CN107351695B

CN107351695B - Automobile thermal management system and electric automobile

Info

Publication number: CN107351695B
Application number: CN201610305553.7A
Authority: CN
Inventors: 汪孟瑛; 叶梅娇; 陈雪峰; 黄健
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2016-05-10
Filing date: 2016-05-10
Publication date: 2020-03-31
Anticipated expiration: 2036-05-10
Also published as: CN107351695A

Abstract

The invention discloses an automobile thermal management system and an electric automobile. The automobile heat management system comprises a heat pump air-conditioning system, a battery pack heat exchange system, an engine cooling system, a first plate heat exchanger and a first switch valve, wherein the heat pump air-conditioning system and the engine cooling system exchange heat with the battery pack heat exchange system through the first plate heat exchanger respectively, a refrigerant inlet of the first plate heat exchanger is communicated with an outlet of an outdoor heat exchanger through a switched-on or switched-off battery cooling branch or is communicated with a first end of a first branch and a first end of a second branch and is communicated with an inlet of the first switch valve through a switched-on or switched-off battery heating branch, a refrigerant outlet of the first plate heat exchanger is communicated with an inlet of a compressor through a switched-on or switched-off battery cooling backflow branch and is communicated with an outlet of the first switch valve through a battery heating backflow branch. Therefore, the cooling and heating in the vehicle are realized, and the battery is cooled and heated to work in a proper temperature range.

Description

Automobile thermal management system and electric automobile

Technical Field

The invention relates to the field of air conditioners of electric automobiles, in particular to an automobile thermal management system and an electric automobile comprising the same.

Background

To ensure that the battery of the electric automobile has high charging and discharging efficiency, proper working temperature is needed, and the performance and the cruising ability of the electric automobile are greatly influenced by overhigh or overhigh temperature. Chinese patent publication No. CN205039220U discloses a cooling system for power battery of automobile. Although this power battery cooling system can cool off power battery through the evaporimeter when refrigeration, but power battery hugs closely with the evaporimeter and carries out the heat transfer together, though feasible in principle, nevertheless is difficult to realize on the car, because the evaporimeter generally all is in air-conditioning box, and the box space is limited, and pure electric vehicles's power battery is very big, generally arranges the vehicle bottom in.

Disclosure of Invention

The invention aims to provide an automobile thermal management system and an electric automobile, and aims to solve the problems.

In order to achieve the above object, according to a first aspect of the present invention, there is provided an automotive thermal management system, which includes a heat pump air conditioning system, a battery pack heat exchange system, an engine cooling system, a first plate heat exchanger and a first switching valve, wherein the heat pump air conditioning system and the engine cooling system exchange heat with the battery pack heat exchange system through the first plate heat exchanger, respectively, the heat pump air conditioning system includes an indoor condenser, an indoor evaporator, a compressor and an outdoor heat exchanger, an outlet of the compressor is communicated with an inlet of the indoor condenser, an outlet of the indoor condenser is communicated with an inlet of the first switching valve, an outlet of the first switching valve is selectively communicated with an inlet of the outdoor heat exchanger through a first throttling branch or a first through-flow branch, and an outlet of the outdoor heat exchanger is selectively communicated with an inlet of the selectively communicated or blocked first branch through a second throttling branch or a second through-flow branch The first end of the first branch is communicated with the first end of the second branch which is selectively switched on or off, the second end of the first branch is communicated with the inlet of the compressor, the second end of the second branch is communicated with the inlet of the indoor evaporator, the outlet of the indoor evaporator is communicated with the inlet of the compressor, the refrigerant inlet of the first plate heat exchanger is communicated with the outlet of the outdoor heat exchanger through a battery cooling branch which is selectively switched on or off, or with the first end of the first branch and the first end of the second branch, and with the inlet of the first switch valve via a selectively turned on or off battery heating branch, the refrigerant outlet of the first plate heat exchanger is communicated with the inlet of the compressor through a battery cooling return branch which is selectively switched on or switched off, and is communicated with the outlet of the first switch valve through a battery heating return branch.

Optionally, a second switch valve is arranged on the first branch.

Optionally, a third on-off valve is arranged on the second branch.

Optionally, the heat pump air conditioning system further comprises: a first three-way valve, an outlet of the outdoor heat exchanger selectively communicating with an inlet of the first three-way valve via a second throttling branch or a second flow branch, a first outlet of the first three-way valve communicating with a first end of the first branch, a second outlet of the first three-way valve communicating with a first end of the second branch.

Optionally, a fourth switch valve is disposed on the battery heating branch.

Optionally, a fifth switch valve is disposed on the battery cooling return branch.

Optionally, a first check valve is further disposed on the battery cooling return branch.

Optionally, a second check valve is disposed on the battery heating reflux branch.

Optionally, the refrigerant inlet of the first plate heat exchanger is communicated with the outlet of the outdoor heat exchanger via a selectively opened or closed battery cooling branch, and a first expansion valve is disposed on the battery cooling branch.

Optionally, a refrigerant inlet of the first plate heat exchanger is communicated with the first end of the first branch and the first end of the second branch via a selectively opened or closed battery cooling branch, and a flow valve is arranged on the battery cooling branch.

Optionally, the outlet of the indoor evaporator communicates with the inlet of the compressor via a third one-way valve.

Optionally, the first plate heat exchanger is connected in series in a coolant loop of the battery pack heat exchange system, and a first water pump, an auxiliary water tank and a battery pack which are connected in series with the first plate heat exchanger are further arranged in the coolant loop.

Optionally, the engine cooling system includes a second water pump, an engine, an indoor warm air core and a second three-way valve, an outlet of the second water pump is communicated with an inlet of the second three-way valve, a first outlet and a second outlet of the second three-way valve are respectively communicated with an engine coolant inlet of the first plate heat exchanger and an inlet of the indoor warm air core, an engine coolant outlet of the first plate heat exchanger and an outlet of the indoor warm air core are both communicated with a coolant inlet of the engine, and a coolant outlet of the engine is communicated with an inlet of the second water pump.

Optionally, a sixth switching valve is disposed on the first through-flow branch, and a second expansion valve is disposed on the first throttle branch.

Optionally, the heat pump air conditioning system further includes a first expansion switch valve, an inlet of the first expansion switch valve is communicated with an outlet of the indoor condenser, an outlet of the first expansion switch valve is communicated with an inlet of the outdoor heat exchanger, the first throttling branch is a throttling flow passage of the first expansion switch valve, and the first through-flow branch is a through-flow passage of the first expansion switch valve.

Optionally, a seventh switching valve is disposed on the second bypass, and a third expansion valve is disposed on the second throttle.

Optionally, the automobile thermal management system is applied to an electric automobile, and further comprises a motor cooling system; the heat pump air conditioning system further includes: a second plate heat exchanger, wherein the second plate heat exchanger is arranged in the second bypass branch and the second plate heat exchanger is simultaneously arranged in the motor cooling system.

Optionally, the refrigerant inlet of the second plate heat exchanger is communicated with the outlet of the outdoor heat exchanger, and the refrigerant outlet of the second plate heat exchanger is communicated with the inlet of the seventh switching valve.

Optionally, the motor cooling system comprises a motor, a motor radiator and a third water pump connected in series with the second plate heat exchanger to form a loop.

Optionally, the heat pump air conditioning system further includes a second expansion switch valve, an inlet of the second expansion switch valve is communicated with an outlet of the outdoor heat exchanger, an outlet of the second expansion switch valve is communicated with the first end of the first branch and is communicated with the first end of the second branch, the second throttling branch is a throttling flow passage of the second expansion switch valve, and the second through-flow branch is a through-flow passage of the second expansion switch valve.

Optionally, the automobile thermal management system is applied to an electric automobile, and further comprises a motor cooling system; the heat pump air conditioning system further includes: a second plate heat exchanger, wherein a refrigerant inlet of the second plate heat exchanger is communicated with an outlet of the second expansion switch valve, a refrigerant outlet of the second plate heat exchanger is communicated with the first end of the first branch and the first end of the second branch, and the second plate heat exchanger is simultaneously arranged in the motor cooling system.

Optionally, the motor cooling system includes a motor coolant main line, a first motor coolant branch line, and a second motor coolant branch line, a first end of the motor coolant main line is selectively communicated with a first end of the first motor coolant branch line or a first end of the second motor coolant branch line, a second end of the first motor coolant branch line and a second end of the second motor coolant branch line are communicated with a second end of the motor coolant main line, wherein a motor, a motor radiator, and a third water pump are connected in series to the motor coolant main line, and the second plate heat exchanger is connected in series to the first motor coolant branch line.

Optionally, the heat pump air conditioning system further includes a gas-liquid separator, an outlet of the gas-liquid separator is communicated with an inlet of the compressor, an inlet of the gas-liquid separator is communicated with an outlet of the indoor evaporator, the second end of the first branch is communicated with an inlet of the gas-liquid separator, and a refrigerant outlet of the first plate heat exchanger is communicated with an inlet of the gas-liquid separator via the battery cooling return branch.

Optionally, the heat pump air conditioning system further includes a PTC heater for heating the wind flowing through the indoor condenser.

Optionally, the PTC heater is disposed on a windward side or a leeward side of the indoor condenser.

According to a second aspect of the invention, an electric vehicle is provided, which comprises the vehicle thermal management system provided according to the first aspect of the invention.

The automobile heat management system provided by the invention can realize the requirements of cooling in summer and heating in winter in the automobile by utilizing the heat pump air conditioning system, and also has the functions of cooling the battery and heating the battery. Through first plate heat exchanger, can carry out the heat exchange through heat pump air conditioning system's refrigerant and battery package coolant liquid, cool down or heat the battery, the coolant liquid of accessible engine carries out the heat exchange with battery package coolant liquid again, heats the battery, utilizes the heat exchange between the three kinds of media, and the effective utilization to the energy under the adaptable different vehicle conditions makes the battery work in suitable temperature range all the time to improve the charge-discharge efficiency, the duration and the life of battery. In addition, the invention can realize the refrigeration and heating of the automobile air conditioning system under the condition of not changing the circulation direction of the refrigerant, has simple structure, ensures that the pipeline arrangement of the whole system is simple, and is easy for batch production.

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

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:

FIG. 1A is a schematic diagram of a heat pump air conditioning system according to one embodiment of the present invention;

FIG. 1B is a schematic diagram of a heat pump air conditioning system according to another embodiment of the present invention;

fig. 2 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;

fig. 3 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;

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

FIG. 5A is a schematic diagram of a heat pump air conditioning system according to another embodiment of the present invention;

FIG. 5B is a schematic diagram of a heat pump air conditioning system according to another embodiment of the present invention;

fig. 6 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;

FIG. 7 is a schematic structural diagram of an automotive thermal management system according to one embodiment of the present invention;

FIG. 8 is a schematic structural diagram of an automotive thermal management system in accordance with another embodiment of the present invention;

FIG. 9 is a schematic diagram of a top view of an expansion switch valve provided in accordance with a preferred embodiment of the present invention;

FIG. 10 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, wherein both the first and second ports are in an open state;

fig. 11 is a front structural view in one perspective of an expansion switching valve provided in a preferred embodiment of the present invention;

FIG. 12 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, with the first port in an open state and the second port in a closed state;

FIG. 13 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, with the first port in a closed position and the second port in an open position;

fig. 14 is a front view schematically illustrating the construction of the expansion switching valve according to another view in accordance with the preferred embodiment of the present invention;

FIG. 15 is a schematic cross-sectional view taken along line AC-AC of FIG. 14, wherein the first port is in an open state and the second port is in a closed state;

fig. 16 is a first internal structural view of the expansion switching valve according to the preferred embodiment of the present invention, in which the first port and the second port are both in an open state;

fig. 17 is a partially enlarged view of a portion a in fig. 16;

fig. 18 is a second internal structural view of the expansion switching valve according to the preferred embodiment of the present invention, wherein the first port is in an open state and the second port is in a closed state;

fig. 19 is a third internal structural view of the expansion switch valve according to the preferred embodiment of the present invention, wherein the first valve port is in a closed state and the second valve port is in an open state.

Detailed Description

The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present invention, are given by way of illustration and explanation only, not limitation.

In the present invention, the electric vehicle mainly refers to a hybrid vehicle.

In the present invention, unless otherwise specified, terms of orientation such as "upper, lower, left, and right" are generally used with respect to the direction of the drawing of the drawings, "upstream, and downstream" are used with respect to the medium, e.g., the flow direction of the refrigerant, specifically, the downstream direction is toward the flow direction of the refrigerant, and the upstream direction is away from the flow direction of the refrigerant, "inner and outer" refer to the inner and outer of the contour of the corresponding component.

Fig. 1A and 1B are schematic structural views of a heat pump air conditioning system according to an embodiment of the present invention. As shown in fig. 1A, the system may include: an HVAC (Heating Ventilation and air conditioning) assembly 600, a compressor 604, and an outdoor heat exchanger 605. The HVAC assembly 600 may include, among other things, an indoor condenser 601 and an indoor evaporator 602. Further, as shown in fig. 1A, an outlet of the compressor 604 communicates with an inlet of the indoor condenser 601, an outlet of the indoor condenser 601 selectively communicates with an inlet of the outdoor heat exchanger 605 via a first throttling branch or a first through-flow branch, an outlet of the outdoor heat exchanger 605 selectively communicates with a first end of a first branch 641 selectively turned on or off and communicates with a first end of a second branch 642 selectively turned on or off via a second throttling branch or a second through-flow branch, a second end of the first branch 641 communicates with an inlet of the compressor 604, a second end of the second branch 642 communicates with an inlet of the indoor evaporator 602, and an outlet of the indoor evaporator 602 communicates with an inlet of the compressor 604.

In the present invention, the first branch 641 and the second branch 642 can be selectively turned on or off according to actual requirements. For example, as shown in fig. 1A, a second on-off valve 643 is provided in the first branch 641, and when the second on-off valve 643 is opened, the first branch 641 is turned on, and when the second on-off valve 643 is closed, the first branch 641 is turned off. The second branch 642 is provided with a third switching valve 644, and when the third switching valve 644 is opened, the second branch 642 is opened, and when the third switching valve 644 is closed, the second branch 642 is closed.

In another embodiment, as shown in fig. 1B, the heat pump air conditioning system may further include: the first three-way valve 645, an outlet of the outdoor heat exchanger 605 is selectively communicated with an inlet 645a of the first three-way valve 645 through a second throttling bypass or a second bypass, a first outlet 645b of the first three-way valve 645 is communicated with a first end of the first branch 641, and a second outlet 645c of the first three-way valve 645 is communicated with a first end of the second bypass 642. Thus, the first branch 641 may be controlled to be turned on or off, and the second branch 642 may be controlled to be turned on or off by the first three-way valve 645.

For example, the first branch 641 may be controlled to be turned on and the second branch 642 may be controlled to be turned off by controlling the inlet 645a to the first outlet 645b of the first three-way valve 645 to be turned on and the inlet 645a to the second outlet 645c to be turned off; and, by controlling the inlet 645a to the first outlet 645b of the first three-way valve 645 to be not conducted and the inlet 645a to the second outlet 645c to be conducted, the first branch 641 may be controlled to be turned off and the second branch 642 may be controlled to be turned on.

Further, in order to prevent the refrigerant from flowing back into the indoor evaporator 602 when the first branch 641 is turned on, optionally, as shown in fig. 1A and 1B, the outlet of the indoor evaporator 602 communicates with the inlet of the compressor 604 via the third check valve 627. Thus, the refrigerant can only be allowed to flow from the indoor evaporator 602 to the compressor 604, but not in the opposite direction.

In the present invention, the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via either the first throttling branch or the first circulating branch. This communication may be accomplished in a number of ways. For example, in one embodiment, as shown in fig. 1A and 1B, the heat pump air conditioning system may further include a first expansion switch valve 603, an inlet of the first expansion switch valve 603 is communicated with an outlet of the indoor condenser 601, an outlet of the first expansion switch valve 603 is communicated with an inlet of the outdoor heat exchanger 605, wherein the first throttling branch is a throttling flow passage of the first expansion switch valve 603, and the first through-flow branch is a through-flow passage of the first expansion switch valve 603.

In the present invention, the expansion on-off valve is a valve having both an expansion valve function (also referred to as an electronic expansion valve function) and an on-off valve function (also referred to as a solenoid valve function), and may be regarded as an integration of the on-off valve and the expansion valve. A through flow channel and a throttling flow channel are formed in the expansion switch valve, when the expansion switch valve is used as the switch valve, the through flow channel in the expansion switch valve is conducted, and a through flow branch is formed at the moment; when the expansion switch valve is used as an expansion valve, the throttling flow passage in the expansion switch valve is communicated, and a throttling branch is formed at the moment.

As another alternative embodiment, as shown in fig. 2, the heat pump air conditioning system may further include a sixth on-off valve 608 and a second expansion valve 607, wherein the sixth on-off valve 608 is disposed on the first through-flow branch, and the second expansion valve 607 is disposed on the first throttle branch. Specifically, as shown in fig. 2, an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a sixth switching valve 608 to form a first through-flow branch, and an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a second expansion valve 607 to form a first throttle branch. When the system is in the high-temperature cooling mode, the sixth switching valve 608 is turned on, the second expansion valve 607 is closed, and the outlet of the indoor condenser 601 is communicated with the inlet of the outdoor heat exchanger 605 via the first through-flow branch. When the system is in the low temperature heating mode, the second expansion valve 607 is turned on, the sixth switching valve 608 is closed, and the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via the first throttling branch.

Similar to the implementation manner of the first flow branch and the first throttling branch, as one implementation manner of the second flow branch and the second throttling branch, as shown in fig. 1A and 1B, the heat pump air conditioning system may further include a second expansion switch valve 606, an inlet of the second expansion switch valve 606 is communicated with an outlet of the outdoor heat exchanger 605, an outlet of the second expansion switch valve 606 is communicated with a first end of the first branch 641 which is selectively turned on or off and is communicated with a first end of the second branch 642 which is selectively turned on or off, wherein the second flow branch is a throttling flow passage of the second expansion switch valve 606, and the second flow branch is a flow passage of the second expansion switch valve 606.

As another alternative embodiment, as shown in fig. 3, the heat pump air conditioning system may further include a seventh switching valve 610 and a third expansion valve 609, wherein the seventh switching valve 610 is disposed on the second branch, and the third expansion valve 609 is disposed on the second branch. Specifically, as shown in fig. 3, the outlet of the outdoor heat exchanger 605 communicates with the first end of the selectively turned-on or turned-off first branch 641 and communicates with the first end of the selectively turned-on or turned-off second branch 642 via the seventh switching valve 610 to form a second through branch, and the outlet of the outdoor heat exchanger 605 communicates with the first end of the selectively turned-on or turned-off first branch 641 and communicates with the first end of the selectively turned-on or turned-off second branch 642 via the third expansion valve 609 to form a second throttling branch. When the system is in the high-temperature cooling mode, the third expansion valve 609 is turned on, and the seventh switching valve 610 is closed. When the system is in the low temperature heating mode, the seventh switching valve 610 is turned on and the third expansion valve 609 is closed.

In order to facilitate piping and save space, it is preferable that the first expansion switch valve 603 and the second expansion switch valve 606 are used in the heat pump air conditioning system provided in the present invention, that is, the embodiment shown in fig. 1A and 1B.

Fig. 4 shows a schematic configuration diagram of a heat pump air conditioning system according to another embodiment of the present invention. As shown in fig. 4, the heat pump air conditioning system may further include a gas-liquid separator 611, wherein an outlet of the indoor evaporator 602 communicates with an inlet of the gas-liquid separator 611, a second end of the first branch 641 communicates with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 communicates with an inlet of the compressor 604. In this way, the refrigerant flowing out through the indoor evaporator 602 or the second end of the first branch 641 may first pass through the gas-liquid separator 611 to undergo gas-liquid separation, and the separated gas may flow back to the compressor 604, so as to prevent the liquid refrigerant from entering the compressor 604 and damaging the compressor 604, thereby prolonging the service life of the compressor 604 and improving the efficiency of the entire heat pump air conditioning system.

In the heat pump low-temperature heating mode, in order to improve the heating capacity, it is preferable that, as shown in fig. 5A and 5B, a second plate heat exchanger 612 is provided in the entire heat pump air conditioning system, and the second plate heat exchanger 612 is also provided in the motor cooling system of the electric vehicle. In this way, the residual heat of the motor cooling system can be used to heat the air conditioning system refrigerant, thereby increasing the suction temperature and suction capacity of the compressor 604.

For example, as shown in fig. 5A, in an embodiment where the heat pump air conditioning system employs the third expansion valve 609 and the seventh switching valve 610, the second plate heat exchanger 612 may be disposed in the second pass branch as shown in fig. 5A. For example, in one embodiment, the refrigerant inlet 612a of the second plate heat exchanger 612 communicates with the outlet of the outdoor heat exchanger 605, and the refrigerant outlet 612b of the second plate heat exchanger 612 communicates with the inlet of the seventh switching valve 610. Alternatively, in another embodiment (not shown), the refrigerant inlet 612a of the second plate heat exchanger 612 may also be in communication with the outlet of the seventh switching valve 610, and the refrigerant outlet 612b of the second plate heat exchanger 612 is in communication with the inlet of the indoor evaporator 602.

At the same time, the second plate heat exchanger 612 is simultaneously arranged in the motor cooling system. As shown in fig. 5A, the motor cooling system may include a motor in series with the second plate heat exchanger 612 to form a loop, a motor radiator 613, and a third water pump 614. In this way, the refrigerant is able to exchange heat with the coolant in the motor cooling system via the second plate heat exchanger 612. The refrigerant passes through the seventh switching valve 610 and the second switching valve 643 and is returned to the compressor 604.

Alternatively, as shown in fig. 5B, in an embodiment where the heat pump air conditioning system employs the second expansion switching valve 606, the refrigerant inlet 612a of the second plate heat exchanger 612 communicates with the outlet of the second expansion switching valve 606, the refrigerant outlet 612B of the second plate heat exchanger 612 communicates with the first end of the first branch 641 and with the first end of the second branch 642, and the second plate heat exchanger 612 is simultaneously provided in the motor cooling system of the electric vehicle. In this way, the refrigerant is able to exchange heat with the coolant in the motor cooling system via the second plate heat exchanger 612. The refrigerant passes through the second on-off valve 643 and then returns to the compressor 604.

The second plate heat exchanger 612 can improve the heating capacity of the air conditioning system in the low-temperature heating mode of the heat pump.

However, in the embodiment of the heat pump air conditioning system shown in fig. 5B, in which the second expansion switching valve 606 is used, in order to avoid heating of the refrigerant in the heat pump high temperature cooling mode, a valve may be used to control whether heat exchange is performed in the second plate heat exchanger 612. Specifically, the electric machine cooling system may include an electric machine coolant trunk 616, a first electric machine coolant branch 617, and a second electric machine coolant branch 618, wherein a first end of the electric machine coolant trunk 616 is selectively in communication with a first end of the first electric machine coolant branch 617 or a first end of the second electric machine coolant branch 618. For example, in one embodiment, a first end of the motor coolant trunk 616 may be in communication with an inlet 615a of a third three-way valve 615, a first end of the first motor coolant branch 617 may be in communication with a first outlet 615b of the third three-way valve 615, and a first end of the second motor coolant branch 618 may be in communication with a second outlet 615c of the third three-way valve 615, whereby the first end of the motor coolant trunk 616 may be controlled to selectively communicate with either the first end of the first motor coolant branch 617 or the first end of the second motor coolant branch 618 by the third three-way valve 615. As shown in fig. 5B, a second end of the first motor coolant branch 617 communicates with a second end of the motor coolant main passage 616, and a second end of the second motor coolant branch 618 also communicates with a second end of the motor coolant main passage 616, wherein the motor, the motor radiator 613, and the third water pump 614 are connected in series to the motor coolant main passage 616, and the second plate heat exchanger 612 is connected in series to the first motor coolant branch 617.

As described above, when the air conditioning system operates in the heat pump low-temperature heating mode, the refrigerant needs to be heated in the second plate heat exchanger 612 in order to improve heating performance. In this case, therefore, the first motor coolant branch 617 can be rendered conductive by controlling the third three-way valve 615, whereby the coolant in the motor cooling system flows through the second plate heat exchanger 612, at which point heat exchange with the refrigerant can be achieved. However, when the system is operating in the heat pump high temperature cooling mode, there is no need to heat the refrigerant in the second plate heat exchanger 612. In this case, therefore, the second motor coolant branch 618 can be rendered conductive by controlling the third three-way valve 615, whereby the coolant in the motor cooling system does not flow through the second plate heat exchanger 612, and the second plate heat exchanger 612 only flows through as a flow path for the refrigerant.

In the heat pump air conditioning system provided by the present invention, various refrigerants such as R134a, R410a, R32, R290 and the like can be used, and a medium-high temperature refrigerant is preferably used.

Fig. 6 is a schematic configuration diagram of a heat pump air conditioning system according to another embodiment of the present invention. As shown in fig. 6, the HVAC assembly 600 may further include a PTC heater 619, the PTC heater 619 being used to heat the wind flowing through the indoor condenser 601.

In the present invention, the PTC heater 619 may be a high voltage PTC (driven by the vehicle high voltage battery), with a voltage range: 200V-900V. Alternatively, the PTC heater 619 may be a low voltage PTC (12V or 24V battery operated), voltage range: 9V-32V. In addition, the PTC heater 619 may be a complete core composed of several PTC ceramic wafer modules and heat dissipation fins, or a strip-shaped or block-shaped PTC ceramic wafer module with heat dissipation fins.

In the present invention, the PTC heater 619 may be disposed on the windward side or the leeward side of the indoor condenser 601. Also, in order to improve the heating effect of the wind flowing through the indoor condenser 601, the PTC heater 619 may be provided in parallel with the indoor condenser 601. In other embodiments, the PTC heater 619 may also be disposed at the foot blowing air port and the defrost air port of the box of the HVAC assembly 600, or at the air ports of the defrost air duct.

If the PTC heater 619 is arranged on the windward side or the leeward side of the indoor condenser 601 in the box body and is arranged in parallel with the indoor condenser 601, a groove can be dug in the shell of the box body, the PTC heater 619 is vertically inserted into the box body, a bracket can be welded on the side plate of the indoor condenser 601, and the PTC heater 619 is fixed on the bracket of the indoor condenser 601 through a screw. If the PTC heater 619 is arranged at the foot blowing air port and the defrosting air port of the box body or at the air port of the defrosting air channel, the PTC heater can be directly fixed at the air ports of the air outlet and the air channel port of the box body through screws.

Through the embodiment, when the temperature outside the vehicle is too low, and the heating quantity of the low-temperature heating of the heat pump does not meet the requirement in the vehicle, the PTC heater 619 can be operated to assist in heating, so that the defects that the heating quantity is small when the low-temperature heating of the heat pump air conditioning system is carried out, the defrosting and demisting of the whole vehicle are slow, the heating effect is poor and the like can be eliminated.

FIG. 7 is a schematic structural diagram of an automotive thermal management system in accordance with an embodiment of the invention. As shown in fig. 7, the system may include the heat pump air conditioning system, the battery pack heat exchange system, the engine cooling system and the first plate heat exchanger 620 described above, wherein the heat pump air conditioning system and the engine cooling system exchange heat with the battery pack heat exchange system through the first plate heat exchanger 620, respectively. In the present invention, the first plate heat exchanger 620 is a three-plate heat exchanger. The three-layer plate heat exchanger is a plate heat exchanger with three heat exchange channels formed inside, wherein a refrigerant of a heat pump air conditioning system flows in one heat exchange channel, battery cooling liquid flows in one heat exchange channel, and engine cooling liquid flows in the other heat exchange channel. As shown in fig. 7, the thermal management system of the automobile further includes a first switching valve 635, wherein an outlet of the indoor condenser 601 is communicated with an inlet of the first switching valve 635, and an outlet of the first switching valve 635 is selectively communicated with an inlet of the outdoor heat exchanger 605 via a first throttling branch or a first through-flow branch. As shown in particular in fig. 7, the outlet of the first on-off valve 635 may communicate with the inlet of the outdoor heat exchanger 605 via the first expansion on-off valve 603. Further, the refrigerant inlet 620a of the first plate heat exchanger 620 communicates with the outlet of the outdoor heat exchanger 605 via the selectively turned-on or turned-off battery cooling branch 621, or communicates with the first end of the selectively turned-on or turned-off first branch 641 and communicates with the first end of the selectively turned-on or turned-off second branch 642 via the selectively turned-on or turned-off battery cooling branch 621. In addition, the refrigerant inlet 620a of the first plate heat exchanger 620 is also in communication with the inlet of the first switch valve 635 via the selectively opened or closed battery heating branch 636, and the refrigerant outlet 620b of the first plate heat exchanger 620 is in communication with the inlet of the compressor 604 via the selectively opened or closed battery cooling return branch 622, and is in communication with the outlet of the first switch valve 635 via the battery heating return branch 637.

In the present invention, a refrigerant bypass branch, which is formed by the battery cooling branch 621, the first plate heat exchanger 620 and the battery cooling return branch 622 and is connected in parallel with the indoor evaporator 602, is added for cooling the battery, so that when in the heat pump high-temperature refrigeration mode, the refrigerant can be divided into two parts: one of the refrigerants flows to the indoor evaporator 602 and evaporates in the indoor evaporator 602 to absorb indoor ambient heat and lower indoor temperature; another strand of refrigerant flows to first plate heat exchanger 620 to carry out the heat transfer through first plate heat exchanger 620 and the coolant in the battery coolant return circuit of battery package heat transfer system, absorb the heat of coolant, and then can realize the cooling to the battery package.

In the present invention, the refrigerant inlet 620a of the first plate heat exchanger 620 is connected in two modes: in one embodiment, as shown in fig. 7, the refrigerant inlet 620a of the first plate heat exchanger 620 may communicate with the outlet of the outdoor heat exchanger 605 via a selectively opened or closed battery cooling branch 621. Specifically, a first expansion valve 623 may be provided on the battery cooling branch 621. In this way, it is possible to control whether the refrigerant can flow into the refrigerant inlet 620a of the first plate heat exchanger 620 by opening or closing the first expansion valve 623 according to actual demand. That is, whether the battery cooling branch 621 is in the on state or the off state is controlled.

In this embodiment, in the heat pump high temperature refrigeration mode, the refrigerant of medium temperature and high pressure coming out of the outdoor heat exchanger 605 is directly divided into two streams: one to the second expansion switch valve 606; and the other stream flows to the first expansion valve 623. In other words, the refrigerant is split and then throttled, cooled and depressurized on each branch.

In another embodiment, as shown in fig. 8, the refrigerant inlet 620a of the first plate heat exchanger 620 communicates with the first end of the first branch 641 and the first end of the second branch 642 via a battery cooling branch 621 that is selectively opened or closed, and a flow valve 625 is provided on the battery cooling branch 621. In the embodiment shown in fig. 8 in particular, the outlet of the outdoor heat exchanger 605 communicates with the first end of the first branch 641, which is selectively turned on or off, via the second expansion switching valve 606, communicates with the first end of the second branch 642, which is selectively turned on or off, and communicates with the refrigerant inlet 620a of the first plate heat exchanger 620 via the battery cooling branch 621, which is selectively turned on or off.

In this way, it is possible to control whether the refrigerant can flow into the refrigerant inlet 620a of the first plate heat exchanger 620 by controlling the flow valve 625, i.e., whether the battery cooling branch 621 is in the on state or the off state. In addition, controlling the flow valve 625 may also regulate the amount of flow of refrigerant into the first plate heat exchanger 620.

In this embodiment, in the heat pump high-temperature refrigeration mode, the refrigerant of medium temperature and high pressure coming out of the outdoor heat exchanger 605 is throttled by the second expansion switch valve 606 and then divided into two streams: one to the third on/off valve 644 (in this case, the second on/off valve 643 is closed) and the other to the flow valve 625 to achieve the distribution of the flow proportions of the two refrigerants. In other words, in this case, the refrigerant is throttled, reduced in temperature and pressure, and then split in the main line.

In order to prevent the low-temperature and low-pressure refrigerant from flowing back to the first plate heat exchanger 620 in the heat pump low-temperature heating mode, a first check valve 626 is provided in the battery cooling return branch 622. That is, the first check valve 626 permits the refrigerant to flow from the refrigerant outlet 620b of the first plate heat exchanger 620 to the inlet of the compressor 604 only in one direction, but not in the opposite direction.

In order to prevent the refrigerant of low temperature and low pressure from flowing back into the indoor evaporator 602 when only the battery pack is cooled, the outlet of the indoor evaporator 602 may communicate with the inlet of the compressor 604 via the third check valve 627. That is, the third check valve 627 allows refrigerant to flow from the outlet of the indoor evaporator 602 to the inlet of the compressor 604 only in one direction, and does not flow in the opposite direction.

Turning now to the schematic diagram of the thermal management system of the vehicle shown in FIG. 7. As shown in fig. 7, the refrigerant inlet 620a of the first plate heat exchanger 620 communicates with the inlet of the first switching valve 635 via the battery heating branch 636 which is selectively turned on or off, and the refrigerant outlet 620b of the first plate heat exchanger 620 communicates with the outlet of the first switching valve 635 via the battery heating return branch 637.

In the present invention, a first on-off valve 635 is added between the outlet of the indoor condenser 601 and the first expansion on-off valve 603, and a battery heating branch 636 and a battery heating return branch 637 which are respectively communicated with the refrigerant inlet 620a and the refrigerant outlet 620b of the first plate heat exchanger 620 are added, and the battery heating branch 636, the first plate heat exchanger 620 and the battery heating return branch 637 together form a refrigerant bypass branch which is connected in parallel with the first on-off valve 635 and is used for heating the battery. Thus, when in the low temperature heating plus battery heating mode, the high temperature and high pressure refrigerant from the compressor 604 can be split into two streams: one of them refrigerant flow direction indoor condenser 601's entry, the condensation is exothermic, rise indoor ambient temperature, it is the high-pressure liquid refrigerant of medium temperature to come out from indoor condenser 601, the export of indoor condenser 601 links to each other with the entry of first ooff valve 635, another refrigerant flow direction first plate heat exchanger 620, and exchange heat through the coolant liquid in first plate heat exchanger 620 and the battery coolant liquid return circuit of battery package heat exchange system, the condensation is exothermic, the heat of refrigerant release is absorbed to the coolant liquid, and then can realize the heating intensification to the battery package.

To facilitate control of whether refrigerant flows through the battery heating branch, a fourth on-off valve 638 is provided on the battery heating branch 636. Thus, when it is desired to heat the battery, for example, in a battery heating mode, the fourth switch valve 638 may be opened, and the refrigerant may flow through the first plate heat exchanger 620 to provide heat to the battery pack heat exchange system. When the battery is not required to be heated, for example, in the battery cooling mode, the fourth switch valve 638 may be closed, so as to prevent the refrigerant with high temperature and high pressure from entering the first plate heat exchanger 620 to heat the battery, which may further increase the temperature of the battery.

To prevent the low-temperature and high-pressure liquid refrigerant from the refrigerant outlet 620b of the first plate heat exchanger 620 from directly flowing to the compressor 604 in the battery heating mode, causing damage to the compressor, a fifth switching valve 639 is provided in the battery cooling return branch 622. Thus, when the system is in the battery heating mode, the fifth switching valve 639 may be closed, and at this time, the battery cooling return branch 622 is cut off, so that the low-temperature and high-pressure liquid refrigerant coming out of the refrigerant outlet 620b of the first plate heat exchanger 620 flows to the first expansion switching valve 603 entirely via the battery heating return branch 637.

In order to prevent the high-temperature and high-pressure gas refrigerant flowing out of the indoor condenser 601 from flowing to the refrigerant outlet 620b of the first plate heat exchanger 620 along the battery heating return branch 637 after passing through the first switching valve 635 in the battery cooling mode, the battery heating return branch 637 is provided with a second check valve 640. That is, the second check valve 640 may unidirectionally allow the refrigerant to flow from the refrigerant outlet 620b of the first plate heat exchanger 620 to the inlet of the first expansion switching valve 603, but not in the opposite direction.

Furthermore, as shown in fig. 7 and 8, the first plate heat exchanger 620 is connected in series in a coolant circuit of the battery pack heat exchange system, and a first water pump 628, a radiator 629 and a battery pack 630 are also provided in the coolant circuit in series with the first plate heat exchanger 620, wherein the battery coolant can flow into the first plate heat exchanger 620 via a battery coolant inlet 620f of the first plate heat exchanger 620 and flow out of the first plate heat exchanger 620 via a battery coolant outlet 620e of the first plate heat exchanger 620. When the battery cooling branch 621 is conducting, the refrigerant of the heat pump air conditioning system may flow into the first plate heat exchanger 620 via the refrigerant inlet 620a of the first plate heat exchanger 620 and flow out of the first plate heat exchanger 620 via the refrigerant outlet 620b of the first plate heat exchanger 620. In this way, through first plate heat exchanger 620, can realize the heat exchange of refrigerant and battery coolant to cool down for the battery package. When the battery heating branch 636 is on, the refrigerant of the heat pump air conditioning system may flow into the first plate heat exchanger 620 via the refrigerant inlet 620a of the first plate heat exchanger 620 and flow out of the first plate heat exchanger 620 via the refrigerant outlet 620b of the first plate heat exchanger 620. In this way, the first plate heat exchanger 620 can exchange heat between the refrigerant and the battery coolant, thereby heating the battery pack.

As described above, in order to prevent the liquid refrigerant from entering the compressor 604 to damage the compressor 604, thereby making it possible to extend the life span of the compressor 604 and improve the efficiency of the entire heat pump air conditioning system, the gas-liquid separator 611 is provided in the heat pump air conditioning system. As shown in fig. 7 and 8, the inlet of the gas-liquid separator 611 communicates with the inlet of the gas-liquid separator 611 via the battery cooling return branch 622 in addition to the outlet of the indoor evaporator 602 and the second end of the first branch 641, and the refrigerant outlet 620b of the first plate heat exchanger 620 communicates with the inlet of the gas-liquid separator 611. In other words, the refrigerant coming out of the first plate heat exchanger 620 may first pass through the gas-liquid separator 611 to undergo gas-liquid separation, and the separated gas may flow back to the compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 and damaging the compressor 604.

Further, as shown in fig. 7 and 8, the engine cooling system includes a second water pump 631, an engine 632, an indoor warm air core 633, and a second three-way valve 634, wherein an outlet of the second water pump 631 communicates with an inlet 634a of the second three-way valve 634, a first outlet 634b and a second outlet 634c of the second three-way valve 634 communicate with an engine coolant inlet 620c of the first plate heat exchanger 620 and an inlet of the indoor warm air core 633, respectively, an engine coolant outlet 620d of the first plate heat exchanger 620 and an outlet of the indoor warm air core 633 both communicate with a coolant inlet of the engine 632, and a coolant outlet of the engine 632 communicates with an inlet of the second water pump 631.

When the second water pump 631 is switched on, and the inlet 634a of the second three-way valve 634 is conducted with the first outlet 634b of the second three-way valve 634, the engine coolant may flow into the first plate heat exchanger 620 via the engine coolant inlet 620c of the first plate heat exchanger 620 and flow out of the first plate heat exchanger 620 via the engine coolant outlet 620d of the first plate heat exchanger 620. In this way, the battery pack can be heated by the residual heat of the engine 632. In addition, it is also possible to supply heat to the interior of the vehicle by using the residual heat of the engine by conducting the inlet 634a of the second three-way valve 634 and the second outlet 634c of the second three-way valve 634 such that the engine coolant flows into the indoor warm air core 633.

The following describes in detail the cycle and principle of the thermal management system of the automobile in different operation modes by taking fig. 7 as an example. It should be understood that the system cycle process and principle under other embodiments (e.g., the embodiment shown in fig. 8) are similar to those in fig. 7, and are not described in detail herein.

The first mode is as follows: and (4) a heat pump high-temperature refrigeration cycle mode. When the system is in this mode, the entire system forms a high temperature refrigeration cycle. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the control air does not pass through the indoor condenser 601, and since no air passes through, heat exchange does not occur in the indoor condenser 601, and the indoor condenser 601 is used only as a flow passage, and at this time, the control air is still high-temperature and high-pressure air that has come out of the indoor condenser 601. The outlet of the indoor condenser 601 is connected to the first expansion switch valve 603 via the first switch valve 635, and the first expansion switch valve 603 functions as a switch valve and only serves as a flow passage, and the gas still having high temperature and high pressure flows out of the first expansion switch valve 603. The outlet of the first expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the liquid which comes out of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the outdoor heat exchanger 605 is connected to the second expansion switch valve 606, and at this time, the second expansion switch valve 606 functions as an expansion valve and functions as a throttling element to perform throttling, and low-temperature and low-pressure liquid flows out. The opening degree of the second expansion switching valve 606 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the evaporator outlet refrigerant from the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The second switching valve 643 is closed and the third switching valve 644 is opened, so that the first branch 641 is blocked and the second branch 642 is conducted. The low-temperature and low-pressure liquid from the second expansion switch valve 606 enters the indoor evaporator 602 to be evaporated, and absorbs indoor heat to lower the indoor temperature, so that the low-temperature and low-pressure gas exits from the indoor evaporator 602. The indoor evaporator 602 is connected to the gas-liquid separator 611 via the third check valve 627, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure is returned to the compressor 604, thereby forming a circulation. In this case, air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. In this mode, the first expansion valve 623 is closed, the first water pump 628 is closed, the second water pump 631 is closed, the second three-way valve 634 is de-energized, i.e., closed, the first switching valve 635 is opened, and the fourth switching valve 638 is closed.

And a second mode: battery cooling circulation mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the control air does not pass through the indoor condenser 601, and since no air passes through, heat exchange does not occur in the indoor condenser 601, and the indoor condenser 601 is used only as a flow passage, and at this time, the control air is still high-temperature and high-pressure air that has come out of the indoor condenser 601. The outlet of the indoor condenser 601 is connected to the first expansion switch valve 603 via the first switch valve 635, and the first expansion switch valve 603 functions as a switch valve and only serves as a flow passage, and the gas still having high temperature and high pressure flows out of the first expansion switch valve 603. The outlet of the first expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the liquid which comes out of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the outdoor heat exchanger 605 is connected to the first expansion valve 623, and the low-temperature and low-pressure liquid flows out of the first expansion valve 623 after the throttling and cooling of the first expansion valve 623. The opening degree of the first expansion valve 623 may be given an opening degree according to actual demand, which may be adjusted according to pressure and temperature acquisition data of a pressure-temperature sensor installed between the refrigerant outlet 620b of the first plate heat exchanger 620 and the inlet of the gas-liquid separator 611. The outlet of the first expansion valve 623 is connected to the refrigerant inlet 620a of the first plate heat exchanger 620, and the low-temperature and low-pressure liquid exchanges heat with the hot water from the battery pack 630 in the first plate heat exchanger 620, so that the refrigerant outlet 620b of the first plate heat exchanger 620 is low-temperature and low-pressure gas. The refrigerant outlet 620b of the first plate heat exchanger 620 is connected to a fifth switch valve 639, the fifth switch valve 639 is connected to a first check valve 622, the low-temperature and low-pressure gas passes through the fifth switch valve 639 and the first check valve 622 and then enters a gas-liquid separator 611, the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas returns to the compressor 604, thereby forming a cycle. At this time, the indoor condenser 601 passes no air, and flows only as a refrigerant flow path. In this mode, the first expansion valve 623 is opened, the second expansion switching valve 606 is closed, the first water pump 628 is opened, the second water pump 631 is closed, the second three-way valve 634 is de-energized, the first switching valve 635 is opened, the fourth switching valve 638 is closed, and the fifth switching valve 639 is opened.

And a third mode: and a heat pump high-temperature refrigeration and battery cooling circulation mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the control air does not pass through the indoor condenser 601, and since no air passes through, heat exchange does not occur in the indoor condenser 601, and the indoor condenser 601 is used only as a flow passage, and at this time, the control air is still high-temperature and high-pressure air that has come out of the indoor condenser 601. The outlet of the indoor condenser 601 is connected to the first expansion switch valve 603 via the first switch valve 635, and the first expansion switch valve 603 functions as a switch valve and only serves as a flow passage, and the gas still having high temperature and high pressure flows out of the first expansion switch valve 603. The outlet of the first expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the liquid which comes out of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the outdoor heat exchanger 605 is connected to the second expansion switch valve 606 and the first expansion valve 623, and at this time, the medium-temperature and high-pressure liquid from the outdoor heat exchanger 605 is divided into two streams: one flows to the inlet of the second expansion switch valve 606, and at this time, the second expansion switch valve 606 functions as an expansion valve, and functions as a throttling element to perform throttling, and the low-temperature and low-pressure liquid flows out. The opening degree of the second expansion switching valve 606 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the evaporator outlet refrigerant from the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The second switching valve 643 is closed and the third switching valve 644 is opened, so that the first branch 641 is blocked and the second branch 642 is conducted. The low-temperature and low-pressure liquid from the second expansion switch valve 606 enters the indoor evaporator 602 to be evaporated, and absorbs indoor heat to lower the indoor temperature, so that the low-temperature and low-pressure gas exits from the indoor evaporator 602. The other stream flows to the inlet of the first expansion valve 623, and the opening degree of the first expansion valve 623 may be given a certain opening degree according to actual demand, which may be adjusted according to pressure and temperature acquisition data of a pressure-temperature sensor between the refrigerant outlet 620b of the first plate heat exchanger 620 and the inlet of the gas-liquid separator 611. The temperature is reduced by throttling the first expansion valve 623, and the low-temperature and low-pressure liquid flows out of the first expansion valve 623. The outlet of the first expansion valve 623 is connected to the refrigerant inlet 620a of the first plate heat exchanger 620, and the low-temperature and low-pressure liquid exchanges heat with the hot water from the battery pack 630 in the first plate heat exchanger 620, so that the refrigerant outlet 620b of the first plate heat exchanger 620 is low-temperature and low-pressure gas. The outlet of the indoor evaporator 602 is connected with the gas-liquid separator 611 through the third check valve 627, the refrigerant outlet 620b of the first plate heat exchanger 620 is connected with the fifth switch valve 639, the fifth switch valve 639 is connected with the first check valve 622, the low-temperature and low-pressure gas from the refrigerant outlet 620b of the first plate heat exchanger 620 passes through the fifth switch valve 639 and the first check valve 622 and then joins with the low-temperature and low-pressure gas from the indoor evaporator 602, and enters the gas-liquid separator 611, the liquid which is not evaporated is separated through the gas-liquid separator 611, and finally the low-temperature and low-pressure gas returns to the compressor 604, thereby forming a cycle. In this case, air flows only through the indoor evaporator 602 in the HVAC unit 600, and air flows only through the indoor condenser 601 as a refrigerant flow path without passing through. In this mode, the first expansion valve 623 is opened, the second expansion switch valve 606 is opened, the first water pump 628 is opened, the second water pump 631 is closed, the second three-way valve 634 is de-energized, the first switch valve 635 is opened, the fourth switch valve 638 is closed, and the fifth switch valve 639 is opened.

And a fourth mode: and (4) a heat pump low-temperature heating circulation mode. As shown in fig. 7, first, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, the high-temperature and high-pressure gas is condensed in the indoor condenser 601, heat is released into the room, and the indoor temperature is increased, so that medium-temperature and high-pressure liquid is discharged from the indoor condenser 601. The outlet of the indoor condenser 601 is connected to the first expansion switch valve 603 via the first switch valve 635, and the first expansion switch valve 603 functions as an expansion valve and a throttling element, and the outlet of the first expansion switch valve 603 is low-temperature and low-pressure liquid. The opening degree of the first expansion switching valve 603 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the compressor discharge temperature) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion switch valve 603 is connected to an outdoor heat exchanger 605, and the outdoor heat exchanger 605 absorbs heat of outdoor air, and low-temperature and low-pressure gas flows out of the outdoor heat exchanger 605. The outlet of the outdoor heat exchanger 605 is connected to a second expansion switching valve 606, and the second expansion switching valve 606 functions as a switching valve and flows only as one flow path. The second switching valve 643 is opened and the third switching valve 644 is closed, so that the first branch 641 is turned on and the second branch 642 is turned off. The low-temperature low-pressure gas from the second expansion switch valve 606 directly enters a gas-liquid separator 611, the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas returns to the compressor 604, thereby forming a cycle. At this time, in this mode, the first expansion valve 623 is closed, the first water pump 628 is closed, the second water pump 631 is closed, the second three-way valve 634 is de-energized, the first on-off valve 635 is opened, and the fourth on-off valve 638 is closed.

Based on the existing HVAC blower design, if it is desired to control the air flow through the indoor condenser 601, the air first passes through the indoor evaporator 602 before entering the indoor condenser 601. However, since heat exchange is not performed in the indoor evaporator 602 in the warming mode, the first branch 641 is turned on and the second branch 642 is turned off, so that the indoor evaporator 602 is short-circuited, and even if wind flows through the indoor evaporator 602, the refrigerant temperature is not affected.

And a fifth mode: and (3) a low-temperature heating circulation mode of the engine. As shown in fig. 7, the high-temperature coolant from the engine 632 passes through the second water pump 631, the inlets 634a to 634c of the second three-way valve 634, passes through the indoor warm air core 633, exchanges heat with air to cool the coolant to a low temperature, and then flows back to the engine 632, thereby completing one cycle. In this mode, the compressor 604, the first on-off valve 635, the fourth on-off valve 638, the fifth on-off valve 639, the first expansion on-off valve 603, the second expansion on-off valve 606, the first expansion valve 623, the second on-off valve 643, and the third on-off valve 644 are all in the power-off state, the first water pump 628 is turned off, the second water pump 631 operates, the inlet 634a to the outlet 634c of the second three-way valve 634 are open, and the inlet 634a to the outlet 634b are not open.

Mode six: heat pump mode battery heating cycle mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and at this time, the control air does not pass through the indoor condenser 601, and since no air passes through, no heat exchange is performed in the indoor condenser 601, and the indoor condenser 601 is used only as a flow channel, and at this time, the high-temperature and high-pressure gas is discharged from the indoor condenser 601. An outlet of the indoor condenser 601 is connected with a fourth switch valve 638, the fourth switch valve 638 is connected with a refrigerant inlet 620a of the first plate heat exchanger 620, high-temperature and high-pressure gas flowing out of the indoor condenser 601 exchanges heat with cold water coming out of the battery pack 630 in the first plate heat exchanger 620, and a refrigerant outlet 620b of the first plate heat exchanger 620 is liquid refrigerant with medium temperature and high pressure. The refrigerant outlet 620b of the first plate heat exchanger 620 is connected to the outlet of the first switching valve 635 through the second check valve 640, and the outlet of the first switching valve 635 is connected to the inlet of the first expansion switching valve 603. At this time, the first expansion switching valve 603 functions as an expansion valve, functions as a throttling element, and outputs low-temperature and low-pressure liquid. The opening degree of the first expansion switching valve 603 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the compressor discharge temperature) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion switch valve 603 is connected to an outdoor heat exchanger 605, and the outdoor heat exchanger 605 absorbs heat of outdoor air, and low-temperature and low-pressure gas flows out of the outdoor heat exchanger 605. The outlet of the outdoor heat exchanger 605 is connected to a second expansion switching valve 606, and the second expansion switching valve 606 functions as a switching valve and flows only as one flow path. The second switching valve 643 is opened and the third switching valve 644 is closed, so that the first branch 641 is turned on and the second branch 642 is turned off. The low-temperature low-pressure gas from the second expansion switch valve 606 directly enters a gas-liquid separator 611, the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas returns to the compressor 604, thereby forming a cycle. Through the first plate heat exchanger 620, the battery pack can be heated by using the refrigerant of the heat pump air conditioning system, so that the temperature of the battery pack can be increased. In the HVAC assembly 600, no wind flows to the indoor condenser 601 and the indoor evaporator 602, and only flows through as a refrigerant flow passage. In this mode, the first on-off valve 635 is closed, the fourth on-off valve 638 is opened, the first expansion valve 623 is closed, the second expansion on-off valve 606 is opened, the first water pump 628 is opened, the second water pump 631 is closed, and the second three-way valve 634 is de-energized.

Mode seven: engine mode battery heating cycle mode. As shown in fig. 7, the high-temperature coolant from the engine 632 flows to the first plate heat exchanger 620 through the second water pump 631 and the inlets 634a to 634b of the second three-way valve 634, exchanges heat with the cold water from the battery pack 630 to cool the coolant to a low temperature, and then flows back to the engine 632, thereby completing one cycle of engine-mode battery heating. Through first plate heat exchanger 620, can utilize the engine coolant to heat for the battery package, raise the temperature of battery package. In this mode, the compressor 604, the first on-off valve 635, the fourth on-off valve 638, the fifth on-off valve 639, the first expansion on-off valve 603, the second expansion on-off valve 606, the first expansion valve 623, the second on-off valve 643, and the third on-off valve 644 are all in the de-energized state, the first water pump 628 is operated, the second water pump 631 is operated, the inlet 634a to the outlet 634b of the second three-way valve 634 are open, and the inlet 634a to the outlet 634c are closed.

And a mode eight: and a heat pump mode low-temperature heating and battery heating circulation mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that medium-temperature and high-pressure liquid is discharged from the indoor condenser 601. At this time, the medium-temperature and high-pressure liquid from the indoor condenser 601 is divided into two streams: one of the refrigerant flows into the first plate heat exchanger 620 through the fourth switching valve 638, and exchanges heat with the cold water coming out of the battery pack 630 at the first plate heat exchanger 620, the refrigerant outlet 620b of the first plate heat exchanger 620 is the liquid refrigerant with medium temperature and high pressure, and the refrigerant outlet 620b of the first plate heat exchanger 620 is connected to the outlet of the first switching valve 635 through the second check valve 640. The other flow passes through the first on-off valve 635, and then joins the medium-temperature and high-pressure liquid refrigerant flowing out of the outlet of the second check valve 640, and flows into the inlet of the first expansion on-off valve 603. At this time, the first expansion switching valve 603 functions as an expansion valve, functions as a throttling element, and outputs low-temperature and low-pressure liquid. The opening degree of the first expansion switching valve 603 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the compressor discharge temperature) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion switch valve 603 is connected to an outdoor heat exchanger 605, and the outdoor heat exchanger 605 absorbs heat of outdoor air, and low-temperature and low-pressure gas flows out of the outdoor heat exchanger 605. The outlet of the outdoor heat exchanger 605 is connected to a second expansion switching valve 606, and the second expansion switching valve 606 functions as a switching valve and flows only as one flow path. The second switching valve 643 is opened and the third switching valve 644 is closed, so that the first branch 641 is turned on and the second branch 642 is turned off. The low-temperature low-pressure gas from the second expansion switch valve 606 directly enters a gas-liquid separator 611, the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas returns to the compressor 604, thereby forming a cycle. Through the first plate heat exchanger 620, the battery pack can be heated by using the refrigerant of the heat pump air conditioning system, so that the temperature of the battery pack can be increased. At this time, in this mode, the fourth switching valve 638 is opened, the first switching valve 635 is in an open state, the first expansion valve 623 is in a closed state, the fifth switching valve 639 is closed, the first water pump 628 is opened, the second water pump 631 is closed, and the second three-way valve 634 is de-energized.

The mode nine: the engine mode is low-temperature heating and battery heating circulation mode. As shown in fig. 7, the high-temperature coolant from the engine 632 passes through the second water pump 631 and is branched at the second three-way valve 634, one path of the coolant passes through the inlets 634a to 634b of the second three-way valve 634 to the first plate heat exchanger 620, and exchanges heat with the cold water from the battery pack 630 to cool the coolant to a low temperature, and the other path of the coolant passes through the inlets 634a to 634c of the second three-way valve 634 to the indoor warm air core 633 and exchanges heat with the air to cool the coolant to a low temperature, and the coolant flowing out of the engine coolant outlet 620d of the first plate heat exchanger 620 and the indoor warm air core 633 flows back to the engine 632 together, thereby completing an engine mode low-temperature heating and battery heating cycle. Through first plate heat exchanger 620, can utilize the engine coolant to heat for the battery package, raise the temperature of battery package. In this mode, the compressor 604, the first on-off valve 635, the fourth on-off valve 638, the fifth on-off valve 639, the first expansion on-off valve 603, the second expansion on-off valve 606, the first expansion valve 623, the second on-off valve 643, and the third on-off valve 644 are all in the de-energized state, the first water pump 628 is operated, the second water pump 631 is operated, the inlet 634a to the outlet 634b of the second three-way valve 634 are open, and the inlet 634a to the outlet 634c are open.

As described above, in the present invention, the expansion opening/closing valve is a valve having both the expansion valve function and the opening/closing valve function, and may be regarded as an integration of the opening/closing valve and the expansion valve. Hereinafter, an example embodiment of an expansion switching valve will be provided.

The above-mentioned expansion switching valve may include a valve body 500, wherein the valve body 500 is formed with an inlet 501, an outlet 502, and an internal flow passage communicating between the inlet 501 and the outlet 502, the internal flow passage is mounted with a first valve spool 503 and a second valve spool 504, the first valve spool 503 makes the inlet 501 and the outlet 502 directly communicate or disconnect from each other, and the second valve spool 504 makes the inlet 501 and the outlet 502 communicate or disconnect from each other through a choke 505.

The "direct communication" realized by the first valve core means that the coolant entering from the inlet 501 of the valve body 500 can pass through the first valve core and directly flow to the outlet 502 of the valve body 500 through the internal flow passage without being affected, and the "disconnection communication" realized by the first valve core means that the coolant entering from the inlet 501 of the valve body 500 cannot pass through the first valve core and cannot flow to the outlet 502 of the valve body 500 through the internal flow passage. The "communication through the orifice" realized by the second valve spool means that the coolant entering from the inlet 501 of the valve body 500 can flow to the outlet 502 of the valve body 500 through the orifice after passing through the second valve spool and throttling, and the "disconnection" realized by the second valve spool means that the coolant entering from the inlet 501 of the valve body 500 cannot flow to the outlet 502 of the valve body 500 through the orifice 505 without passing through the second valve spool.

Thus, the expansion switching valve of the present invention can allow the coolant entering from the inlet 501 to achieve at least three states by controlling the first and second spools. I.e., 1) an off state; 2) a direct communication state across the first spool 503; and 3) throttle communication across the second spool 504.

The high-temperature and high-pressure liquid refrigerant can be turned into low-temperature and low-pressure fog-shaped hydraulic refrigerant after being throttled by the throttle 505, conditions can be created for evaporation of the refrigerant, namely the cross-sectional area of the throttle 505 is smaller than that of the outlet 504, and the opening degree of the throttle 505 can be adjusted by controlling the second valve core, so that the flow rate of the refrigerant flowing through the throttle 505 is controlled, insufficient refrigeration caused by too little refrigerant is prevented, and liquid impact of the compressor caused by too much refrigerant is prevented. That is, the cooperation of the second valve spool 504 and the valve body 500 may make the expansion switching valve function as an expansion valve.

Thus, the first valve core 503 and the second valve core 504 are arranged on the internal flow passage of the same valve body 500 to realize the on-off control and/or throttling control functions of the inlet 501 and the outlet 502, the structure is simple, the production and the installation are easy, and when the expansion switch valve provided by the invention is applied to a heat pump system, the refrigerant charge of the whole heat pump system can be reduced, the cost is reduced, the pipeline connection is simplified, and the oil return of the heat pump system is facilitated.

As an exemplary internal mounting structure of the valve body 500, as shown in fig. 9 to 14, the valve body 500 includes a valve seat 510 forming an internal flow passage, and a first valve housing 511 and a second valve housing 512 mounted on the valve seat 510, a first electromagnetic driving part 521 for driving a first valve core 503 is mounted in the first valve housing 511, a second electromagnetic driving part 522 for driving a second valve core 504 is mounted in the second valve housing 512, the first valve core 503 extends from the first valve housing 511 to the internal flow passage in the valve seat 510, and the second valve core 504 extends from the second valve housing 512 to the internal flow passage in the valve seat 510.

Wherein, the position of the first valve core 503 can be conveniently controlled by controlling the on/off of the first electromagnetic driving part 521, such as an electromagnetic coil, so as to control the direct connection or disconnection of the inlet 501 and the outlet 502; the position of the second spool 504 can be conveniently controlled by controlling the energization and de-energization of the second electromagnetic drive 522, e.g., a solenoid, to control whether the inlet 501 and outlet 502 are in communication with the orifice 505. In other words, the electronic expansion valve and the electromagnetic valve, which share the inlet 501 and the outlet 502, are installed in parallel in the valve body 500, so that the automatic control of the on-off and/or throttling of the expansion switch valve can be realized, and the pipeline trend is simplified.

In order to fully utilize the spatial positions of the expansion switch valve in all directions and prevent the expansion switch valve from interfering with the connection of different pipelines, the valve seat 510 is formed in a polyhedral structure, and the first and

second valve casings

511 and 512, the inlet 501 and the outlet 502 are respectively disposed on different surfaces of the polyhedral structure, wherein the installation directions of the first and

second valve casings

511 and 512 are perpendicular to each other, and the opening directions of the inlet 501 and the outlet 502 are perpendicular to each other. Like this, can be with import, outlet pipe way connection on polyhedral structure's different surfaces, can avoid the problem that the pipeline arrangement is in disorder, tangled.

As a typical internal structure of the expansion switching valve, as shown in fig. 9 to 12, the internal flow passage includes a first flow passage 506 and a second flow passage 507 respectively communicating with the inlet 501, the first flow passage 506 is formed with a first valve port 516 cooperating with the first spool 503, the orifice 505 is formed in the second flow passage 507 to form a second valve port 517 cooperating with the second spool 504, and the first flow passage 506 and the second flow passage 507 meet downstream of the second valve port 517 and communicate with the outlet 502.

That is, the position of the first valve core 503 is changed to close or open the first valve port 516, and thus the blocking or communication of the first flow passage 506 communicating the inlet 501 and the outlet 502 is controlled, so that the above-described function of communicating or blocking the communication of the solenoid valve can be realized. Similarly, the position of the second valve element 504 is changed to open or close the second valve port 517, thereby achieving the throttle function of the electronic expansion valve.

The first flow channel 506 and the second flow channel 507 can respectively communicate with the inlet 501 and the outlet 502 in any suitable arrangement, in order to reduce the overall occupied space of the valve body 500, as shown in fig. 13, the second flow channel 507 and the outlet 502 are opened in the same direction, the first flow channel 506 is formed as a first through hole 526 perpendicular to the second flow channel 507, the inlet 501 communicates with the second flow channel 507 through a second through hole 527 opened on the side wall of the second flow channel 507, and the first through hole 526 and the second through hole 527 respectively communicate with the inlet 501. The first through hole 526 may be spatially perpendicular to or parallel to the second through hole 527, which is not limited in the present invention and falls within the protection scope of the present invention.

To further simplify the overall footprint of the valve body 500, as shown in fig. 16-19, an inlet 501 and an outlet 502 are provided on the valve body 500 perpendicular to each other. In this way, as shown in fig. 16 to 18, the axis of the inlet 501, the axis of the outlet 502 (i.e., the axis of the second flow passage 507), and the axis of the first flow passage 506 are arranged vertically two by two in space, thereby preventing interference of the movements of the first and

second spools

503 and 504 and enabling maximum use of the internal space of the valve body 500.

As shown in fig. 12 and 13, to facilitate the closing and opening of the first port 516, the first valve element 503 is disposed coaxially with the first port 516 in the moving direction to selectively block or separate from the first port 516.

To facilitate the closing and opening of the second valve port 517, the second spool 504 is disposed coaxially with the second valve port 517 in the moving direction to selectively block or disengage the second valve port 517.

As shown in fig. 15, in order to ensure the reliability of the first valve core 503 for blocking the first flow passage 506, the first valve core 503 may include a first valve rod 513 and a first plug 523 connected to an end of the first valve rod 513, wherein the first plug 523 is used for sealing and pressing against an end surface of the first valve port 516 to block the first flow passage 506.

To facilitate adjustment of the opening degree of the orifice 505 of the expansion switch valve, as shown in fig. 12 and 13, the second valve spool 504 includes a second valve stem 514, an end portion of the second valve stem 514 is formed into a conical head structure, and the second valve port 517 is formed into a conical hole structure matched with the conical head structure.

The opening degree of the orifice 505 of the expansion switch valve can be adjusted by the vertical movement of the second valve element 504, and the vertical movement of the second valve element 504 can be adjusted by the second electromagnetic driving unit 522. If the opening degree of the orifice 505 of the expansion switch valve is zero, as shown in fig. 12, the second valve body 504 is at the lowest position, the second valve body 504 blocks the second valve port 517, and the refrigerant cannot pass through the orifice 505 at all, that is, the second valve port 517; if the expansion switch valve orifice 505 has an opening degree, as shown in fig. 13, a gap is formed between the orifice 505 and the tapered head structure at the end of the second valve body 504, and the refrigerant is throttled and then flows to the outlet 502. If the throttle opening of the expansion switch valve needs to be increased, the second electromagnetic driving part 522 is controlled to enable the second valve core 504 to move upwards, so that the conical head structure is far away from the throttle opening 505, and the opening of the throttle opening 505 is increased; on the contrary, when the opening degree of the orifice 505 of the expansion switch valve needs to be decreased, the second spool 504 may be driven to move downward.

In use, when only the solenoid function of the expansion switch valve is required, as shown in fig. 12, 15, and 18, the first valve body 503 is separated from the first port 516, the first port 516 is in an open state, the second valve body 504 is at the lowest position, the second valve body 504 closes the orifice 505, and the refrigerant flowing into the internal flow path from the inlet 501 cannot pass through the orifice 505 at all but flows into the outlet 502 through the first port 516 and the first through hole 526 in this order. When the electromagnetic valve is powered off, the first valve core 503 moves to the left, the first plug 523 is separated from the first valve port 516, and the refrigerant can pass through the first through hole 526; when the electromagnetic valve is energized, the first valve core 503 moves rightwards, the first plug 523 is attached to the first valve port 516, and the refrigerant cannot pass through the first through hole 526.

Note that the dashed lines with arrows in fig. 12 and 18 represent the flow paths and the direction of the refrigerant when the solenoid valve function is used.

When only the electronic expansion valve function using the expansion switch valve is required, as shown in fig. 13 and 19, the second port 517, i.e., the choke 505, is in an open state, the first valve body 503 closes the first port 516, the refrigerant flowing from the inlet 501 into the internal flow passage cannot flow through the first through hole 526 but flows only through the second through hole 527 and the choke 505 into the outlet 502, and the second valve body 504 can be moved up and down to adjust the opening degree of the choke 505.

In fig. 13 and 19, dotted lines with arrows represent flow paths and directions of the refrigerant when the electronic expansion valve function is used.

When it is required to simultaneously use the solenoid valve function and the electronic expansion valve function of the expansion switch valve, as shown in fig. 10, 16 and 17, wherein the dotted lines with arrows represent the flow path and the direction of the refrigerant, the first valve spool 503 is separated from the first valve port 516, the first valve port 516 is in an open state, and the orifice 505 is in an open state, the refrigerant flowing into the internal flow passage can flow to the outlet 502 along the first flow passage 506 and the second flow passage 507, respectively, thereby simultaneously having the solenoid valve function and the electronic expansion valve function.

It should be understood that the above-described embodiment is merely an example of one of the expansion on-off valves, and is not intended to limit the present invention, and other expansion on-off valves having both the expansion valve function and the on-off valve function are also applicable to the present invention.

The invention further provides an electric automobile which comprises the automobile thermal management system provided by the invention. The electric vehicle may be a hybrid vehicle.

The preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, however, the present invention is not limited to the specific details of the above embodiments, and various simple modifications can be made to the technical solution of the present invention within the technical idea of the present invention, and these simple modifications are within the protective scope of the present invention.

It should be noted that the various features described in the above embodiments may be combined in any suitable manner without departing from the scope of the invention. The invention is not described in detail in order to avoid unnecessary repetition.

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

Claims

1. An automotive thermal management system, characterized in that the automotive thermal management system comprises a heat pump air conditioning system, a battery pack heat exchange system, an engine cooling system, a first plate heat exchanger (620) and a first switch valve (635), the heat pump air conditioning system and the engine cooling system exchange heat with the battery pack heat exchange system through the first plate heat exchanger (620) respectively, the heat pump air conditioning system comprises an indoor condenser (601), an indoor evaporator (602), a compressor (604) and an outdoor heat exchanger (605), an outlet of the compressor (604) is communicated with an inlet of the indoor condenser (601), an outlet of the indoor condenser (601) is communicated with an inlet of the first switch valve (635), an outlet of the first switch valve (635) is selectively communicated with an inlet of the outdoor heat exchanger (605) through a first throttling branch or a first through-flow branch, an outlet of the outdoor heat exchanger (605) is selectively communicated with a first end of a first selectively opened or closed branch (641) and a first end of a second selectively opened or closed branch (642) through a second throttling branch or a second circulating branch, a second end of the first branch (641) is communicated with an inlet of the compressor (604), a second end of the second branch (642) is communicated with an inlet of the indoor evaporator (602), an outlet of the indoor evaporator (602) is communicated with an inlet of the compressor (604), a refrigerant inlet (620a) of the first plate heat exchanger (620) is communicated with an outlet of the outdoor heat exchanger (605) through a selectively opened or closed battery cooling branch (621) or communicated with a first end of the first branch (641) and a first end of the second branch (642), and communicates with an inlet of the first on-off valve (635) via a selectively opened or closed battery heating branch (636), a refrigerant outlet (620b) of the first plate heat exchanger (620) communicates with an inlet of the compressor (604) via a selectively opened or closed battery cooling return branch (622), and communicates with an outlet of the first on-off valve (635) via a battery heating return branch (637).

2. The automotive thermal management system of claim 1, characterized in that a second on-off valve (643) is disposed on the first branch (641).

3. The automotive thermal management system of claim 1, characterized in that a third on-off valve (644) is arranged on the second branch (642).

4. The automotive thermal management system of claim 1, wherein the heat pump air conditioning system further comprises: a first three-way valve (645), an outlet of the outdoor heat exchanger (605) selectively communicating with an inlet of the first three-way valve (645) via a second throttling branch or a second bypass branch, a first outlet of the first three-way valve (645) communicating with a first end of the first branch (641), a second outlet of the first three-way valve (645) communicating with a first end of the second branch (642).

5. The automotive thermal management system of claim 1, characterized in that a fourth switching valve (638) is disposed on the battery heating branch (636).

6. The automotive thermal management system of claim 1, wherein a fifth on-off valve (639) is provided on the battery cooling return branch (622).

7. The automotive thermal management system of claim 6, further characterized in that a first one-way valve (626) is disposed on the battery cooling return branch (622).

8. The automotive thermal management system of claim 1, wherein a second one-way valve (640) is disposed on the battery heater return branch (637).

9. The automotive thermal management system of claim 1, characterized in that a refrigerant inlet (620a) of the first plate heat exchanger (620) communicates with an outlet of the outdoor heat exchanger (605) via a selectively conducting or blocking battery cooling branch (621), and a first expansion valve (623) is disposed in the battery cooling branch.

10. The automotive thermal management system according to claim 1, characterized in that a refrigerant inlet (620a) of the first plate heat exchanger (620) communicates with a first end of the first branch (641) and a first end of the second branch (642) via a selectively conducting or blocking battery cooling branch (621), and a flow valve (625) is provided on the battery cooling branch (621).

11. The automotive thermal management system of claim 1, wherein an outlet of the indoor evaporator (602) communicates with an inlet of the compressor (604) via a third one-way valve (627).

12. The automotive thermal management system of claim 1, wherein the first plate heat exchanger (620) is connected in series in a coolant circuit of the battery pack heat exchange system, and wherein a first water pump (628), a radiator tank (629) and a battery pack (630) are also provided in the coolant circuit in series with the first plate heat exchanger (620).

13. The automotive thermal management system of claim 1, characterized in that the engine cooling system comprises a second water pump (631), an engine (632), an indoor heater core (633), and a second three-way valve (634), an outlet of the second water pump (631) communicates with an inlet (634a) of the second three-way valve (634), a first outlet (634b) and a second outlet (634c) of the second three-way valve (634) are respectively communicated with an engine coolant inlet (620c) of the first plate heat exchanger (620) and an inlet of the indoor heater core (633), an engine coolant outlet (620d) of the first plate heat exchanger (620) and an outlet of the indoor warm air core (633) are both communicated with a coolant inlet of the engine (632), the coolant outlet of the engine (632) communicates with the inlet of the second water pump (631).

14. The automotive thermal management system of claim 1, wherein a sixth switching valve (608) is disposed in the first flow branch, and a second expansion valve (607) is disposed in the first throttle branch.

15. The automotive thermal management system of claim 1, further comprising a first expansion switch valve (603), wherein an inlet of the first expansion switch valve (603) is communicated with an outlet of the indoor condenser (601), an outlet of the first expansion switch valve (603) is communicated with an inlet of the outdoor heat exchanger (605), the first throttling branch is a throttling flow passage of the first expansion switch valve (603), and the first through-flow branch is a through-flow passage of the first expansion switch valve (603).

16. The automotive thermal management system of claim 1, wherein a seventh switching valve (610) is disposed in the second bypass branch, and a third expansion valve (609) is disposed in the second throttle branch.

17. The automotive thermal management system of claim 16, applied to an electric automobile, further comprising an electric motor cooling system;

the heat pump air conditioning system further includes: a second plate heat exchanger (612), wherein the second plate heat exchanger (612) is arranged in the second flow branch and the second plate heat exchanger (612) is simultaneously arranged in the motor cooling system.

18. The automotive thermal management system of claim 17, characterized in that a refrigerant inlet (612a) of the second plate heat exchanger (612) communicates with an outlet of the outdoor heat exchanger (605), and a refrigerant outlet (612b) of the second plate heat exchanger (612) communicates with an inlet of the seventh switching valve (610).

19. The automotive thermal management system of claim 17 or 18, characterized in that the electric motor cooling system comprises an electric motor connected in series with the second plate heat exchanger (612) to form a circuit, an electric motor radiator (613) and a third water pump (614).

20. The automotive thermal management system of claim 1, further comprising a second expansion switch valve (606), an inlet of the second expansion switch valve (606) being in communication with an outlet of the outdoor heat exchanger (605), an outlet of the second expansion switch valve (606) being in communication with a first end of the first branch (641) and with a first end of the second branch (642), the second throttling branch being a throttling flow passage of the second expansion switch valve (606), the second through-flow branch being a through-flow passage of the second expansion switch valve (606).

21. The automotive thermal management system of claim 20, applied to an electric automobile, further comprising an electric motor cooling system;

the heat pump air conditioning system further includes: a second plate heat exchanger (612), wherein a refrigerant inlet (612a) of the second plate heat exchanger (612) communicates with an outlet of the second expansion switch valve (606), a refrigerant outlet (612b) of the second plate heat exchanger (612) communicates with a first end of the first branch (641) and with a first end of the second branch (642), and the second plate heat exchanger (612) is provided in the motor cooling system at the same time.

22. The automotive thermal management system of claim 21, wherein the electric machine coolant system comprises an electric machine coolant trunk (616), a first electric machine coolant branch (617), and a second electric machine coolant branch (618), a first end of the motor coolant trunk (616) selectively communicates with a first end of the first motor coolant branch (617) or a first end of the second motor coolant branch (618), a second end of the first motor coolant branch (617) and a second end of the second motor coolant branch (618) communicate with a second end of the motor coolant trunk (616), wherein a motor, a motor radiator (613) and a third water pump (614) are connected in series on the motor cooling liquid main line (616), the second plate heat exchanger (612) is connected in series with the first motor cooling liquid branch (617).

23. The automotive thermal management system of claim 1, further comprising a gas-liquid separator (611), an outlet of the gas-liquid separator (611) communicating with an inlet of the compressor (604), an inlet of the gas-liquid separator (611) communicating with an outlet of the indoor evaporator (602), a second end of the first branch (641) communicating with an inlet of the gas-liquid separator (611), and a refrigerant outlet (620b) of the first plate heat exchanger (620) communicating with an inlet of the gas-liquid separator (611) via the battery cooling return branch (622).

24. The automotive thermal management system of claim 1, further comprising a PTC heater (619), the PTC heater (619) being configured to heat air flowing through the indoor condenser (601).

25. The automotive thermal management system of claim 24, wherein the PTC heater (619) is disposed on a windward side or a leeward side of the indoor condenser.

26. An electric vehicle comprising a vehicle thermal management system according to any of claims 1-25.