure;

fig. 21 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. 22 is a pressure-enthalpy diagram of the refrigerant of the heat pump air conditioning system in the second dehumidification mode according to an embodiment of the present disclosure;

fig. 23 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 third 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 third dehumidification mode;

fig. 24 is a refrigerant pressure-enthalpy diagram of the heat pump air conditioning system in the third dehumidification mode according to the embodiment of the present disclosure.

Description of the reference numerals

1-a compressor; 2-outdoor heat exchanger; 3-a first heat exchanger; 4-a first expansion valve; 5-indoor evaporator; 6-gas-liquid separation device; 7-indoor condenser; 8-a through-flow path; 9-throttling the flow path; 10-a first flow path; 11-a second flow path; 12-a first shut-off valve; 13-a second stop valve; 14-a third stop valve; 15-a second expansion valve; 16-an expansion switch valve; 17-a third flow path; 18-a one-way valve; 19-a second heat exchanger; 20-a third expansion valve; 21-a fourth stop valve; 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 the embodiments of the disclosure refers to 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 term "connection" referred to in the present disclosure may be a direct connection or an indirect connection between two devices or apparatuses, where "throttling flow path" refers to a flow path that can throttle and cut off a refrigerant, and "through flow path" refers to a flow path that can realize through flow (i.e., direct conduction of the refrigerant without throttling) and cut off of the refrigerant.

As shown in fig. 1 to 24, the present disclosure provides a heat pump air conditioning system, which may be used in a vehicle, and includes a compressor 1, an outdoor heat exchanger 2, a first heat exchanger 3, a first expansion valve 4, and an indoor evaporator 5, an outlet of the compressor 1 is connected to an inlet of the outdoor heat exchanger 2, an outlet of the outdoor heat exchanger 2 is connected to a first refrigerant inlet a of the first heat exchanger 3, a first refrigerant outlet B of the first heat exchanger 3 is connected to an inlet of the indoor evaporator 5 via the first expansion valve 4, an outlet of the indoor evaporator 5 is connected to a second refrigerant inlet C of the first heat exchanger 3, and a second refrigerant outlet D of the first heat exchanger 3 is connected to an inlet of the compressor 1. That is, in the cooling mode of the heat pump air conditioning system, the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 loses enthalpy in the first heat exchanger 3 and then enters the interior evaporator 5, and the first heat exchanger 3 can increase the degree of supercooling of the refrigerant that is about to enter the interior evaporator 5, thereby increasing the heat absorption capacity of the refrigerant in the interior evaporator 5.

Specifically, in the cooling mode, as shown in fig. 5, 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. 6), the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 through the first refrigerant inlet a of the first heat exchanger 3, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 3 in the first heat exchanger 3, the refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2 loses enthalpy again, the enthalpy value further decreases (as shown by an arrow 300a in fig. 6), and the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 is throttled and depressurized by the first expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase, and the low-liquid-phase absorbs heat of the air in the passenger compartment in the interior evaporator 5, thereby cooling the passenger compartment. The heat-absorbed refrigerant flowing out of the outlet of the interior evaporator 5 flows into the first heat exchanger 3, enthalpy lost by the refrigerant flowing into the first heat exchanger 3 from the outlet of the exterior heat exchanger 2 is obtained in the first heat exchanger 3, and the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 finally returns to the compressor 1.

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 3 by arranging the first heat exchanger 3, so that the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and the refrigerant flowing out of the outlet of the indoor evaporator 5 are subjected to further heat dissipation and cooling, namely, the refrigerant can release heat twice through the outdoor heat exchanger 2 and the first heat exchanger 3 before entering the indoor evaporator 5, and the problem that the heat release amount of the refrigerant is insufficient due to the influence of the ambient temperature at the outdoor heat exchanger 2 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 5 are more, the supercooling degree of the refrigerant entering the indoor evaporator 5 is favorably improved, and the inflow temperature of the indoor evaporator 5 is favorably lowered, so that the vehicle heat management system provided by the disclosure can still have better refrigeration effect and refrigeration efficiency under the high-temperature environment, and the rapid cooling of a passenger compartment is realized. In other words, by providing the first heat exchanger 3 and allowing the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 to release heat in the first heat exchanger 3, the problems that the heat release amount of the refrigerant in the outdoor heat exchanger 2 is limited in a high-temperature environment and the condensing heat exchange performance is affected when the outdoor heat exchanger 2 is used as both a condenser and an evaporator can be solved.

In order to reduce the control complexity of the heat pump air conditioning system provided by the present disclosure, in one embodiment provided by the present disclosure, the outlet of the interior evaporator 5 is connected to the inlet of the gas-liquid separation device 6, and the gas outlet of the gas-liquid separation device 6 is connected to the second refrigerant inlet C of the first heat exchanger 3. That is, the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior evaporator 5 first enters the gas-liquid separator 6, is separated into the gas-phase refrigerant and the liquid-phase refrigerant in the gas-liquid separator 6, and then the gas-phase refrigerant enters the first heat exchanger 3 to absorb the heat of the refrigerant flowing into the first heat exchanger 3 from the outlet of the exterior heat exchanger 2.

In the prior art, the gas-liquid separation device is usually disposed at an inlet of the compressor, that is, after the refrigerant returning to the compressor is subjected to gas-liquid separation by the gas-liquid separation device, the gaseous refrigerant returns to the compressor. However, the gaseous refrigerant separated by the gas-liquid separator still carries a small amount of liquid refrigerant, and the liquid refrigerant entering the compressor causes liquid slugging of the compressor. Therefore, in the prior art, the superheat degree of the refrigerant at the inlet of the compressor is generally controlled to be 0, that is, the refrigerant at the inlet of the compressor is located on the saturated vapor line of the refrigerant, so as to avoid liquid impact on the compressor caused by the refrigerant. However, control of the superheat of the refrigerant increases the complexity of control of the heat pump air conditioning system.

In the present disclosure, the gas-liquid separator 6 is not disposed at the inlet of the compressor 1, i.e., downstream of the first heat exchanger 3 and upstream of the compressor 1, but at the second refrigerant inlet C of the first heat exchanger 3. Since the gaseous refrigerant flowing out of the gas outlet of the gas-liquid separation device 6 absorbs heat and obtains enthalpy after entering the first heat exchanger 3, the refrigerant can pass through a saturated vapor line and enter a superheated vapor region (as shown by an arrow 300b in fig. 6), the refrigerant in the superheated vapor region is in a pure gas state, and the pure gas refrigerant entering the compressor 1 does not cause liquid impact on the compressor 1. That is to say, even if a small amount of liquid refrigerant is carried in the gaseous refrigerant flowing out of the gas outlet of the gas-liquid separation device 6, the liquid refrigerant can absorb heat and evaporate into a gaseous state in the first heat exchanger 3, so that the refrigerant entering the compressor 1 is a pure gaseous refrigerant, superheat degree control is not required, and control complexity of the heat pump air conditioning system can be reduced.

In order to enable the heat pump air conditioning system provided by the present disclosure to have more operation modes and to have stronger functionality, optionally, in a first embodiment provided by the present disclosure, as shown in fig. 2, the heat pump air conditioning system may further include an indoor condenser 7, a through-flow path 8, and a throttle flow path 9, wherein an outlet of the compressor 1 is connected to an inlet of the through-flow path 8 and an inlet of the indoor condenser 7, an outlet of the indoor condenser 7 is connected to an inlet of the throttle flow path 9, an outlet of the through-flow path 8 and an outlet of the throttle flow path 9 are connected to an inlet of the outdoor heat exchanger 2, and an outlet of the outdoor heat exchanger 2 is further connected to an inlet of the gas-liquid separation device 6 via a first flow path 10 that is selectively opened or closed. In the first embodiment, by controlling the respective opening and closing of the through-flow path 8, the throttle path 9, and the first path 10, and the opening and closing of the first expansion valve 4, the heat pump air conditioning system can have a heat pump heating mode and a first dehumidification mode, and specifically, by closing the through-flow path 8, opening the throttle path 9 and the first path 10, and closing the first expansion valve 4, a heat pump heating mode as shown in fig. 11 can be implemented, in which a high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 enters the indoor condenser 7 and releases heat to the passenger compartment in the indoor condenser 7, thereby heating the passenger compartment; by stopping the through-flow path 8 and the first flow path 10, and conducting the throttle flow path 9, and opening the first expansion valve 4, a first dehumidification mode as shown in fig. 19 can be implemented, in which a high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 enters the indoor condenser 7, and releases heat to the passenger compartment in the indoor condenser 7, the refrigerant flowing out of the indoor condenser 7 loses enthalpy through the outdoor heat exchanger 2 and the first heat exchanger 3, and is throttled and reduced in pressure by the first expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant, which absorbs heat in the indoor evaporator 5, and when the humid air with a relatively high temperature of the passenger encounters the indoor evaporator 5 with a relatively low temperature, water droplets are condensed on the surface of the indoor evaporator 5 to form condensed water, so that the air humidity in the passenger compartment can be reduced, and the indoor condenser 7 is in an operating state, can release heat to the passenger compartment, balance the temperature of the passenger compartment, and ensure that the temperature of the passenger compartment is not too low due to the opening of the indoor evaporator 5.

In the first embodiment, when the heat pump air conditioning system is in the cooling mode, the refrigerant flowing out of the outlet of the compressor 1 may enter the interior condenser 7, and at this time, the damper mechanism on the vehicle may be controlled to make the air blown out by the fan flow only through the interior evaporator 5 and not through the interior condenser 7, so that even if there is a high-temperature and high-pressure gaseous refrigerant in the interior condenser 7, the high-temperature and high-pressure gaseous refrigerant does not exchange heat with the air in the passenger compartment, thereby avoiding the problem that the temperature in the passenger compartment cannot be reduced due to the heat exchange between the refrigerant in the interior condenser 7 and the passenger compartment.

In a second embodiment provided in the present disclosure, as shown in fig. 1, in addition to the first embodiment, an outlet of the compressor 1 may be connected to an inlet of the indoor condenser 7 via a second flow path 11 that is selectively opened or closed. That is, the refrigerant flowing out of the outlet of the compressor 1 can be selected to directly flow into the indoor condenser 7 or directly flow into the outdoor heat exchanger 2 by controlling the through-flow path 8 and the second flow path 11, so that, as shown in fig. 5, in the cooling mode, by controlling the second flow path 11 to be cut off, the refrigerant flowing out of the outlet of the compressor 1 can directly flow into the outdoor heat exchanger 2 without flowing into the indoor condenser 7, thereby preventing the refrigerant in the indoor condenser 7 from transferring heat to the air in the passenger compartment in a heat radiation manner due to the existence of high-temperature and high-pressure gaseous refrigerant, and affecting the cooling effect and the cooling efficiency of the indoor evaporator 5.

In a third embodiment provided by the present disclosure, as shown in fig. 3, the heat pump air conditioning system may further include an indoor condenser 7, a through-flow path 8, and a throttle flow path 9, an outlet of the compressor 1 is connected to an inlet of the indoor condenser 7, an outlet of the indoor condenser 7 is selectively connected to an inlet of the outdoor heat exchanger 2 via the through-flow path 8 or the throttle flow path 9, and an outlet of the outdoor heat exchanger 2 is further connected to an inlet of the gas-liquid separation device 6 via a first flow path 10 that is selectively turned on or off. Here, it should be noted that the outlet of the indoor condenser 7 is selectively connected to the inlet of the outdoor heat exchanger 2 through the through-flow passage 8 or the throttle passage 9, which means that the outlet of the indoor condenser 7 can be selectively communicated with the inlet of the outdoor heat exchanger 2 through the through-flow passage 8 or the throttle passage 9, that is, the refrigerant flowing out of the outlet of the indoor condenser 7 can be selectively flowed into the inlet of the outdoor heat exchanger 2 through the through-flow passage 8 or the throttle passage 9.

In the third embodiment, in the cooling mode, the throttle flow path 9 is closed, the through-flow path 8 is opened, the first flow path 10 is closed, and at this time, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 sequentially passes through the interior condenser 7 and the through-flow path 8 and then enters the exterior heat exchanger 2, and the damper mechanism is controlled so that the air blown out by the fan can only flow through the interior evaporator 5 and does not flow through the interior condenser 7, that is, at this time, although the high-temperature and high-pressure gaseous refrigerant flows through the interior condenser 7, since the interior condenser 7 has no air to pass through, the refrigerant does not exchange heat with the air in the passenger compartment in the interior condenser 7, and the interior condenser 7 is used as a through-flow path. In the heat pump heating mode, the through flow path 8 is closed, the throttling flow path 9 is communicated, and the first flow path 10 is communicated, so that the refrigerant which releases heat to the passenger compartment in the indoor condenser 7 can be throttled and depressurized through the throttling flow path 9 and then enters the outdoor heat exchanger 2, and the refrigerant can absorb the heat of the outside atmosphere in the outdoor heat exchanger 2. In the first dehumidification mode, the through-flow path 8 is cut off, the throttling flow path 9 is communicated, the first flow path 10 is cut off, the refrigerant which releases heat to the passenger compartment in the indoor condenser 7 can be throttled and depressurized through the throttling flow path 9 and then enters the outdoor heat exchanger 2, the refrigerant absorbs the heat of the outside atmosphere in the outdoor heat exchanger 2, then the heat is released in the first heat exchanger 3, and the refrigerant enters the indoor evaporator 5 after being throttled and depressurized through the first expansion valve 4, so that the humid air in the passenger compartment is condensed into condensed water on the surface of the indoor evaporator 5.

The third embodiment is different from the second embodiment in that, in the third embodiment, the refrigerant discharged from the outlet of the compressor 1 flows through the interior condenser 7 in both the cooling mode and the heat pump heating mode, and in the cooling mode, no air passes through the interior condenser 7, the interior condenser 7 only functions as a through-flow, and the refrigerant does not exchange heat with the air in the passenger compartment in the interior condenser 7; in the second embodiment, in the cooling mode, the refrigerant discharged from the outlet of the compressor 1 flows through the indoor condenser 7 and directly enters the outdoor heat exchanger 2; in the heating mode, the refrigerant discharged from the outlet of the compressor 1 directly flows into the interior condenser 7.

Alternatively, as shown in fig. 1 and 2, in the first and second embodiments, the first flow path 10 is provided with the first stop valve 12, the second flow path 11 is provided with the second stop valve 13, the through flow path 8 is provided with the third stop valve 14, and the throttle flow path 9 is provided with the second expansion valve 15, so that the first flow path 10 and the second flow path 11 can be selectively connected or disconnected, the through flow path 8 directly passes or disconnects the refrigerant, and the throttle flow path 9 throttles or shuts the refrigerant.

Alternatively, as for the third embodiment, in one embodiment, as shown in fig. 3, a first stop valve 12 is provided on the first flow path 10, a third stop valve 14 is provided on the through flow path 8, and a second expansion valve 15 is provided on the throttle flow path 9.

In another embodiment, the first flow path 10 is provided with a first stop valve 12, the heat pump air conditioning system further includes an expansion switch valve 16, the outlet of the indoor condenser 7 is connected to the inlet of the outdoor heat exchanger 2 via the expansion switch valve 16, the through-flow path 8 is a through-flow path in the expansion switch valve 16, and the throttle flow path 9 is a throttle path in the expansion switch valve 16. Here, the expansion switch valve 16 is equivalent to an integration of an expansion valve and a switch valve, the expansion switch valve 16 has a throttle flow channel and a through flow channel inside, the throttle flow channel is provided with a throttle valve port and a throttle valve core inside, the through flow channel is provided with a through flow valve port and a through flow valve core inside, and the throttle valve core or the through flow valve core can be selectively controlled to be opened according to the working mode of the heat pump air conditioning system, so that the refrigerant has a throttle state of being throttled and depressurized and a through flow state of not throttling and being directly conducted through the expansion switch valve 16.

In another embodiment, a first on-off valve may be provided in the first flow path 10, a second on-off valve may be provided in the second flow path 11, and a third on-off valve may be provided in the flow path 8.

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

In order to enable the heat pump air conditioning system to have different dehumidification modes at different ambient temperatures, the heat pump air conditioning system provided by the disclosure can have a second dehumidification mode and a third dehumidification mode in addition to the first dehumidification mode. In one embodiment, the outlet of the interior condenser 7 is further connected to the inlet of the first expansion valve 4 via a third flow path 17 that is selectively opened and closed, and the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 via a check valve 18. As shown in fig. 21 and 23, the heat pump air conditioning system can have the second dehumidification mode and the third dehumidification mode by controlling the on or off of the third flow path 17.

In the second dehumidification mode, as shown in fig. 21, the throttle flow path 9 is closed, the third flow path 17 is opened, and the heat-released refrigerant flowing out of the outlet of the interior condenser 7 is throttled and depressurized by the first expansion valve 4 and then directly enters the interior evaporator 5. In the third dehumidification mode, as shown in fig. 23, the throttle flow path 9 is opened, the third flow path 17 is opened, the heat-released refrigerant flowing out of the outlet of the indoor condenser 7 is divided into two streams, one stream is throttled and depressurized by the throttle flow path 9 and flows into the outdoor heat exchanger 2, the other stream is throttled and depressurized by the first expansion valve 4 and flows into the indoor evaporator 5, and the refrigerant flowing out of the indoor evaporator 5 and the refrigerant flowing out of the outdoor heat exchanger 2 are merged and finally returned to the compressor 1.

Here, as shown in fig. 23, in the third dehumidification mode, the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 via the check valve 18, so that the refrigerant flowing out of the outlet of the interior condenser 7 can only flow into the first expansion valve 4 and cannot flow back into the first heat exchanger 3 via the first check valve 18, and the pressure of the refrigerant flowing out of the outlet of the exterior heat exchanger 2 (the pressure corresponding to the arrow 200 in fig. 24) is lower than the pressure of the refrigerant flowing out of the outlet of the interior condenser 7 (the pressure corresponding to the arrow 700 in fig. 24), so that the refrigerant flowing out of the outlet of the exterior heat exchanger 2 cannot flow into the first expansion valve 4 via the first heat exchanger 3 and the first check valve 18.

As shown in fig. 19 to 24, one of the main differences among the first dehumidification mode, the second dehumidification mode, and the third dehumidification mode is as follows: whether or not the refrigerant flowing out of the interior condenser 7 flows into the outdoor heat exchanger 2 absorbs heat of the outside air in the outdoor heat exchanger 2, and transfers heat in the environment. Specifically, in the first dehumidification mode, as shown in fig. 19, all the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2, absorbs heat in the outdoor heat exchanger 2, flows into the first heat exchanger 3, releases heat in the first heat exchanger 3, throttles by the first expansion valve 4, and enters the indoor evaporator 5; in the second dehumidification mode, all the refrigerant flowing out of the interior condenser 7 flows into the interior evaporator 5, and does not flow through the exterior heat exchanger 2; in the third dehumidification mode, a part of the refrigerant flowing out of the interior condenser 7 directly flows into the outdoor heat exchanger 2, and the other part directly flows into the interior evaporator 5. Based on this, the first dehumidification mode may be applied to a case where the ambient temperature is low, for example, a case where the ambient temperature is less than 5 ℃; the second dehumidification mode may be applied to a case where the ambient temperature is higher than that applied in the first dehumidification mode, for example, the ambient temperature is 10 ℃ to 15 ℃; the ambient temperature applied by the third dehumidification mode may be between the ambient temperatures applied by the first dehumidification mode and the second dehumidification mode, for example, 5-10 ℃.

In addition, the first dehumidification mode, the second dehumidification mode, and the third dehumidification mode are further different in that: in the first dehumidification mode, the refrigerant flowing out of the gas outlet of the gas-liquid separation device 6 absorbs heat of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3, and in the second dehumidification mode and the third dehumidification mode, no refrigerant flows into the first refrigerant inlet a of the first heat exchanger 3, so that the refrigerant flowing out of the gas outlet of the gas-liquid separation device 6 cannot exchange heat in the first heat exchanger 3, that is, in the second dehumidification mode and the third dehumidification mode, the first heat exchanger 3 is used as a through flow passage, and the refrigerant does not exchange heat in the first heat exchanger 3. As mentioned above, when the refrigerant flowing out of the gas-liquid separator 6 exchanges heat in the first heat exchanger 3, the superheat degree adjustment is not required, and thus, in the first dehumidification mode, the superheat degree adjustment of the refrigerant flowing into the compressor 1 is not required, and in the second dehumidification mode and the third dehumidification mode, the superheat degree adjustment of the refrigerant flowing into the compressor 1 is required, so that the refrigerant is on the saturated vapor line, that is, as shown in fig. 22 and 24, the start point of the arrow 100 is on the saturated vapor line.

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

Because the first refrigerant outlet B of the first heat exchanger 3 is also connected with the refrigerant inlet of the second heat exchanger 19 through the third expansion valve 20, the refrigerant can exchange heat with the cooling liquid which enters the second heat exchanger 19 after absorbing heat at the electronic device in the second heat exchanger 19, so that the heat emitted by the electronic device is recovered to the heat pump air conditioning system.

Specifically, as shown in fig. 15, the heat pump air conditioning system provided by the present disclosure further has a first heat pump waste heat recovery heating mode, in which the through-flow path 8 is closed, the second path 11 is open, the throttle path 9 is open, the first expansion valve 4 is closed, the first path 10 is closed, the high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the indoor condenser 7 and releases heat to the passenger compartment in the indoor condenser 7, thereby increasing the temperature of the passenger compartment, the refrigerant flowing out of the indoor condenser 7 flows into the outdoor heat exchanger 2 after being throttled and depressurized through the throttle path 9, and absorbs the heat of the outside atmosphere in the outdoor heat exchanger 2, thereby transporting the heat in the outdoor environment, so that the enthalpy value of the refrigerant increases, the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first refrigerant heat exchanger 3 and loses enthalpy, and then is throttled and depressurized through the second expansion valve 15, the low-temperature refrigerant flows into the second heat exchanger 19, the high-temperature coolant after absorbing heat from the electronic device absorbs heat to the refrigerant, thereby obtaining heat release from the low-temperature heat pump, and solving the problem of the heat absorption in the outdoor heat exchanger 2. The refrigerant flowing out of the outlet of the second heat exchanger 19 after absorbing heat can increase the suction temperature and suction pressure at the inlet of the compressor 1, which is beneficial to improving the heating capacity of the heat pump air-conditioning system in a low-temperature environment. That is, in the first heat pump waste heat recovery heating mode, the refrigerant may carry heat of the outside air through the outdoor heat exchanger 2 and may carry heat of the electronic devices through the second heat exchanger 19.

Alternatively, the outlet of the interior condenser 7 is connected to the inlet of the first expansion valve 4 and the inlet of the third expansion valve 20 via a third flow path 17 that is selectively opened or closed, and the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the first expansion valve 4 and the inlet of the third expansion valve 20 via a check valve 18. Since the outlet of the indoor condenser 7 is also connected to the inlet of the third expansion valve 20 via the third flow path 17, the heat pump air conditioning system provided by the present disclosure may further have a second heat pump waste heat recovery-containing heating mode.

Specifically, as shown in fig. 17, the control through-flow path 8 is closed, the second path 11 is opened, the third path 17 is opened, the throttle path 9 is opened, the first path 10 is opened, and the third expansion valve 20 is opened, so that the heat pump air conditioning system can have a second heat pump waste heat recovery heating mode. In this mode, the refrigerant flowing out of the outlet of the interior condenser 7 is divided into two streams, one stream is throttled and depressurized by the throttle flow path 9 and then enters the exterior heat exchanger 2 to absorb heat of the outside atmosphere, the other stream is throttled and depressurized by the third expansion valve 20 and then enters the second heat exchanger 19, the heat of the high-temperature coolant absorbing heat at the electronic device is absorbed in the second heat exchanger 19, and the heat-absorbed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 and the heat-absorbed refrigerant flowing out of the outlet of the exterior heat exchanger 2 converge and then return to the compressor 1 together. In the second heat pump waste heat recovery heating mode, the first refrigerant outlet B of the first heat exchanger 3 is connected to the inlet of the third expansion valve 20 via the check valve 18, so that the refrigerant flowing out of the outlet of the interior condenser 7 cannot flow back into the first heat exchanger 3, and the pressure of the refrigerant flowing out of the outlet of the exterior heat exchanger 2 (see arrow 200 in fig. 18) is lower than the pressure of the refrigerant flowing out of the outlet of the interior condenser 7 (see arrow 700 in fig. 18), so that the refrigerant flowing out of the outlet of the exterior heat exchanger 2 cannot flow through the first heat exchanger 3 into the third expansion valve 20.

The difference between the first heat pump heating mode with waste heat recovery and the second heat pump heating mode with waste heat recovery is that in the first heat pump heating mode with waste heat recovery, all the refrigerant flowing out of the outlet of the indoor condenser 7 enters the outdoor heat exchanger 2, absorbs heat in the outdoor heat exchanger 2, then flows through the first heat exchanger 3 and then absorbs heat in the second heat exchanger 19; in the second heat pump heating mode including the waste heat recovery mode, a part of the refrigerant flowing out of the outlet of the interior condenser 7 absorbs heat in the exterior heat exchanger 2, and the other part absorbs heat in the second heat exchanger 19. On this basis, as shown in fig. 15, in the first heat pump waste heat recovery heating mode, the refrigerant flowing out of the gas-liquid separator 6 at the gas outlet absorbs the heat of the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 in the first heat exchanger 3, and therefore, in the first heat pump waste heat recovery heating mode, the degree of superheat of the refrigerant to be introduced into the compressor 1 is controlled to 0 without performing the degree of superheat control on the refrigerant to be introduced into the compressor 1. In the second heat pump waste heat recovery heating mode, as shown in fig. 17, since the refrigerant does not exchange heat in the first heat exchanger 3 in this mode, that is, the first heat exchanger 3 is used as a through flow passage, the refrigerant flowing into the compressor 1 needs to be adjusted in superheat degree so that the refrigerant is on a saturated vapor line, that is, as shown in fig. 18, the start point of the arrow 100 is on the saturated vapor line.

In addition, since the outlet of the interior condenser 7 is further connected to the inlet of the third expansion valve 20 via the third flow path 17, the heat pump air conditioning system provided by the present disclosure may further have a waste heat recovery heating mode, in which the refrigerant flowing out of the outlet of the interior condenser 7 does not flow through the exterior heat exchanger 2 and carries the heat of the outside atmosphere, but directly flows into the second heat exchanger 19 and carries the heat of the electronic devices in the second heat exchanger 19.

Specifically, in the waste heat recovery heating mode, as shown in fig. 13, the through-flow path 8 is closed, the second flow path 11 is open, the throttle flow path 9 is closed, the first flow path 10 is closed, the third flow path 17 is open, the third expansion valve 20 is open, the compressor 1, the interior condenser 7, the third expansion valve 20, the second heat exchanger 19, the gas-liquid separator 6, and the first heat exchanger 3 are sequentially connected in series to form a loop, the refrigerant flowing out from the outlet of the interior condenser 7 is throttled and depressurized by the third expansion valve 20 and flows into the second heat exchanger 19, the heat of the high-temperature coolant having absorbed heat from the electronic device is absorbed in the second heat exchanger 19, and the refrigerant flowing out from the refrigerant outlet of the second heat exchanger 19 and having obtained enthalpy finally returns to the compressor 1.

Here, 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 the battery pack is in a charging state, the charger, the DC-DC converter and the like can emit heat due to the 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 mode, a first heat pump waste heat recovery mode or a second heat pump waste heat recovery mode, so that the heat of the charger, the DC-DC converter and the like is recovered into the heat pump air-conditioning system while the heat dissipation requirements of the charger, the DC-DC converter and the like are met, 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 mode, a first heat pump comprises the waste heat recovery mode or a second heat pump comprises the waste heat recovery mode, 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.

Alternatively, the third flow path 17 may be provided with a fourth shutoff valve 21, and the third flow path 17 may be opened or closed by controlling the opening or closing of the fourth shutoff valve 21. In another embodiment, a fourth on-off valve may be provided in the third flow path 17.

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 the battery pack is charged quickly, the second cooling liquid outlet of the second heat exchanger 19 can be used for being connected with the inlet of the battery pack of the vehicle, and the second cooling liquid inlet of the second heat exchanger 19 can be used for being connected with the outlet of the battery pack, so that the battery pack can be cooled quickly through the heat pump air conditioning system provided by the disclosure.

Specifically, as shown in fig. 9, in the battery pack cooling mode, the through-flow path 8 is opened, the second flow path 11, the throttle flow path 9, and the first flow path 10 are all closed, the first expansion valve 4 is closed, and the third expansion valve 20 is opened, so that 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, i.e., the enthalpy value decreases (as shown by an arrow 200 in fig. 10), the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3 through the first refrigerant inlet a of the first heat exchanger 3, and exchanges heat with the refrigerant flowing in from the second refrigerant inlet C of the first heat exchanger 3 in the first heat exchanger 3, the refrigerant flowing into the first heat exchanger 3 from the outlet of the outdoor heat exchanger 2 loses enthalpy again, the enthalpy value further decreases (as shown by an arrow 300a in fig. 10), the refrigerant after enthalpy loss flowing out of the first refrigerant outlet B of the first heat exchanger 3 is throttled and depressurized by the third expansion valve 20 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 the high-temperature coolant absorbing heat at the battery pack in the second heat exchanger 19, so that the low-temperature coolant flows out of the second coolant outlet of the second heat exchanger 19, and the low-temperature coolant can continue to cool the battery pack.

Because under the battery package cooling mode that this disclosure provided, the refrigerant carries out heat release twice through outdoor heat exchanger 2 and first heat exchanger 3 before entering second heat exchanger 19, is favorable to increasing the supercooling degree of the refrigerant that gets into in second heat exchanger 19, and the supercooling degree is higher, and the refrigerant is more in the heat absorption in second heat exchanger 19 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.

When the battery pack has a cooling demand and the passenger compartment has a cooling demand, the first expansion valve 4 may be opened based on the battery pack cooling mode, so that the heat pump air conditioning system provided by the present disclosure may have both cooling and battery pack cooling modes. In this mode, as shown in fig. 7, the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 is divided into two streams, one stream enters the indoor evaporator 5 after being throttled and depressurized by the first expansion valve 4 to absorb heat in the passenger compartment to cool the passenger compartment, and the other stream enters the second heat exchanger 19 after being throttled and depressurized by the third expansion valve 20 to absorb heat in the battery pack to cool the battery pack.

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. 5 to 24 by taking the embodiment in fig. 1 as an example. The cycle-through principle of the system in other embodiments (e.g., fig. 2 to 4) is similar to that in fig. 1, and is not repeated herein.

For ease of understanding, a pressure-enthalpy diagram such as that shown in fig. 6 will be described before describing the main 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. 5, the first stop valve 12 is closed, the second stop valve 13 is closed, the third stop valve 14 is opened, the fourth stop valve 21 is closed, the first expansion valve 4 is opened, and the second expansion valve 15 and the third expansion valve 20 are closed. As shown in fig. 5 and 6, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant, so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (shown by arrow 100 in fig. 6), 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 to lose enthalpy (shown by arrow 200 in fig. 6), the enthalpy-lost refrigerant flowing out of the outlet of the outdoor heat exchanger 2 flows into the first heat exchanger 3, continues to release heat and lose enthalpy (shown by arrow 300a in fig. 6) in the first heat exchanger 3, the first refrigerant outlet B of the first heat exchanger 3 flows out a liquid refrigerant, the enthalpy pressure of the liquid refrigerant in the first expansion valve 4 drops and passes through a saturated liquid line (shown by arrow 400 in fig. 6), the outlet of the first expansion valve 4 flows out a low-temperature gas-liquid two-phase refrigerant, and the low-temperature gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the interior evaporator 5 and obtains enthalpy (shown by arrow 500 in fig. 6) to lower the temperature of the passenger compartment, thereby achieving low-pressure refrigeration of the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior evaporator 5 flows into the gas-liquid separator 6, is separated into a liquid state and a gas state in the gas-liquid separator 6, flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 6) and flows into the first heat exchanger 3, absorbs heat in the first heat exchanger 3, and obtains enthalpy lost in the first heat exchanger 3 by the refrigerant flowing out of the outlet of the exterior heat exchanger 2 (as indicated by an arrow 300b in fig. 6), so that a small amount of liquid refrigerant carried in the gas refrigerant separated by the gas-liquid separator 6 is evaporated into the gas refrigerant, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 is located in a superheated steam zone, and the gas refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1. In the refrigeration mode, the refrigerant releases heat to the outside atmosphere through the outdoor heat exchanger 2 to lose enthalpy, and releases heat again in the first heat exchanger 3 to lose enthalpy, so that the refrigeration mode can provide the refrigerant with higher supercooling degree to the indoor evaporator 5, and the heat pump air conditioning system can have better refrigeration effect and refrigeration efficiency in a high-temperature environment.

And a second mode: cooling and battery pack cooling modes. In this mode, as shown in fig. 7, the first stop valve 12 is closed, the second stop valve 13 is closed, the third stop valve 14 is opened, the fourth stop valve 21 is closed, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As shown in fig. 7 and 8, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant (as indicated by an arrow 100 in fig. 8), 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 (as indicated by an arrow 200 in fig. 8), the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and losing enthalpy flows into the first heat exchanger 3, and the heat is continuously released and lost enthalpy in the first heat exchanger 3 (as indicated by an arrow 300a in fig. 8). The liquid refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 is divided into two streams, one stream is subjected to isenthalpic pressure reduction in the first expansion valve 4 and passes through a saturated liquid line (as shown by an arrow 400 in fig. 8), a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment and obtains enthalpy (as shown by an arrow 500 in fig. 8) in the indoor evaporator 5 to reduce the temperature of the passenger compartment and realize refrigeration of the passenger compartment; the other side of the refrigerant flow is subjected to an enthalpy pressure drop in the third expansion valve 20 and passes through a saturated liquid line (as shown by an arrow 2000 in fig. 8), a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of an outlet of the third expansion valve 20, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature coolant after absorbing heat at the battery pack in the second heat exchanger 19 and obtains enthalpy (as shown by an arrow 190 in fig. 8), so that the low-temperature coolant for cooling the battery pack can flow out from a second coolant outlet of the second heat exchanger 19, and the battery pack is cooled. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior evaporator 5 and the gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 converge and flow into the gas-liquid separator 6, are separated into a liquid state and a gaseous state in the gas-liquid separator 6, the gaseous refrigerant flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 8) and flows into the first heat exchanger 3, absorbs heat in the first heat exchanger 3, and obtains enthalpy (as indicated by an arrow 300b in fig. 8) lost by the refrigerant flowing out of the outlet of the exterior heat exchanger 2 in the first heat exchanger 3, so that a small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separator 6 is evaporated into a gaseous refrigerant, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 is located in a superheated vapor region, and the gaseous refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1. In the refrigeration mode, the refrigerant releases heat to the outside atmosphere through the outdoor heat exchanger 2 to lose enthalpy, releases heat again in the first heat exchanger 3 to lose enthalpy, so that the refrigeration mode can provide the refrigerant with higher supercooling degree to the indoor evaporator 5, the heat pump air conditioning system can have better refrigeration effect and refrigeration efficiency in a high-temperature environment, meanwhile, the battery pack can be rapidly cooled, and the battery pack is beneficial to rapid charging.

And a third mode: battery pack cooling mode. In this mode, as shown in fig. 9, the first stop valve 12 is closed, the second stop valve 13 is closed, the third stop valve 14 is opened, the fourth stop valve 21 is closed, the first expansion valve 4 is closed, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As shown in fig. 9 and 10, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (indicated by arrow 100 in fig. 10), 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 (indicated by arrow 200 in fig. 10), the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and losing enthalpy flows into the first heat exchanger 3, and the heat of the refrigerant is continuously released and lost enthalpy in the first heat exchanger 3 (indicated by arrow 300a in fig. 10). The liquid refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 has a reduced enthalpy pressure in the third expansion valve 20 and passes through a saturated liquid line (as shown by an arrow 2000 in fig. 10), and a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the third expansion valve 20, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature coolant absorbed at the battery pack in the second heat exchanger 19 and obtains enthalpy (as shown by an arrow 190 in fig. 10), so that the low-temperature coolant used for cooling the battery pack can flow out of the second coolant outlet of the second heat exchanger 19, and the battery pack is cooled. The gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 flows into the gas-liquid separator 6, is separated into a liquid state and a gas state in the gas-liquid separator 6, flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 10) and flows into the first heat exchanger 3, absorbs heat in the first heat exchanger 3, obtains enthalpy lost in the first heat exchanger 3 by the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 (as indicated by an arrow 300b in fig. 10), further evaporates a small amount of liquid refrigerant carried in the gas refrigerant separated by the gas-liquid separator 6 into the gas refrigerant, allows the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 to be located in a superheated steam zone, and returns the gas state flowing out of the second refrigerant outlet D of the first heat exchanger 3 to the compressor 1. In the refrigeration mode, the refrigerant releases heat to the outside atmosphere through the outdoor heat exchanger 2 to lose enthalpy, and releases heat again in the first heat exchanger 3 to lose enthalpy, so that the refrigeration mode can provide the refrigerant with higher supercooling degree to the indoor evaporator 5, and the more heat absorbed by the refrigerant with higher supercooling degree is, the more heat is, the more the cooling time of the battery pack is favorably shortened, and the quick cooling of the battery pack is realized.

And a fourth mode: and (4) a heat pump heating mode. In this mode, as shown in fig. 11, the first stop valve 12 is opened, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is closed, the first expansion valve 4 is closed, the second expansion valve 15 is opened, and the third expansion valve 20 is closed. As shown in fig. 11 and 12, 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. 12), 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. 12), thereby increasing the temperature of the passenger compartment and heating the passenger compartment. The refrigerant after heat release flowing out of the outlet of the interior condenser 7 has an equal enthalpy pressure drop in the second expansion valve 15 and passes through a saturated liquid line (as indicated by an arrow 150 in fig. 12), the outlet of the second expansion valve 15 flows out a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat of the outside atmosphere in the exterior heat exchanger 2 and obtains enthalpy (as indicated by an arrow 200 in fig. 12), the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the exterior heat exchanger 2 and having an increased temperature is divided into a gas refrigerant and a liquid refrigerant in the gas-liquid separator 6, and the gas refrigerant flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 12) and returns to the compressor 1 through the first heat exchanger 3. In this mode, since the gaseous refrigerant flowing out of the gas-liquid separator 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 serves as a through-flow passage, the refrigerant needs to be controlled to have a superheat degree of 0 before returning to the compressor 1, that is, the starting point of the arrow 100 in fig. 12 is located on the saturated vapor line.

And a fifth mode: and a waste heat recovery heating mode. In this mode, as shown in fig. 13, the first stop valve 12 is closed, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is closed, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As shown in fig. 13 and 14, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that a high-temperature high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 14) is discharged from an outlet of the compressor 1, and the high-temperature high-pressure gaseous refrigerant flows into the interior condenser 7, releases heat to the passenger compartment in the interior condenser 7, and loses enthalpy (indicated by an arrow 700 in fig. 14), thereby increasing the temperature of the passenger compartment and warming the passenger compartment. The refrigerant after heat release flowing out of the outlet of the interior condenser 7 has an equal enthalpy pressure drop in the third expansion valve 20 and passes through a saturated liquid line (as indicated by an arrow 2000 in fig. 14), the refrigerant of a gas-liquid two-phase mixed state with a low temperature and a low pressure flows out of the outlet of the third expansion valve 20, the refrigerant of the gas-liquid two-phase mixed state with a low temperature and a low pressure absorbs heat of the high-temperature coolant absorbed at the electronic device in the second heat exchanger 19 and obtains enthalpy (as indicated by an arrow 190 in fig. 14), so that the heat dissipated by the electronic device is recovered to the air conditioning system, the refrigerant of a gas-liquid two-phase mixed state with a raised temperature flowing out of the refrigerant outlet of the second heat exchanger 19 is separated into a gas refrigerant and a liquid refrigerant in the gas-liquid separator 6, and the gas refrigerant flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 14) and returns to the compressor 1 through the first heat exchanger 3.

Mode six: the first heat pump comprises a waste heat recovery heating mode. In this mode, as shown in fig. 15, the first stop valve 12 is closed, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is closed, the first expansion valve 4 is closed, the second expansion valve 15 is opened, and the third expansion valve 20 is opened. 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 a high-temperature high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 16) is discharged from an outlet of the compressor 1, and the high-temperature 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 increases the temperature of the passenger compartment to heat the passenger compartment. The refrigerant after heat release flowing out of the outlet of the interior condenser 7 has an equal enthalpy pressure drop in the second expansion valve 15 and passes through a saturated liquid line (as indicated by an arrow 150 in fig. 16), the refrigerant of a low temperature and low pressure in a gas-liquid two-phase mixed state flows out of the outlet of the second expansion valve 15, the refrigerant of the low temperature and low pressure in a gas-liquid two-phase mixed state absorbs heat of the outside atmosphere in the exterior heat exchanger 2 and obtains enthalpy (as indicated by an arrow 200 in fig. 16), the refrigerant flowing out of the outlet of the exterior heat exchanger 2 flows into the first heat exchanger 3 and loses enthalpy (as indicated by an arrow 300a in fig. 16) in the first heat exchanger 3, the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 has an equal enthalpy pressure drop in the third expansion valve 20 (as indicated by an arrow 2000 in fig. 16), the refrigerant of a low temperature and low pressure in a gas-liquid two-phase flows out of the outlet of the third expansion valve 20, the low temperature and low pressure in a gas-liquid two-liquid phase refrigerant absorbing heat of the high temperature coolant absorbed at the electronic device in the second gas-liquid phase heat exchanger 19 and obtaining enthalpy (as indicated by an arrow 190 in fig. 16), and recovering heat of the electronic device to recover heat to the heat of the air conditioning system. The gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the second heat exchanger 19 is divided into a gas-phase refrigerant and a liquid-phase refrigerant in the gas-liquid separating device 6, the gas-phase refrigerant flows out from the gas outlet of the gas-liquid separating device 6 (as shown by a point 600 in fig. 16) and enters the first heat exchanger 3, the gas-phase refrigerant absorbs heat in the first heat exchanger 3 to obtain enthalpy lost in the first heat exchanger 3 by the refrigerant flowing out of the outlet of the outdoor heat exchanger 2 (as shown by an arrow 300b in fig. 16), so that a small amount of liquid-phase refrigerant carried in the gas-phase refrigerant separated by the gas-liquid separating device 6 is evaporated into the gas-phase refrigerant, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 is located in a superheated steam zone, and the gas-phase refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1.

A seventh mode: the second heat pump comprises a waste heat recovery heating mode. In this mode, as shown in fig. 17, the first stop valve 12 is opened, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is closed, the second expansion valve 15 is opened, and the third expansion valve 20 is opened. As shown in fig. 17 and 18, 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. 18), 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. 18), 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 of which flows into the second expansion valve 15 and has an isenthalpic pressure drop in the second expansion valve 15 and passes through a saturated liquid line (as indicated by an arrow 150 in fig. 18), and the outlet of the second expansion valve 15 flows out a low-temperature and low-pressure gas-liquid two-phase mixed-state refrigerant, which absorbs heat of the outside atmosphere and obtains enthalpy (as indicated by an arrow 200 in fig. 18) in the outdoor heat exchanger 2; another flow of the refrigerant flows into the third expansion valve 20, the enthalpy pressure of the refrigerant in the third expansion valve 20 decreases, and the refrigerant passes through a saturated liquid line (as shown by an arrow 2000 in fig. 18), a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out from an outlet of the third expansion valve 20, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat of the high-temperature coolant absorbing heat from the electronic device in the second heat exchanger 19 and obtains enthalpy (as shown by an arrow 190 in fig. 18), so that the heat of the electronic device is recovered to the air conditioning system, the gas-liquid two-phase mixed refrigerant flowing out from an outlet of the outdoor heat exchanger 2 and the gas-liquid two-phase mixed refrigerant flowing out from a refrigerant outlet of the second heat exchanger 19 converge and enter the gas-liquid separator 6, and are separated into the gas-liquid refrigerant in the gas-liquid separator 6, and the gas refrigerant flows out from a gas outlet of the gas-liquid separator 6 (as shown by a point 600 in fig. 18) and flows back to the compressor 1 through the first heat exchanger 3. In this mode, the refrigerant flowing out of the gas-liquid separator 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a through-flow passage in this mode.

And a mode eight: a first dehumidification mode. In this mode, as shown in fig. 19, the first stop valve 12 is closed, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is closed, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is opened. As shown in fig. 19 and 20, 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. 20), 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 (indicated by an arrow 700 in fig. 20), thereby balancing the temperature in the passenger compartment. The refrigerant after heat release flowing out of the outlet of the interior condenser 7 has a reduced enthalpy pressure in the second expansion valve 15 and passes through a saturated liquid line (as indicated by an arrow 150 in fig. 20), the refrigerant in a gas-liquid two-phase mixed state having a low temperature and a low pressure flows out of the outlet of the second expansion valve 15, the refrigerant in a gas-liquid two-phase mixed state having a low temperature and a low pressure absorbs heat of the outside atmosphere and obtains enthalpy in the exterior heat exchanger 2 (as indicated by an arrow 200 in fig. 20), the refrigerant flowing out of the outlet of the exterior heat exchanger 2 flows into the first heat exchanger 3 and loses enthalpy in the first heat exchanger 3 by heat release (as indicated by an arrow 300a in fig. 20), the refrigerant flowing out of the first refrigerant outlet B of the first heat exchanger 3 has a reduced enthalpy pressure in the first expansion valve 4 (as indicated by an arrow 400 in fig. 20), the refrigerant in a gas-liquid two-phase having a low temperature and a low pressure flows into the interior evaporator 5 and absorbs heat and obtains enthalpy (as indicated by an arrow 500 in fig. 20), and the humid air in the interior of the passenger compartment is dehumidified by the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the interior evaporator 5 is divided into a gas-phase refrigerant and a liquid-phase refrigerant in the gas-liquid separating device 6, the gas-phase refrigerant flows out from the gas outlet of the gas-liquid separating device 6 (as shown by a point 600 in fig. 20) and enters the first heat exchanger 3, the gas-phase refrigerant absorbs heat in the first heat exchanger 3, enthalpy lost in the first heat exchanger 3 by the refrigerant flowing out of the outlet of the exterior heat exchanger 2 (as shown by an arrow 300b in fig. 20) is obtained, so that a small amount of liquid-phase refrigerant carried in the gas-phase refrigerant separated by the gas-liquid separating device 6 is evaporated into the gas-phase refrigerant, the refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 is positioned in a superheated steam region, and the gas-phase refrigerant flowing out of the second refrigerant outlet D of the first heat exchanger 3 returns to the compressor 1.

The mode nine: and a second dehumidification mode. In this mode, as shown in fig. 21, the first stop valve 12 is closed, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is opened, the second expansion valve 15 is closed, and the third expansion valve 20 is closed. As shown in fig. 21 and 22, 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 (as indicated by an arrow 100 in fig. 22), 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. 22) so as to balance the temperature in the passenger compartment. The refrigerant after heat release flowing out from the outlet of the interior condenser 7 has an equal enthalpy pressure drop in the first expansion valve 4 and passes through a saturated liquid line (as shown by an arrow 400 in fig. 22), the refrigerant in a gas-liquid two-phase mixed state with a low temperature and a low pressure flows out from the outlet of the first expansion valve 4, the refrigerant in the gas-liquid two-phase mixed state with the low temperature and the low pressure flows into the interior evaporator 5, absorbs heat in the interior evaporator 5 and obtains enthalpy (as shown by an arrow 500 in fig. 22), and when the humid air in the passenger compartment meets the interior evaporator 5 with a low temperature, condensed water is formed on the surface of the interior evaporator 5, so that the humidity of the air in the passenger compartment is reduced, and the passenger compartment dehumidification function is realized. The gas-liquid two-phase mixed refrigerant having an increased temperature flowing out of the outlet of the interior evaporator 5 is separated into a gas refrigerant and a liquid refrigerant in the gas-liquid separator 6, and the gas refrigerant flows out of the gas outlet of the gas-liquid separator 6 (as indicated by a point 600 in fig. 22) and returns to the compressor 1 through the first heat exchanger 3. In this mode, the refrigerant flowing out of the gas-liquid separator 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a through-flow passage in this mode.

And a tenth mode: and a third dehumidification mode. In this mode, as shown in fig. 23, the first stop valve 12 is opened, the second stop valve 13 is opened, the third stop valve 14 is closed, the fourth stop valve 21 is opened, the first expansion valve 4 is opened, the second expansion valve 15 is opened, and the third expansion valve 20 is closed. As shown in fig. 23 and 24, 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 (as indicated by an arrow 100 in fig. 24), 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. 24), thereby balancing the temperature in the passenger compartment. The refrigerant flowing out of the outlet of the interior condenser 7 is divided into two streams, one of which flows into the second expansion valve 15 and has an equal enthalpy pressure drop in the second expansion valve 15 and passes through a saturated liquid line (as indicated by an arrow 150 in fig. 24), and the outlet of the second expansion valve 15 flows out of a low-temperature and low-pressure gas-liquid two-phase mixed-state refrigerant, which absorbs heat of the outside atmosphere and obtains enthalpy (as indicated by an arrow 200 in fig. 24) in the exterior heat exchanger 2; the other flow of the refrigerant flows into the first expansion valve 4, the enthalpy pressure of the refrigerant in the first expansion valve 4 drops and passes through a saturated liquid line (as shown by an arrow 400 in fig. 24), a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out of an outlet of the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant enters the interior evaporator 5 and absorbs heat in the interior evaporator 5 to obtain enthalpy (as shown by an arrow 500 in fig. 24), and when the humid air in the passenger compartment meets the interior evaporator 5 with lower temperature, condensed water is formed on the surface of the interior evaporator 5, so that the humidity of the air in the passenger compartment is reduced, and the dehumidifying function of the passenger compartment is realized. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 2 and the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior evaporator 5 merge together and enter the gas-liquid separator 6, and are separated into a gas refrigerant and a liquid refrigerant in the gas-liquid separator 6, and the gas refrigerant flows out of the gas outlet of the gas-liquid separator 6 (as shown by a point 600 in fig. 24) and flows through the first heat exchanger 3 to return to the compressor 1. In this mode, the refrigerant flowing out of the gas-liquid separator 6 does not exchange heat in the first heat exchanger 3, that is, the first heat exchanger 3 is used as a through-flow passage in this mode.

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

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 spirit 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 heat exchanger (3), a first expansion valve (4) and an indoor evaporator (5),

the outlet of the compressor (1) is connected with the inlet of the outdoor heat exchanger (2), the outlet of the outdoor heat exchanger (2) is connected with a first refrigerant inlet (A) of the first heat exchanger (3), a first refrigerant outlet (B) of the first heat exchanger (3) is connected with the inlet of the indoor evaporator (5) through the first expansion valve (4), the outlet of the indoor evaporator (5) is connected with a second refrigerant inlet (C) of the first heat exchanger (3), and a second refrigerant outlet (D) of the first heat exchanger (3) is connected with the inlet of the compressor (1).

2. The heat pump air conditioning system according to claim 1, further comprising a gas-liquid separation device (6), wherein an outlet of the interior evaporator (5) is connected to an inlet of the gas-liquid separation device (6), and an outlet of the gas-liquid separation device (6) is connected to the second refrigerant inlet (C) of the first heat exchanger (3).

3. Heat pump air conditioning system according to claim 2, characterized in that it further comprises an indoor condenser (7), a through-flow path (8) and a throttle flow path (9),

the outlet of the compressor (1) is connected with the inlet of the through-flow path (8) and the inlet of the indoor condenser (7), the outlet of the indoor condenser (7) is connected with the inlet of the throttling flow path (9), the outlet of the through-flow path (8) and the outlet of the throttling flow path (9) are connected with the inlet of the outdoor heat exchanger (2), and the outlet of the outdoor heat exchanger (2) is further connected with the inlet of the gas-liquid separation device (6) through a first flow path (10) which is selectively conducted or cut off.

4. A heat pump air conditioning system according to claim 3, characterized in that the outlet of the compressor (1) is connected to the inlet of the indoor condenser (7) via a second flow path (11) which is selectively opened or closed.

5. The heat pump air conditioning system according to claim 4, wherein a first stop valve (12) is provided in the first flow path (10), a second stop valve (13) is provided in the second flow path (11), a third stop valve (14) is provided in the through-flow path (8), and a second expansion valve (15) is provided in the throttle flow path (9).

6. Heat pump air conditioning system according to claim 2, characterized in that it further comprises an indoor condenser (7), a through-flow path (8) and a throttle flow path (9),

the outlet of the compressor (1) is connected with the inlet of the indoor condenser (7), the outlet of the indoor condenser (7) is selectively connected with the inlet of the outdoor heat exchanger (2) through the through flow path (8) or the throttling flow path (9), and the outlet of the outdoor heat exchanger (2) is also connected with the inlet of the gas-liquid separation device (6) through a first flow path (10) which is selectively communicated or closed.

7. The heat pump air conditioning system according to claim 6, characterized in that a first shut-off valve (12) is provided on the first flow path (10), a third shut-off valve (14) is provided on the through-flow path (8), and a second expansion valve (15) is provided on the throttle flow path (9); or,

the heat pump air-conditioning system further comprises an expansion switch valve (16), an outlet of the indoor condenser (7) is connected with an inlet of the outdoor heat exchanger (2) through the expansion switch valve (16), the through flow path (8) is a through flow path in the expansion switch valve (16), and the throttling flow path (9) is a throttling flow path in the expansion switch valve (16).

8. The heat pump air conditioning system according to any one of claims 3 to 7, wherein the outlet of the interior condenser (7) is further connected to the inlet of the first expansion valve (4) via a third flow path (17) that is selectively opened or closed, and the first refrigerant outlet (B) of the first heat exchanger (3) is connected to the inlet of the first expansion valve (4) via a check valve (18).

9. The heat pump air conditioning system according to any one of claims 3 to 7, further comprising a second heat exchanger (19) and a third expansion valve (20), wherein the first refrigerant outlet (B) of the first heat exchanger (3) is further connected to a refrigerant inlet of the second heat exchanger (19) via the third expansion valve (20), the refrigerant outlet of the second heat exchanger (19) is connected to an inlet of the gas-liquid separation device (6), the first coolant outlet of the second heat exchanger (19) is configured to be connected to an inlet of an electronic device of a vehicle, and the first coolant inlet of the second heat exchanger (19) is configured to be connected to an outlet of the electronic device.

10. The heat pump air conditioning system according to claim 9, wherein the outlet of the indoor condenser (7) is further connected to the inlet of the first expansion valve (4) and the inlet of the third expansion valve (20) via a third flow path (17) that is selectively opened or closed, and the first refrigerant outlet (B) of the first heat exchanger (3) is connected to the inlet of the first expansion valve (4) and the inlet of the third expansion valve (20) through a check valve (18).

11. The heat pump air conditioning system according to claim 10, characterized in that a fourth shutoff valve (21) is provided on the third flow path (17).

12. The heat pump air conditioning system of claim 9, wherein the electronics comprise at least one of a motor, a charger, a motor controller, a DC-DC converter.

13. The heat pump air conditioning system of claim 9, wherein the second coolant outlet of the second heat exchanger (19) 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 (19) is adapted to be connected to an outlet of the battery pack.

14. A vehicle comprising a heat pump air conditioning system according to any one of claims 1 to 13.