CN114801656A

CN114801656A - Heat pump air conditioning system and vehicle

Info

Publication number: CN114801656A
Application number: CN202110118929.4A
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: 2021-01-28
Filing date: 2021-01-28
Publication date: 2022-07-29

Abstract

The invention relates to a heat pump air-conditioning system and a vehicle, the system comprises a compressor, an indoor condenser, an indoor evaporator, an outdoor heat exchanger, a first flow path and a second flow path which are selectively conducted or cut off, an outlet of the compressor is connected with an inlet of the indoor condenser and is connected with an inlet of the outdoor heat exchanger through the first flow path, an outlet of the indoor condenser is connected with a first refrigerant inlet of the first heat exchanger, a first refrigerant outlet of the first heat exchanger is connected with an inlet of the outdoor heat exchanger through a first expansion valve, an outlet of the outdoor heat exchanger is connected with a first refrigerant inlet of the second heat exchanger and is connected with a second refrigerant inlet of the first heat exchanger through a second flow path, a first refrigerant outlet of the second heat exchanger is connected with an inlet of the indoor evaporator through a second expansion valve, an outlet of the indoor evaporator and a second refrigerant outlet of the first heat exchanger are both connected with a second inlet of the second heat exchanger, and a second refrigerant outlet of the second heat exchanger is connected with an inlet of the compressor.

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 between the refrigerant and the outside atmosphere in the outdoor heat exchanger is affected by the ambient temperature, for example, when the outside ambient temperature is high, 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 at high temperature are poor.

In the heating working condition of the existing vehicle heat pump air-conditioning system, high-temperature and high-pressure gaseous refrigerant discharged by the compressor releases heat to a passenger compartment at the indoor condenser, and the refrigerant after heat release is throttled and depressurized by the throttle valve, absorbs and carries heat of outside atmosphere in the outdoor heat exchanger, and then returns to the compressor. Because the refrigerant needs to carry the heat of the outside atmosphere before returning to the compressor, the heat exchange amount between the refrigerant and the outside atmosphere in the outdoor heat exchanger is affected by the ambient temperature, for example, when the outside ambient temperature is low, the heat absorption amount of the refrigerant in the outdoor heat exchanger is limited, so that the heating effect and the heating efficiency of the vehicle heat pump air-conditioning system at low temperature are poor.

Disclosure of Invention

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

In order to accomplish the above objects, the present disclosure provides a heat pump air conditioning system including a compressor, an indoor condenser, an indoor evaporator, an outdoor heat exchanger, a first heat exchanger, a second heat exchanger, a first expansion valve, a second expansion valve, a first flow path selectively opened or closed, a second flow path selectively opened or closed,

an outlet of the compressor is connected to an inlet of the indoor condenser and to an inlet of the outdoor heat exchanger via the first flow path, an outlet of the indoor condenser is connected with a first refrigerant inlet of the first heat exchanger, a first refrigerant outlet of the first heat exchanger is connected with an inlet of the outdoor heat exchanger through the first expansion valve, an outlet of the outdoor heat exchanger is connected with a first refrigerant inlet of the second heat exchanger, and is connected to a second refrigerant inlet of the first heat exchanger via the second flow path, a first refrigerant outlet of the second heat exchanger is connected to an inlet of the interior evaporator via the second expansion valve, an outlet of the indoor evaporator and a second refrigerant outlet of the first heat exchanger are both connected with a second refrigerant inlet of the second heat exchanger, and a second refrigerant outlet of the second heat exchanger is connected with an inlet of the compressor.

Optionally, the heat pump air conditioning system further comprises a first liquid storage drying tank and a second liquid storage drying tank, an outlet of the indoor condenser is connected with an inlet of the first liquid storage drying tank, a liquid outlet of the first liquid storage drying tank is connected with a first refrigerant inlet of the first heat exchanger, an outlet of the outdoor heat exchanger is connected with an inlet of the second liquid storage drying tank, and a liquid outlet of the second liquid storage drying tank is connected with a first refrigerant inlet of the second heat exchanger.

Optionally, the heat pump air conditioning system further includes a subcooler located downstream of the second liquid storage drying tank, and a liquid outlet of the second liquid storage drying tank is connected to the first refrigerant inlet of the second heat exchanger via the subcooler.

Optionally, the heat pump air conditioning system further includes a third flow path that is selectively opened or closed, and the liquid outlet of the first liquid storage drying tank is further connected to the inlet of the second expansion valve via the third flow path.

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

Optionally, the liquid outlet of the first liquid storage drying tank is further connected with an inlet of the third expansion valve via the third flow path, the second cooling liquid outlet of the third heat exchanger is used for being connected with an inlet of an electronic device of a vehicle, and the second cooling liquid inlet of the third heat exchanger is used for being connected with an outlet of the electronic device.

Optionally, the heat pump air conditioning system further includes a check valve, and the first refrigerant outlet of the second heat exchanger is connected to the inlet of the second expansion valve and the inlet of the third expansion valve via the check valve.

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

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

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

Compared with the prior art that the refrigerant flowing out of the outlet of the indoor condenser directly flows into the outdoor heat exchanger through the expansion valve without enthalpy value reduction, and the refrigerant flowing out of the outlet of the outdoor heat exchanger flows into the compressor without enthalpy value increase, the first heat exchanger is arranged, the first refrigerant inlet of the first heat exchanger is connected with the indoor condenser, the second refrigerant inlet is connected with the inlet of the outdoor heat exchanger through the expansion valve, the second refrigerant inlet is connected with the outlet of the outdoor heat exchanger, and the second refrigerant inlet is connected with the inlet of the compressor 1 through the second heat exchanger, so that on one hand, the supercooling degree of the refrigerant flowing into the outdoor heat exchanger can be increased, the evaporation capacity (i.e. the heat absorption capacity for absorbing heat to the outside atmosphere) of the refrigerant in the outdoor heat exchanger is improved, and the refrigerant can absorb more heat in the outdoor heat exchanger, on the other hand, the superheat degree of the refrigerant flowing out of the outdoor heat exchanger can be increased, the suction temperature and the suction pressure at the inlet of the compressor are improved, the heating capacity of the heat pump air-conditioning system in a low-temperature environment can be further improved, and the problem that the heat absorption capacity of the refrigerant at the outdoor heat exchanger is insufficient due to the limitation of the environment temperature under the condition that the environment temperature is low is solved.

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 outdoor heat exchange outlet and the refrigerant flowing out of the indoor evaporator to exchange heat in the second heat exchanger by arranging the second heat exchanger, further dissipates heat and cools the refrigerant flowing out of the outdoor heat exchanger, namely, the refrigerant can release heat twice through the outdoor heat exchanger and the second heat exchanger before entering the indoor evaporator, and the problem that the heat release amount of the refrigerant at the outdoor heat exchanger is insufficient due to the influence of the ambient temperature under the condition of higher ambient temperature is solved, so that the lost enthalpy and the released heat of the refrigerant before entering the indoor evaporator are more, and the supercooling degree of the refrigerant entering the indoor evaporator is favorably improved, and the refrigerant with lower temperature flows into the indoor evaporator, so that the heat pump air-conditioning system still has better refrigeration effect and refrigeration efficiency in a high-temperature environment, and the passenger compartment is cooled quickly. In other words, by arranging the second heat exchanger and enabling the refrigerant flowing out of the outlet of the outdoor heat exchanger to release heat in the second heat exchanger, the problems that the heat release amount of the refrigerant in the outdoor heat exchanger is limited and the refrigeration effect and the refrigeration efficiency are influenced in a high-temperature environment 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 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. 4 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. 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 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. 6 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. 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 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. 10 is a pressure-enthalpy diagram of a refrigerant in a heat pump heating mode of a heat pump air conditioning system 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 waste heat recovery 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 mode;

fig. 12 is a pressure-enthalpy diagram of a refrigerant in a waste heat recovery 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, where the heat pump air-conditioning system is in a heat pump waste heat recovery 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. 14 is a refrigerant pressure enthalpy diagram of the heat pump air conditioning system in the heat pump waste heat recovery mode 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, 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. 16 is a pressure-enthalpy diagram of a refrigerant of the heat pump air conditioning system in the first dehumidification mode according to an embodiment of the present disclosure;

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

Description of the reference numerals

1-a compressor; 2-indoor condenser; 3-indoor evaporator; 4-outdoor heat exchanger; 5-a first heat exchanger; 6-a second heat exchanger; 7-a first expansion valve; 8-a second expansion valve; 9-a first flow path; 10-a second flow path; 11-a first receiver drier; 12-a second receiver drier; 13-a subcooler; 14-a third flow path; 15-a one-way valve; 16-a third heat exchanger; 17-a third expansion valve; 18-a first shut-off valve; 19-a second stop valve; 20-third stop valve.

Detailed Description

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

In the present disclosure, unless otherwise stated, the term "connection" in the present disclosure may be a direct connection or an indirect connection between two devices or apparatuses, and the term "selectively opened or closed flow path" refers to a flow path in which a refrigerant can be opened or closed.

As shown in fig. 1 to 18, the present disclosure provides a heat pump air conditioning system including a compressor 1, an indoor condenser 2, an indoor evaporator 3, an outdoor heat exchanger 4, a first heat exchanger 5, a second heat exchanger 6, a first expansion valve 7, a second expansion valve 8, a first flow path 9 selectively opened or closed, and a second flow path 10 selectively opened or closed. An outlet of the compressor 1 is connected with an inlet of the indoor condenser 2 and is connected with an inlet of the outdoor heat exchanger 4 through a first flow path 9, an outlet of the indoor condenser 2 is connected with a first refrigerant inlet of the first heat exchanger 5, a first refrigerant outlet of the first heat exchanger 5 is connected with an inlet of the outdoor heat exchanger 4 through a first expansion valve 7, an outlet of the outdoor heat exchanger 4 is connected with a first refrigerant inlet of the second heat exchanger 6 and is connected with a second refrigerant inlet of the first heat exchanger 5 through a second flow path 10, a first refrigerant outlet of the second heat exchanger 6 is connected with an inlet of the indoor evaporator 3 through a second expansion valve 8, an outlet of the indoor evaporator 3 and a second refrigerant outlet of the first heat exchanger 5 are both connected with a second refrigerant inlet of the second heat exchanger 6, and a second refrigerant outlet of the second heat exchanger 6 is connected with an inlet of the compressor 1. The heat pump air conditioning system may have a heat pump heating mode or a cooling mode by controlling the on/off of the first flow path 9 and the second flow path 10.

In the heat pump heating mode, as shown in fig. 9, the first flow path 9 is closed, the second flow path 10 is open, and the compressor 1, the indoor condenser 2, the first refrigerant inlet of the first heat exchanger 5, the first refrigerant outlet of the first heat exchanger 5, the first expansion valve 7, the outdoor heat exchanger 4, the second refrigerant inlet of the first heat exchanger 5, the second refrigerant outlet of the first heat exchanger 5, and the second heat exchanger 6 are sequentially connected in series to form one refrigerant circuit. The high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the indoor condenser 2, and releases heat to the passenger compartment in the indoor condenser 2, thereby increasing the temperature of the passenger compartment and realizing heating of the passenger compartment. The refrigerant having a lowered enthalpy value after heat release flowing out of the outlet of the interior condenser 2 flows into the first heat exchanger 5 from the first refrigerant inlet of the first heat exchanger 5, releases heat to the refrigerant flowing into the first heat exchanger 5 from the second refrigerant inlet of the first heat exchanger 5 and loses enthalpy (as shown by an arrow 500a in fig. 10), the refrigerant flowing out of the first refrigerant outlet of the first heat exchanger 5 is throttled and depressurized in the first expansion valve 7 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant which absorbs heat of the outside air and obtains enthalpy in the exterior heat exchanger 4, the refrigerant flowing out of the outlet of the exterior heat exchanger 4 flows into the first heat exchanger 5 via the second flow path 10 and absorbs heat released from the refrigerant flowing into the first heat exchanger 5 from the outlet of the interior condenser 2 in the first heat exchanger 5 to obtain enthalpy again (as shown by an arrow 500b in fig. 10), finally, the refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 returns to the compressor 1. Here, no refrigerant flows into the second refrigerant inlet of the second heat exchanger 6, the refrigerant does not exchange heat in the second heat exchanger 6, and the second heat exchanger 6 is used as a through flow passage.

Compared with the prior art that the refrigerant flowing out of the outlet of the indoor condenser directly flows into the outdoor heat exchanger through the expansion valve without enthalpy value reduction, and the refrigerant flowing out of the outlet of the outdoor heat exchanger flows into the compressor without enthalpy value increase, the first heat exchanger 5 is arranged, the first refrigerant inlet of the first heat exchanger 5 is connected with the indoor condenser 2, the second refrigerant inlet is connected with the inlet of the outdoor heat exchanger 4 through the expansion valve, the second refrigerant inlet is connected with the outlet of the outdoor heat exchanger 4, and the second refrigerant inlet is connected with the inlet of the compressor 1 through the second heat exchanger 6, on one hand, the supercooling degree of the refrigerant flowing into the outdoor heat exchanger 4 can be increased, the evaporation capacity (namely, the heat absorption capacity for absorbing heat to the outside atmosphere) of the refrigerant in the outdoor heat exchanger 4 is improved, and more heat can be absorbed in the outdoor heat exchanger 4, on the other hand, the superheat degree of the refrigerant flowing out of the outdoor heat exchanger 4 can be increased, the suction temperature and the suction pressure at the inlet of the compressor 1 are improved, the heating capacity of the heat pump air-conditioning system in a low-temperature environment can be further improved, and the problem that the heat absorption capacity of the refrigerant at the outdoor heat exchanger 4 is insufficient due to the limitation of the environment temperature under the condition of low environment temperature is solved.

In the cooling mode, as shown in fig. 3, the first flow path 9 is turned on, the second flow path 10 is turned off, and the compressor 1, the outdoor heat exchanger 4, the first refrigerant inlet of the second heat exchanger 6, the first refrigerant outlet of the second heat exchanger 6, the second expansion valve 8, the indoor evaporator 3, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form a refrigerant circuit. A high-temperature and high-pressure gaseous refrigerant discharged from an outlet of the compressor 1 flows into the outdoor heat exchanger 4, radiates heat to the outside atmosphere in the outdoor heat exchanger 4, loses enthalpy in the outdoor heat exchanger 4, that is, the enthalpy of the refrigerant decreases (as shown by an arrow 400 in fig. 4), the refrigerant flowing out of the outlet of the outdoor heat exchanger 4 flows into the second heat exchanger 6 through the first refrigerant inlet of the second heat exchanger 6, radiates heat to the refrigerant flowing in from the second refrigerant inlet of the second heat exchanger 6 in the second heat exchanger 6, loses enthalpy again in the refrigerant flowing into the second heat exchanger 6 from the outlet of the outdoor heat exchanger 4, further decreases the enthalpy (as shown by an arrow 600a in fig. 4), the refrigerant flowing out of the first refrigerant outlet of the second heat exchanger 6 is decompressed by throttling by the first expansion valve 7 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the low-liquid two phase refrigerant absorbs heat of air in the passenger compartment in the indoor evaporator 3, the temperature in the passenger compartment is reduced, and the refrigeration of the passenger compartment is realized. The heat-absorbed refrigerant flowing out of the outlet of the interior evaporator 3 flows into the second heat exchanger 6, enthalpy lost by the refrigerant flowing into the second heat exchanger 6 from the outlet of the exterior heat exchanger 4 is obtained in the second heat exchanger 6, and the refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 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 second heat exchanger 6 by arranging the second heat exchanger 6, so that the refrigerant flowing out of the outlet of the outdoor heat exchanger 4 and the refrigerant flowing out of the outlet of the indoor evaporator 3 further dissipate heat and cool the refrigerant flowing out of the outlet of the outdoor heat exchanger 4, namely, the refrigerant can release heat twice through the outdoor heat exchanger 4 and the second heat exchanger 6 before entering the indoor evaporator 3, the problem that the heat release amount of the refrigerant is insufficient due to the influence of the environment temperature at the outdoor heat exchanger 4 under the condition of higher environment temperature is solved, therefore, the lost enthalpy value and the released heat of the refrigerant before entering the indoor evaporator 3 are more, and the supercooling degree of the refrigerant entering the indoor evaporator 3 is favorably improved, and the refrigerant with lower temperature flows into the indoor evaporator 3, so that the heat pump air-conditioning system still has better refrigeration effect and refrigeration efficiency in a high-temperature environment, and the passenger compartment is cooled quickly. In other words, by providing the second heat exchanger 6 and enabling the refrigerant flowing out of the outlet of the outdoor heat exchanger 4 to release heat in the second heat exchanger 6, the problems that the refrigerant has limited heat release in the outdoor heat exchanger 4 and affects the refrigeration effect and the refrigeration efficiency in a high-temperature environment can be solved.

In addition, before the refrigerant returns to the compressor 1, it is necessary to ensure that the gaseous refrigerant flows into the compressor 1 as much as possible, because once the liquid refrigerant flows into the compressor 1, a liquid impact occurs in the compressor 1, which affects the service life of the compressor 1. In the prior art, in order to ensure that the gaseous refrigerant flows into the compressor as much as possible, a gas-liquid separation device is generally arranged at an inlet of the compressor, so that the refrigerant returning to the compressor firstly passes through the gas-liquid separation device to be subjected to gas-liquid separation and then returns to the compressor. However, since the gas-liquid separator cannot completely separate the gaseous refrigerant from the liquid refrigerant, the gaseous refrigerant separated by the gas-liquid separator still carries a small amount of liquid refrigerant. Therefore, in the prior art, in order to solve the above problem, the superheat degree of the refrigerant at the inlet of the compressor is usually controlled to be 0, that is, the refrigerant at the inlet of the compressor is located on a saturated vapor line of the refrigerant (refer to the saturated vapor line shown in fig. 4), so that the refrigerant is changed into a pure gaseous refrigerant, and thus, a small amount of liquid refrigerant carried in the gaseous refrigerant separated by the gas-liquid separation device is prevented from causing liquid impact on the compressor. However, the control of the degree of superheat of the refrigerant usually requires complicated calculations and subsequent control of components such as an expansion valve and a compressor, which makes the control of the heat pump air conditioning system very complicated.

However, in the present application, for the heat pump heating mode, the refrigerant absorbs heat and obtains enthalpy in the first heat exchanger 5 before returning to the compressor 1, which enables the refrigerant to pass through a saturated vapor line (as shown by an arrow 500b in fig. 10), so that the refrigerant is located in a superheated vapor region, i.e., the refrigerant is in a pure gas state; for the cooling mode, the refrigerant absorbs heat and gains enthalpy in the second heat exchanger 6 before returning to the compressor 1, which enables the refrigerant to pass through a saturated vapor line (as shown by arrow 600b in fig. 4), thereby placing the refrigerant in a superheated vapor region, i.e., the refrigerant is in a pure gas state. Therefore, for the heat pump heating mode and the cooling mode, the refrigerant entering the compressor 1 can be a pure gaseous refrigerant without complex superheat degree control, the condition of liquid impact of the compressor 1 is avoided, and the control complexity of the heat pump air-conditioning system is reduced.

It is understood that in the battery pack cooling mode, the refrigeration and battery pack cooling mode, the heat pump waste heat recovery mode, and the first dehumidification mode, which will be mentioned later, the refrigerant obtains enthalpy in at least one of the first heat exchanger 5 and the second heat exchanger 6 before returning to the compressor 1 and is located in the superheated steam zone through the saturated steam line, so that no complicated superheat control is required for the battery pack cooling mode, the refrigeration and battery pack cooling mode, the heat pump waste heat recovery mode, and the first dehumidification mode.

For the further increase at the degree of supercooling of the refrigerant of heat pump heating mode from the export outflow of interior condenser 2, the degree of supercooling of the refrigerant that gets into outdoor heat exchanger 4 of increase promptly to further promote the heating effect and the heating efficiency of the heat pump air conditioning system under low temperature environment that this disclosure provides, in an embodiment that this disclosure provided, heat pump air conditioning system still includes first stock solution drying tank 11, the export of interior condenser 2 and the entry linkage of first stock solution drying tank 11, the liquid outlet of first stock solution drying tank 11 and the first refrigerant entry linkage of first heat exchanger 5. The first liquid storage drying tank 11 can enable a liquid refrigerant in a gas-liquid two-phase mixed refrigerant flowing out of an outlet of the indoor condenser 2 to flow into the first heat exchanger 5, so that the supercooling degree of the refrigerant entering the first heat exchanger 5 is improved, the heat release quantity of the refrigerant in the first heat exchanger 5 is improved, the temperature of the refrigerant entering the outdoor heat exchanger 4 can be lower, and the refrigerant can absorb more external atmospheric heat, namely, more heat is transported to the heat pump air conditioning system from the outside.

For further increase from the super-cooled degree of the refrigerant of the export outflow of outdoor heat exchanger 4 under refrigeration mode, the super-cooled degree of the refrigerant that the increase got into indoor evaporator 3 promptly and refrigeration effect and refrigeration efficiency under high temperature environment, in an embodiment that this disclosure provided, heat pump air conditioning system still includes second stock solution drying tank 12, the export of outdoor heat exchanger 4 and the entry linkage of second stock solution drying tank 12, the liquid outlet of second stock solution drying tank 12 and the first refrigerant entry linkage of second heat exchanger 6. The second liquid storage drying tank 12 can enable a liquid refrigerant in a gas-liquid two-phase mixed refrigerant flowing out of an outlet of the outdoor heat exchanger 4 to flow into the second heat exchanger 6, so that the supercooling degree of the refrigerant entering the second heat exchanger 6 is improved, the heat release quantity of the refrigerant in the second heat exchanger 6 is improved, the temperature of the refrigerant entering the indoor evaporator 3 can be lower, the refrigerant can absorb heat of more passenger compartments, and the passenger compartments can be cooled quickly.

Optionally, the heat pump air conditioning system may further include a subcooler 13 located downstream of the second receiver-drier tank 12, and a liquid outlet of the second receiver-drier tank 12 is connected to the first refrigerant inlet of the second heat exchanger 6 via the subcooler 13. Here, the subcooler 13 may further cool the liquid refrigerant flowing out of the liquid outlet of the second receiver-drier tank 12, thereby further increasing the degree of subcooling of the refrigerant entering the second heat exchanger 6.

In order to enable the heat pump air conditioning system provided by the present disclosure to have more operation modes to meet different requirements of users, optionally, the heat pump air conditioning system may further include a third flow path 14 selectively opened or closed, and the liquid outlet of the first liquid storage drying tank 11 is further connected with the inlet of the second expansion valve 8 via the third flow path 14. In this way, the refrigerant flowing out of the outlet of the interior condenser 2 can flow into the interior evaporator 3 sequentially through the first receiver/drier tank 11 and the second expansion valve 8 by controlling the conduction of the third flow path 14, and the heat pump air conditioning system provided by the present disclosure can have the first dehumidification mode and the second dehumidification mode by controlling the conduction or the cutoff of the first flow path 9 and the second flow path 10 when the third flow path 14 is conducted.

Specifically, in the first dehumidification mode, as shown in fig. 15, the first flow path 9 is closed, the second flow path 10 is open, the third flow path 14 is open, the compressor 1, the interior condenser 2, the first receiver/drier tank 11, the first refrigerant inlet of the first heat exchanger 5, the first refrigerant outlet of the first heat exchanger 5, the first expansion valve 7, the exterior heat exchanger 4, the second refrigerant inlet of the first heat exchanger 5, the second refrigerant outlet of the first heat exchanger 5, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form one refrigerant circuit, and the compressor 1, the interior condenser 2, the first receiver/drier tank 11, the second expansion valve 8, the interior evaporator 3, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form another refrigerant circuit. In the first dehumidification mode, a high-temperature and high-pressure gaseous refrigerant discharged from an outlet of the compressor 1 enters the indoor condenser 2 and releases heat to the passenger compartment in the indoor condenser 2, a gas-liquid two-phase mixed refrigerant flowing out of an outlet of the indoor condenser 2 is separated into a gaseous state and a liquid state in the first liquid storage drying tank 11, the liquid refrigerant flows out of a liquid outlet of the first liquid storage drying tank 11 and is divided into two streams, one stream of the refrigerant flows into the indoor evaporator 3 after being throttled and depressurized by the second expansion valve 8, and when wet air with higher temperature in the passenger compartment meets the indoor evaporator 3 with lower temperature, the wet air is condensed into water drops on the surface of the indoor evaporator 3 to form condensed water, so that the air humidity in the passenger compartment can be reduced; the other refrigerant flows into the first heat exchanger 5, releases heat and loses enthalpy in the first heat exchanger 5, is throttled and depressurized by the first expansion valve 7, flows into the outdoor heat exchanger 4, absorbs external heat in the outdoor heat exchanger 4, enters the first heat exchanger 5 from the refrigerant flowing out of the outlet of the outdoor heat exchanger 4, absorbs heat in the first heat exchanger 5 to obtain enthalpy, and flows back to the compressor 1 from the second refrigerant outlet of the first heat exchanger 5 and the refrigerant flowing out of the outlet of the indoor evaporator 3 after converging. Since the indoor evaporator 3 and the indoor condenser 2 are simultaneously operated, the temperature in the passenger compartment can be balanced while dehumidifying the passenger compartment.

In the second dehumidification mode, as shown in fig. 17, the first flow path 9 is closed, the second flow path 10 is closed, and the third flow path 14 is opened, and the compressor 1, the interior condenser 2, the first receiver/drier tank 11, the second expansion valve 8, the interior evaporator 3, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form one refrigerant circuit. In this mode, all the refrigerant flowing out of the liquid outlet of the first receiver/drier tank 11 is throttled and depressurized by the second expansion valve 8 and then flows out of the interior evaporator 3.

The first dehumidification mode and the second dehumidification mode are different in that whether or not the refrigerant flowing out of the liquid outlet of the first receiver-drier tank 11 partially flows into the outdoor heat exchanger 4 through the first heat exchanger 5 and the first expansion valve 7 in sequence, and absorbs heat of the external atmosphere in the outdoor heat exchanger 4 to carry heat of the external environment. Since in the first dehumidification mode, the refrigerant flowing out of the liquid outlet of the first liquid storage drying tank 11 is divided into two streams, and one stream of the refrigerant flows into the outdoor heat exchanger 4 through the first heat exchanger 5 and the first expansion valve 7 in sequence to carry heat in the external environment, while in the second dehumidification mode, the refrigerant flowing out of the liquid outlet of the first liquid storage drying tank 11 does not flow into the outdoor heat exchanger 4 but flows into the indoor evaporator 3 completely without carrying heat in the external environment, the ambient temperature that the first dehumidification mode can be applied to may be lower than the ambient temperature that the second dehumidification mode can be applied to, for example, the first dehumidification mode may be applied to the case where the ambient temperature is 5 ℃ to 10 ℃, and the second dehumidification mode may be applied to the case where the ambient temperature is 10 ℃ to 15 ℃. The first dehumidification mode and the second dehumidification mode are set, so that the heat pump air conditioning system can operate in different dehumidification modes according to different environmental temperatures, and the influence of the external environmental temperature on the dehumidification effect is reduced as much as possible.

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 during quick charging, the heat pump air conditioning system may further include a third heat exchanger 16 and a third expansion valve 17, the first refrigerant outlet of the second heat exchanger 6 is further connected to the refrigerant inlet of the third heat exchanger 16 via the third expansion valve 17, the refrigerant outlet of the third heat exchanger 16 is connected to the second refrigerant inlet of the second heat exchanger 6, the first coolant outlet of the third heat exchanger 16 is used for being connected to the inlet of the battery pack of the vehicle, and the first coolant inlet of the third heat exchanger 16 is used for being connected to the outlet of the battery pack.

In the battery pack cooling mode, as shown in fig. 5, the first flow path 9 is turned on, the second flow path 10 is turned off, and the compressor 1, the outdoor heat exchanger 4, the second receiver/drier 12, the first refrigerant inlet of the second heat exchanger 6, the first refrigerant outlet of the second heat exchanger 6, the third expansion valve 17, the third heat exchanger 16, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form one refrigerant circuit. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 4 is divided into gas and liquid in the second liquid storage drying tank 12, the liquid refrigerant flows into the second heat exchanger 6 and releases heat and loses enthalpy in the second heat exchanger 6, the refrigerant flowing out of the first refrigerant outlet of the second heat exchanger 6 enters the third heat exchanger 16 after throttling and pressure reduction through the third expansion valve 17, and absorbs the heat of the cooling liquid in the third heat exchanger 16, so that the low-temperature cooling liquid can flow out of the first cooling liquid outlet of the third heat exchanger 16 and is used for absorbing the heat of the battery pack, and the purpose of cooling the battery pack by using the cold energy of the heat pump air conditioning system is achieved. In the battery pack cooling mode, the second liquid storage drying tank 12 and the second heat exchanger 6 can both improve the supercooling degree of the refrigerant flowing into the third heat exchanger 16, so that the refrigerant in the third heat exchanger 16 can absorb more heat, and the battery pack can be rapidly cooled.

The battery pack cooling mode can be operated simultaneously with the refrigeration mode, so that the heat pump air conditioning system provided by the disclosure can have a series-parallel mode of the refrigeration and battery pack cooling modes. As shown in fig. 7, in the cooling and battery pack cooling mode, the refrigerant flowing out of the first refrigerant outlet of the second heat exchanger 6 is divided into two streams, one stream is throttled and depressurized by the second expansion valve 8 and then flows into the indoor evaporator 3 to absorb the heat of the passenger compartment; the other stream is throttled and depressurized by a third expansion valve 17 and flows into a third heat exchanger 16 to absorb the heat of the high-temperature cooling liquid absorbing heat from the battery pack, so that the cooling of the battery pack and the refrigeration of the passenger compartment are realized at the same time.

In order to enable the heat pump air conditioning system to realize the passenger compartment heating function without carrying external heat through the outdoor heat exchanger 4, in an embodiment provided by the disclosure, the liquid outlet of the first liquid storage drying tank 11 is further connected with the inlet of the third expansion valve 17 through the third flow path 14, the second coolant outlet of the third heat exchanger 16 is used for being connected with the inlet of an electronic device of a vehicle, and the second coolant inlet of the third heat exchanger 16 is used for being connected with the outlet of the electronic device.

As shown in fig. 11, in the waste heat recovery mode, the first flow path 9 is closed, the second flow path 10 is closed, and the third flow path 14 is opened, and the compressor 1, the interior condenser 2, the first receiver/drier tank 11, the third expansion valve 17, the third heat exchanger 16, the second refrigerant inlet of the second heat exchanger 6, and the second refrigerant outlet of the second heat exchanger 6 are sequentially connected in series to form a single refrigerant circuit. In this mode, a high-temperature and high-pressure gaseous refrigerant discharged from the outlet of the compressor 1 flows into the indoor condenser 2, heat is released to the passenger compartment at the indoor condenser 2 to heat the passenger compartment, the refrigerant flowing out of the outlet of the indoor condenser 2 flows into the first receiver-drier 11, a liquid refrigerant flows out of the liquid outlet of the first receiver-drier 11, is throttled and depressurized by the third expansion valve 17, flows into the third heat exchanger 16, absorbs heat of a high-temperature coolant absorbing heat from an electronic device at the third heat exchanger 16, the enthalpy of the refrigerant in the third heat exchanger 16 increases, and the refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 finally returns to the compressor 1. In this mode. The refrigerant carries the heat emitted by the electronic device during operation to the heat pump air conditioning system through the third heat exchanger 16, so that the heat of the electronic device is utilized to heat the passenger compartment while the electronic device is cooled.

In addition, the heat pump air conditioning system may further have a heat pump waste heat recovery mode, in which, as shown in fig. 13, the first flow path 9 is closed, the second flow path 10 is open, and the third flow path 14 is open, and the refrigerant flowing out of the liquid outlet of the first liquid storage drying tank 11 is divided into two flows, one of the flows is throttled and depressurized by the third expansion valve 17 and flows into the third heat exchanger 16 to absorb heat of the electronic device, and the other flows sequentially through the first heat exchanger 5 and the first expansion valve 7 and then flows into the outdoor heat exchanger 4 to absorb heat of the outside atmosphere. That is, in the heat pump waste heat recovery mode, the refrigerant carries the heat dissipated by the electronic device during operation and the heat in the external environment to the heat pump air conditioning system through the third heat exchanger 16 and the outdoor heat exchanger 4, respectively.

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

Optionally, the heat pump air conditioning system further includes a check valve 15, and the first refrigerant outlet of the second heat exchanger 6 is connected to the inlet of the second expansion valve 8 and the inlet of the third expansion valve 17 via the check valve 15. As shown in fig. 11 and 17, the check valve 15 may be provided to prevent the refrigerant in the third heat exchanger 16 and the interior evaporator 3 from flowing backward to the second heat exchanger 6 in the heat recovery mode and the second dehumidification mode.

Alternatively, the first heat exchanger 5 and the second heat exchanger 6 mentioned above may be plate heat exchangers or coaxial tubes, and the third heat exchanger 16 may be a plate heat exchanger or a tube heat exchanger, and the present disclosure does not limit the specific types of the first heat exchanger 5, the second heat exchanger 6, and the third heat exchanger 16.

In order to selectively connect or disconnect the first flow path 9, the second flow path 10, and the third flow path 14, in one embodiment provided by the present disclosure, a first shutoff valve 18 may be provided on the first flow path 9, a second shutoff valve 19 may be provided on the second flow path 10, and a third shutoff valve 20 may be provided on the third flow path 14. In another embodiment, the first flow path 9 may be provided with a first on-off valve, the second flow path 10 may be provided with a second on-off valve, and the third flow path 14 may be provided with a third on-off valve.

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. 3 to 18 by taking the embodiment in fig. 1 as an example. The cycle cost and the principle of the system under other embodiments (e.g., fig. 2) are similar to those of fig. 1, and are not described in detail herein.

The first mode is as follows: a cooling mode. In this mode, as shown in fig. 3, the first stop valve 18 is opened, the second stop valve 19 is closed, the third stop valve 20 is closed, the first expansion valve 7 is closed, the second expansion valve 8 is opened, and the third expansion valve 17 is closed. As shown in fig. 3 and 4, the refrigerant entering the compressor 1 is a pure 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 an arrow 100 in fig. 4), the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 4, releases heat to the outside atmosphere in the outdoor heat exchanger 4 to lose enthalpy (shown by an arrow 400 in fig. 4), the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 4 flows into the second liquid storage drying tank 12, the liquid refrigerant (shown by a point 120 in fig. 4) flows out of the liquid outlet of the second liquid storage drying tank 12 and flows into the second heat exchanger 6, continues to release heat to lose enthalpy (shown by an arrow 600a in fig. 4) in the second heat exchanger 6, the liquid refrigerant flows out of the first outlet of the second heat exchanger 6, the liquid refrigerant drops in pressure in the second expansion valve 8 and passes through a saturated liquid line (shown by an arrow 800 in fig. 4), the outlet of the second expansion valve 8 discharges a low-temperature and low-pressure gas-liquid two-phase refrigerant, which absorbs heat from the passenger compartment and obtains enthalpy (as indicated by an arrow 300 in fig. 4) in the interior evaporator 3 to lower the temperature of the passenger compartment and cool the passenger compartment. The gas-liquid two-phase mixed refrigerant flowing out of the outlet of the interior evaporator 3 flows into the second heat exchanger 6, absorbs heat in the second heat exchanger 6, and obtains enthalpy (as shown by an arrow 600b in fig. 4) lost by the refrigerant flowing out of the liquid outlet of the second liquid storage drying tank 12 in the second heat exchanger 6, so that the gas-liquid two-phase refrigerant flowing out of the interior evaporator 3 is changed into a gaseous refrigerant, that is, the refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 is located in a superheated steam region, and the pure gaseous refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 finally returns to the compressor 1.

And a second mode: battery pack cooling mode. In this mode, as shown in fig. 5, the first stop valve 18 is opened, the second stop valve 19 is closed, the third stop valve 20 is closed, the first expansion valve 7 is closed, the second expansion valve 8 is closed, and the third expansion valve 17 is opened. As shown in fig. 5 and 6, the refrigerant entering the compressor 1 is a pure 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 an arrow 100 in fig. 6), the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 4, releases heat to the outside atmosphere in the outdoor heat exchanger 4 to lose enthalpy (shown by an arrow 400 in fig. 6), the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 4 flows into the second liquid storage drying tank 12, the liquid refrigerant (shown by a point 120 in fig. 6) flows out of the liquid outlet of the second liquid storage drying tank 12 and flows into the second heat exchanger 6, continues to release heat to lose enthalpy (shown by an arrow 600a in fig. 6) in the second heat exchanger 6, the liquid refrigerant flows out of the first outlet of the second heat exchanger 6, the liquid refrigerant drops in pressure in the third expansion valve 17 and passes through a saturated liquid line (shown by an arrow 170 in fig. 6), the outlet of the third expansion valve 17 discharges a low-temperature and low-pressure gas-liquid two-phase refrigerant, which absorbs heat of the coolant in the third heat exchanger 16 and obtains enthalpy (as indicated by an arrow 160 in fig. 6), so that the first coolant outlet of the third heat exchanger 16 discharges a low-temperature coolant, which can absorb heat of the battery pack to cool the battery pack. The gas-liquid two-phase mixed refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 flows into the second heat exchanger 6, absorbs heat in the second heat exchanger 6, and obtains enthalpy (as shown by an arrow 600b in fig. 6) lost by the refrigerant flowing out of the liquid outlet of the second liquid storage drying tank 12 in the second heat exchanger 6, so that the gas-liquid two-phase refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 is changed into a gaseous refrigerant, that is, the refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 is located in a superheated steam zone, and the pure gaseous refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 finally returns to the compressor 1.

And a third mode: cooling and battery pack cooling modes. In this mode, as shown in fig. 7, the first stop valve 18 is opened, the second stop valve 19 is closed, the third stop valve 20 is closed, the first expansion valve 7 is closed, the second expansion valve 8 is opened, and the third expansion valve 17 is opened. As shown in fig. 7 and 8, the refrigerant entering the compressor 1 is a pure 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 an arrow 100 in fig. 8), the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 4, releases heat to the outside atmosphere in the outdoor heat exchanger 4 to lose enthalpy (shown by an arrow 400 in fig. 8), the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 4 flows into the second receiver-drier tank 12, the liquid refrigerant (shown by a point 120 in fig. 8) flows out of the second receiver-drier tank 12 and flows into the second heat exchanger 6, continues to release heat to lose enthalpy (shown by an arrow 600a in fig. 8) in the second heat exchanger 6, the liquid refrigerant flows out of the first refrigerant outlet of the second heat exchanger 6, the liquid refrigerant is divided into two streams, and the stream of the medium enthalpy pressure drops in the second expansion valve 8 and passes through a saturated liquid line (shown by an arrow 800 in fig. 8) Shown in the figure), the outlet of the second expansion valve 8 discharges a low-temperature and low-pressure gas-liquid two-phase refrigerant, which absorbs heat of the passenger compartment and obtains enthalpy (as shown by an arrow 300 in fig. 8) in the indoor evaporator 3 to reduce the temperature of the passenger compartment and realize the refrigeration of the passenger compartment; the other side of the refrigerant flow is subjected to an enthalpy pressure drop in the third expansion valve 17 and passes through a saturated liquid line (as shown by an arrow 170 in fig. 8), and a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of an outlet of the third expansion valve 17, and the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the coolant in the third heat exchanger 16 and obtains enthalpy (as shown by an arrow 160 in fig. 8), so that the low-temperature coolant flows out of a first coolant outlet of the third heat exchanger 16, and the low-temperature coolant can absorb heat of the battery pack, thereby cooling the battery pack. The gas-liquid two-phase refrigerant mixture flowing out of the outlet of the interior evaporator 3 and the gas-liquid two-phase refrigerant mixture flowing out of the refrigerant outlet of the third heat exchanger 16 converge and flow into the second heat exchanger 6, and absorb heat in the second heat exchanger 6 to obtain enthalpy (as shown by an arrow 600b in fig. 8) lost by the refrigerant flowing out of the liquid outlet of the second liquid storage drying tank 12 in the second heat exchanger 6, so that the gas-liquid two-phase refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 is changed into a gaseous refrigerant, that is, the refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 is located in a superheated steam zone, and the pure gaseous refrigerant flowing out of the second refrigerant outlet of the second heat exchanger 6 finally returns to the compressor 1.

And a fourth mode: and (4) a heat pump heating mode. In this mode, as shown in fig. 9, the first stop valve 18 is closed, the second stop valve 19 is opened, the third stop valve 20 is closed, the first expansion valve 7 is opened, the second expansion valve 8 is closed, and the third expansion valve 17 is closed. As shown in fig. 9 and 10, 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. 10), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 2, and releases heat to the passenger compartment in the interior condenser 2 to lose enthalpy (as indicated by arrow 200 in fig. 10), thereby increasing the temperature of the passenger compartment and heating the passenger compartment. The gas-liquid two-phase refrigerant mixture after heat release flowing out of the outlet of the interior condenser 2 flows into the first receiver drier 11, the liquid refrigerant (as indicated by point 110 in fig. 10) flows out of the second receiver drier 12 and flows into the first heat exchanger 5, and loses enthalpy by heat release in the first heat exchanger 5 (as indicated by arrow 500a in fig. 10), the liquid refrigerant flows out of the first refrigerant outlet of the first heat exchanger 5, the liquid refrigerant drops in enthalpy pressure in the first expansion valve 7 and passes through a saturated liquid line (as indicated by arrow 700 in fig. 10), the low-temperature and low-pressure two-phase gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 7, the low-temperature and low-pressure two-phase gas-liquid two-phase refrigerant mixture absorbs heat in the exterior heat exchanger 4 and obtains enthalpy (as indicated by arrow 400 in fig. 10), and the gas-liquid two-phase refrigerant flowing out of the outlet of the exterior heat exchanger 4 continues absorbing heat in the first heat exchanger 5, the lost enthalpy of the refrigerant flowing into the first heat exchanger 5 from the first receiver/drier 11 is obtained (as shown by an arrow 500b in fig. 10), so that the gas-liquid two-phase refrigerant flowing out of the outlet of the outdoor heat exchanger 4 is changed into a gaseous refrigerant, that is, the refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 is located in a superheated vapor region, and the gaseous refrigerant returns to the compressor 1 after passing through the second heat exchanger 6. Here, the first refrigerant inlet of the second heat exchanger 6 does not flow in the refrigerant, that is, the refrigerant does not exchange heat in the second heat exchanger 6, and the second heat exchanger 6 is used as a through flow passage.

And a fifth mode: and (4) a waste heat recovery mode. In this mode, as shown in fig. 11, the first stop valve 18 is closed, the second stop valve 19 is closed, the third stop valve 20 is opened, the first expansion valve 7 is closed, the second expansion valve 8 is closed, and the third expansion valve 17 is opened. 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 2, and releases heat to the passenger compartment in the interior condenser 2 to lose enthalpy (as indicated by an arrow 200 in fig. 12), so as to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The gas-liquid two-phase refrigerant mixture after heat release flowing out of the outlet of the interior condenser 2 flows into the first receiver drier 11, the liquid refrigerant (as indicated by a point 110 in fig. 12) flows out of the second receiver drier 12, the enthalpy pressure of the liquid refrigerant drops in the third expansion valve 17 and passes through a saturated liquid line (as indicated by an arrow 170 in fig. 12), and the outlet of the third expansion valve 17 flows out the gas-liquid two-phase refrigerant at low temperature and low pressure, and the gas-liquid two-phase refrigerant at low temperature and low pressure absorbs heat of the high-temperature coolant after absorbing heat from the electronic device in the third heat exchanger 16 and obtains enthalpy (as indicated by an arrow 160 in fig. 12), so that heat of the electronic device is recovered into the heat pump air conditioning system. The refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 is returned to the compressor 1 via the second heat exchanger 6. Here, no refrigerant flows into the first refrigerant inlet of the second heat exchanger 6, that is, the refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 does not exchange heat in the second heat exchanger 6.

Mode six: the heat pump includes a waste heat recovery mode. In this mode, as shown in fig. 13, the first stop valve 18 is closed, the second stop valve 19 is opened, the third stop valve 20 is opened, the first expansion valve 7 is opened, the second expansion valve 8 is closed, and the third expansion valve 17 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 the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant (as indicated by an arrow 100 in fig. 14), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 2, and releases heat to the passenger compartment in the interior condenser 2 to lose enthalpy (as indicated by an arrow 200 in fig. 14), so as to increase the temperature of the passenger compartment and achieve heating of the passenger compartment. The gas-liquid two-phase refrigerant mixture after heat release flowing out of the outlet of the interior condenser 2 flows into the first liquid storage drying tank 11, the liquid refrigerant (as shown by a point 110 in fig. 14) flows out of the liquid outlet of the first liquid storage drying tank 11, the liquid refrigerant is divided into two streams, one stream is subjected to equal enthalpy pressure drop in the third expansion valve 17 and passes through a saturated liquid line (as shown by an arrow 170 in fig. 14), the gas-liquid two-phase refrigerant at low temperature and low pressure flows out of the outlet of the third expansion valve 17, and the gas-liquid two-phase refrigerant at low temperature and low pressure absorbs heat of high-temperature cooling liquid after heat absorption from an electronic device in the third heat exchanger 16 and obtains enthalpy (as shown by an arrow 160 in fig. 14), so that the heat of the electronic device is recovered into the heat pump air conditioning system; the other flow of the refrigerant flows into the first heat exchanger 5, releases heat and loses enthalpy in the first heat exchanger 5 (as indicated by an arrow 500a in fig. 14), a liquid refrigerant flows out of the first refrigerant outlet of the first heat exchanger 5, the liquid refrigerant is subjected to an enthalpy pressure drop in the first expansion valve 7 and passes through a saturated liquid line (as indicated by an arrow 700 in fig. 14), a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out of the outlet of the first expansion valve 7, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat of the outside atmosphere in the outdoor heat exchanger 4 and obtains enthalpy (as indicated by an arrow 400 in fig. 14), and the gas-liquid two-phase refrigerant flowing out of the outlet of the outdoor heat exchanger 4 continues to absorb heat in the first heat exchanger 5, and obtains enthalpy lost by the refrigerant flowing from the first liquid storage drying tank 11 into the first heat exchanger 5 (as indicated by an arrow 500b in fig. 14). The refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 and the refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 merge together and then return to the compressor 1 through the second heat exchanger 6. Here, no refrigerant flows into the first refrigerant inlet of the second heat exchanger 6, that is, the refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 and the refrigerant flowing out of the refrigerant outlet of the third heat exchanger 16 do not exchange heat in the second heat exchanger 6.

Mode seven: a first dehumidification mode. In this mode, as shown in fig. 15, the first stop valve 18 is closed, the second stop valve 19 is opened, the third stop valve 20 is opened, the first expansion valve 7 is opened, the second expansion valve 8 is opened, and the third expansion valve 17 is closed. As shown in fig. 15 and 16, the refrigerant entering the compressor 1 is a gaseous refrigerant, and the compressor 1 compresses the gaseous refrigerant such that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 16), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 2, releases heat to the passenger compartment in the interior condenser 2, and loses enthalpy (indicated by an arrow 200 in fig. 16). The gas-liquid two-phase refrigerant mixture after heat release flowing out of the outlet of the interior condenser 2 flows into the first receiver drier 11, the first receiver drier 11 flows out a liquid refrigerant (as shown by a point 110 in fig. 16), the liquid refrigerant is divided into two streams, one stream drops in enthalpy pressure in the second expansion valve 8 and passes through a saturated liquid line (as shown by an arrow 800 in fig. 16), the outlet of the second expansion valve 8 flows out a gas-liquid two-phase refrigerant with low temperature and low pressure, the gas-liquid two-phase refrigerant with low temperature and low pressure absorbs heat of the passenger compartment in the interior evaporator 3 and obtains enthalpy (as shown by an arrow 300 in fig. 16), humid air with higher temperature in the passenger compartment meets the indoor evaporator 3 with lower temperature, and droplets in the humid air are condensed on the surface of the indoor evaporator 3 to form condensed water, so as to achieve dehumidification of the passenger compartment; the other flow from the liquid outlet of the first liquid storage drying tank 11 flows into the first heat exchanger 5, releases heat in the first heat exchanger 5 to lose enthalpy (as shown by an arrow 500a in fig. 16), the first refrigerant outlet of the first heat exchanger 5 flows out liquid refrigerant, the liquid refrigerant is reduced in enthalpy pressure in the first expansion valve 7 and passes through a saturated liquid line (as indicated by an arrow 700 in fig. 16), a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant flows out of an outlet of the first expansion valve 7, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat of the outside air in the outdoor heat exchanger 4 to obtain enthalpy (as indicated by an arrow 400 in fig. 16), and the gas-liquid two-phase refrigerant flowing out of the outlet of the outdoor heat exchanger 4 continues to absorb heat in the first heat exchanger 5 to obtain enthalpy lost by the refrigerant flowing into the first heat exchanger 5 from the first receiver/drier tank 11 (as indicated by an arrow 500b in fig. 16). The refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 and the refrigerant flowing out of the refrigerant outlet of the interior evaporator 3 merge together and then return to the compressor 1 through the second heat exchanger 6. Here, the first refrigerant inlet of the second heat exchanger 6 does not have the refrigerant flowing therein, that is, the refrigerant flowing out of the second refrigerant outlet of the first heat exchanger 5 and the refrigerant flowing out of the outlet of the interior evaporator 3 do not exchange heat in the second heat exchanger 6.

And a mode eight: and a second dehumidification mode. In this mode, as shown in fig. 17, the first stop valve 18 is closed, the second stop valve 19 is closed, the third stop valve 20 is opened, the first expansion valve 7 is closed, the second expansion valve 8 is closed, and the third expansion valve 17 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 a high-temperature and high-pressure gaseous refrigerant (indicated by an arrow 100 in fig. 18), and the high-temperature and high-pressure gaseous refrigerant flows into the interior condenser 2, releases heat to the passenger compartment in the interior condenser 2, and loses enthalpy (indicated by an arrow 200 in fig. 18). The gas-liquid two-phase refrigerant mixture after heat release flowing out of the outlet of the indoor condenser 2 flows into the first liquid storage drying tank 11, a liquid refrigerant (as shown by a point 110 in fig. 18) flows out of the liquid outlet of the first liquid storage drying tank 11, the liquid refrigerant is subjected to equal enthalpy pressure drop in the second expansion valve 8 and passes through a saturated liquid line (as shown by an arrow 800 in fig. 18), a low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the second expansion valve 8, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor evaporator 3 and obtains enthalpy (as shown by an arrow 300 in fig. 18), humid air with higher temperature in the passenger compartment meets the indoor evaporator 3 with lower temperature, and small droplets in the humid air are condensed on the surface of the indoor evaporator 3 to form condensed water, so that dehumidification of the passenger compartment is achieved. The refrigerant flowing out of the outlet of the interior evaporator 3 returns to the compressor 1 through the second heat exchanger 6. Here, no refrigerant flows into the first refrigerant inlet of the second heat exchanger 6, that is, the refrigerant flowing out of the outlet of the interior evaporator 3 does not exchange heat in the second heat exchanger 6.

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

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

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

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

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

Claims

1. A heat pump air conditioning system is characterized by comprising a compressor (1), an indoor condenser (2), an indoor evaporator (3), an outdoor heat exchanger (4), a first heat exchanger (5), a second heat exchanger (6), a first expansion valve (7), a second expansion valve (8), a first flow path (9) which is selectively communicated or cut off, and a second flow path (10) which is selectively communicated or cut off,

the outlet of the compressor (1) is connected with the inlet of the indoor condenser (2) and is connected with the inlet of the outdoor heat exchanger (4) through the first flow path (9), the outlet of the indoor condenser (2) is connected with the first refrigerant inlet of the first heat exchanger (5), the first refrigerant outlet of the first heat exchanger (5) is connected with the inlet of the outdoor heat exchanger (4) through the first expansion valve (7), the outlet of the outdoor heat exchanger (4) is connected with the first refrigerant inlet of the second heat exchanger (6) and is connected with the second refrigerant inlet of the first heat exchanger (5) through the second flow path (10), the first refrigerant outlet of the second heat exchanger (6) is connected with the inlet of the indoor evaporator (3) through the second expansion valve (8), the outlet of the indoor evaporator (3) and the second refrigerant outlet of the first heat exchanger (5) are connected with the second heat exchange outlet And a second refrigerant inlet of the device (6) is connected, and a second refrigerant outlet of the second heat exchanger (6) is connected with an inlet of the compressor (1).

2. The heat pump air-conditioning system according to claim 1, further comprising a first liquid storage drying tank (11) and a second liquid storage drying tank (12), wherein an outlet of the indoor condenser (2) is connected to an inlet of the first liquid storage drying tank (11), a liquid outlet of the first liquid storage drying tank (11) is connected to a first refrigerant inlet of the first heat exchanger (5), an outlet of the outdoor heat exchanger (4) is connected to an inlet of the second liquid storage drying tank (12), and a liquid outlet of the second liquid storage drying tank (12) is connected to a first refrigerant inlet of the second heat exchanger (6).

3. The heat pump air conditioning system according to claim 2, further comprising a subcooler (13) downstream of the second receiver-drier tank (12), wherein the liquid outlet of the second receiver-drier tank (12) is connected to the first refrigerant inlet of the second heat exchanger (6) via the subcooler (13).

4. A heat pump air conditioning system according to claim 2 or 3, characterized in that the heat pump air conditioning system further comprises a third flow path (14) that is selectively opened or closed, and the liquid outlet of the first reservoir tank (11) is further connected to the inlet of the second expansion valve (8) via the third flow path (14).

5. The heat pump air-conditioning system according to claim 4, further comprising a third heat exchanger (16) and a third expansion valve (17), wherein the first refrigerant outlet of the second heat exchanger (6) is further connected to the refrigerant inlet of the third heat exchanger (16) via the third expansion valve (17), the refrigerant outlet of the third heat exchanger (16) is connected to the second refrigerant inlet of the second heat exchanger (6), the first coolant outlet of the third heat exchanger (16) is used for connecting to the inlet of the battery pack of the vehicle, and the first coolant inlet of the third heat exchanger (16) is used for connecting to the outlet of the battery pack.

6. The heat pump air conditioning system according to claim 5, wherein the liquid outlet of the first receiver-drier tank (11) is further connected via the third flow path (14) to an inlet of the third expansion valve (17), a second coolant outlet of the third heat exchanger (16) being adapted to be connected to an inlet of an electronic device of a vehicle, and a second coolant inlet of the third heat exchanger (16) being adapted to be connected to an outlet of the electronic device.

7. The heat pump air conditioning system according to claim 6, further comprising a check valve (15), wherein the first refrigerant outlet of the second heat exchanger (6) is connected to an inlet of the second expansion valve (8) and an inlet of the third expansion valve (17) via the check valve (15).

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

9. The heat pump air conditioning system according to claim 4, wherein a first shut-off valve (18) is provided in the first flow path (9), a second shut-off valve (19) is provided in the second flow path (10), and a third shut-off valve (20) is provided in the third flow path (14).

10. A vehicle comprising a heat pump air conditioning system according to any one of claims 1 to 9.