CN108116186B

CN108116186B - Automobile heat management system and electric automobile

Info

Publication number: CN108116186B
Application number: CN201611084563.9A
Authority: CN
Inventors: 李珍; 杨志芳
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2016-11-30
Filing date: 2016-11-30
Publication date: 2020-01-03
Anticipated expiration: 2036-11-30
Also published as: CN108116186A

Abstract

The utility model relates to a car thermal management system and electric automobile, this car thermal management system include heat pump air conditioning system and on-vehicle refrigerator system, and heat pump air conditioning system includes air condition compressor, air conditioner indoor condenser, air conditioner indoor evaporator and air conditioner outdoor heat exchanger, and the export of air conditioner indoor condenser still communicates through the entry of second expansion valve with the refrigerator evaporator, and the export of refrigerator evaporator still communicates with the entry of air conditioner indoor evaporator or air condition compressor's entry. Therefore, under the bypass refrigeration mode of the bypass heating refrigerator, the refrigerator evaporator can replace an outdoor heat exchanger of an air conditioner, the waste heat generated by refrigeration of the refrigerator is utilized to heat the refrigerant of the air conditioning system, and refrigeration and heating of the air conditioner are simultaneously realized on the basis of saving energy consumption.

Description

Automobile heat management system and electric automobile

Technical Field

The disclosure relates to the field of vehicle-mounted refrigerators of electric automobiles, in particular to an automobile thermal management system and an electric automobile.

Background

The vehicle-mounted refrigerator is a refrigerated cabinet carried on an automobile and is a new generation of refrigeration appliance popular in the international market. In the related technology, when the vehicle-mounted refrigerator is refrigerated by adopting the independent micro compressor, the refrigeration power is small, and the refrigeration speed is low. When a traditional air conditioning system is adopted to refrigerate a vehicle-mounted refrigerator, as a refrigeration core component is a mechanical compressor, the power system output of the whole vehicle is lost when the refrigerator is rapidly refrigerated, and the driving experience of a user is influenced; in addition, if the air conditioning system of the whole vehicle is not started, the air conditioning system is started only due to refrigeration of the vehicle-mounted refrigerator, energy consumption waste of the whole vehicle can be caused, and noise is high.

Disclosure of Invention

In order to solve the problems in the prior art, according to a first aspect of the present disclosure, there is provided an automotive thermal management system including a heat pump air conditioning system and an on-board refrigerator system, the heat pump air conditioning system including an air conditioning indoor condenser, an air conditioning indoor evaporator, an air conditioning compressor, and an air conditioning outdoor heat exchanger, an outlet of the air conditioning compressor being communicated with an inlet of the air conditioning indoor condenser, an outlet of the air conditioning indoor condenser being selectively communicated with an inlet of the air conditioning outdoor heat exchanger via a first throttling branch or a first through-flow branch, an outlet of the air conditioning outdoor heat exchanger being selectively communicated with an inlet of the air conditioning compressor via a second through-flow branch or with an inlet of the air conditioning indoor evaporator via a second throttling branch, an outlet of the air conditioning indoor evaporator being communicated with an inlet of the air conditioning compressor, the vehicle-mounted refrigerator system comprises a refrigerator compressor, a refrigerator condenser, a first expansion valve and a refrigerator evaporator, wherein an outlet of the refrigerator compressor is communicated with an inlet of the refrigerator condenser, an outlet of the refrigerator condenser is communicated with an inlet of the refrigerator evaporator through the first expansion valve, an outlet of the refrigerator evaporator is communicated with an inlet of the refrigerator compressor, an outlet of the condenser in the air-conditioning chamber is also communicated with an inlet of the refrigerator evaporator through a second expansion valve, and an outlet of the refrigerator evaporator is also communicated with an inlet of the evaporator in the air-conditioning chamber or an inlet of the air-conditioning compressor; or the outlet ends of the first throttling branch and the first through flow branch are also communicated with the inlet of the refrigerator evaporator, and the outlet of the refrigerator evaporator is also communicated with the inlet of the indoor evaporator of the air conditioner or the inlet of the air conditioner compressor.

Optionally, a third expansion valve is disposed on the first throttle branch, and a first switch valve is disposed on the first through-flow branch.

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

Optionally, a fourth expansion valve is disposed in the second throttling branch, and a second switch valve is disposed in the second bypass branch.

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

Optionally, the heat pump air conditioning system further comprises a gas-liquid separator, an outlet of the air conditioner indoor evaporator is communicated with an inlet of the gas-liquid separator, and an outlet of the gas-liquid separator is communicated with an inlet of the air conditioner compressor.

Optionally, the automobile thermal management system further comprises a third switch valve and a fourth switch valve, the outlet of the refrigerator evaporator is communicated with the inlet of the air-conditioning indoor evaporator or the inlet of the air-conditioning compressor through the third switch valve, and the outlet of the refrigerator evaporator is communicated with the inlet of the refrigerator compressor through the fourth switch valve

Optionally, the automobile thermal management system further comprises a second one-way valve, and an outlet of the refrigerator evaporator is communicated with an inlet of the air-conditioning indoor evaporator or an inlet of the air-conditioning compressor sequentially through the third switch valve and the second one-way valve.

Optionally, the automobile thermal management system further comprises a third one-way valve and a fourth one-way valve, an outlet of the condenser in the air conditioner chamber is communicated with an inlet of the refrigerator evaporator through the second expansion valve and the third one-way valve in sequence, and the first expansion valve is communicated with an inlet of the refrigerator evaporator through the fourth one-way valve.

Optionally, the automobile thermal management system further includes a fifth switch valve and a sixth switch valve, outlet ends of the first throttle branch and the first through-flow branch are communicated with an inlet of the air-conditioning outdoor heat exchanger through the fifth switch valve, and outlet ends of the first throttle branch and the first through-flow branch are communicated with an inlet of the refrigerator evaporator through the sixth switch valve.

Optionally, the automobile thermal management system further includes a fourth check valve and a fifth check valve, the first expansion valve is communicated with the inlet of the refrigerator evaporator through the fourth check valve, and outlet ends of the first throttling branch and the second flow branch are communicated with the inlet of the refrigerator evaporator through the sixth switching valve and the fifth check valve in sequence.

Optionally, the automobile thermal management system further comprises a first flow valve and a second flow valve, outlet ends of the first throttling branch and the first through-flow branch are communicated with an inlet of the air-conditioning outdoor heat exchanger through the first flow valve, and outlet ends of the first throttling branch and the first through-flow branch are communicated with an inlet of the refrigerator evaporator through the second flow valve.

Optionally, the automobile thermal management system further includes a fourth check valve and a sixth check valve, the first expansion valve is communicated with the inlet of the refrigerator evaporator through the fourth check valve, and outlet ends of the first throttling branch and the second flow branch are communicated with the inlet of the refrigerator evaporator through the second flow valve and the sixth check valve in sequence.

According to a second aspect of the present disclosure, there is provided an electric vehicle comprising the vehicle thermal management system provided according to the first aspect of the present disclosure.

Through the technical scheme, the vehicle-mounted refrigerator system is added, and the refrigerator evaporator of the vehicle-mounted refrigerator system is connected in series on a refrigerator refrigeration bypass formed between the air conditioner indoor condenser and the air conditioner indoor evaporator. Therefore, in the bypass refrigeration mode of the air-conditioning bypass heating refrigerator, the refrigerator evaporator can replace an air-conditioning outdoor heat exchanger, so that the waste heat generated by refrigeration of the refrigerator is utilized to heat the refrigerant of the air-conditioning system, and the refrigeration of the refrigerator and the heating of the air conditioner are realized simultaneously on the basis of saving energy consumption. In addition, in the present disclosure, the in-vehicle refrigerator system and the air conditioner system operate independently of each other without interfering with each other. In addition, due to the fact that the refrigerator refrigeration bypass is additionally arranged, the refrigerator can be switched to multiple working modes during refrigeration, and the refrigeration requirements of users in different degrees are met.

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

Drawings

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

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

FIG. 2 is a schematic diagram of a heat pump air conditioning system according to another embodiment of the present disclosure;

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

FIG. 4 is a schematic structural diagram of an automotive thermal management system according to one embodiment of the present disclosure;

FIG. 5 is a schematic structural diagram of an automotive thermal management system provided in accordance with another embodiment of the present disclosure;

FIG. 6 is a schematic structural diagram of an automotive thermal management system according to another embodiment of the present disclosure;

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

FIG. 8 is a schematic structural diagram of an automotive thermal management system according to another embodiment of the present disclosure;

FIG. 9 is a schematic structural diagram of an automotive thermal management system according to another embodiment of the present disclosure;

FIG. 10 is a schematic diagram of a top view of an expansion switch valve provided in accordance with a preferred embodiment of the present disclosure;

FIG. 11 is a schematic cross-sectional view taken along line AB-AB of FIG. 10, wherein both the first and second ports are in an open state;

fig. 12 is a front structural view in one view of an expansion switching valve provided in a preferred embodiment of the present disclosure;

FIG. 13 is a schematic cross-sectional view taken along line AB-AB of FIG. 10, with the first port in an open state and the second port in a closed state;

FIG. 14 is a schematic cross-sectional view taken along line AB-AB of FIG. 10, with the first port in a closed position and the second port in an open position;

fig. 15 is a front structural view of an expansion switching valve provided in a preferred embodiment of the present disclosure from another perspective;

FIG. 16 is a schematic cross-sectional view taken along line AC-AC of FIG. 15, wherein the first port is in an open state and the second port is in a closed state;

fig. 17 is a first internal structural view of an expansion switching valve provided in accordance with a preferred embodiment of the present disclosure, in which both the first port and the second port are in an open state;

fig. 18 is a partially enlarged view of a portion a in fig. 17;

fig. 19 is a second internal structural view of the expansion switching valve provided in accordance with the preferred embodiment of the present disclosure, wherein the first port is in an open state and the second port is in a closed state;

fig. 20 is a third internal structural view of the expansion switch valve provided in the preferred embodiment of the present disclosure, 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 specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.

In the present disclosure, unless otherwise specified, the use of directional terms such as "upper, lower, left, and right" generally refers to the directions of the drawing of the drawings, "upstream, and downstream" refer to the directions of flow of media, such as refrigerant, specifically, the direction of flow of refrigerant is downstream and the direction of flow of refrigerant away therefrom is upstream, and "inner and outer" refer to the inner and outer of the respective component profiles.

In the invention, the electric vehicle can comprise a pure electric vehicle, a hybrid electric vehicle and a fuel cell vehicle.

Fig. 1 is a schematic configuration diagram of a heat pump air conditioning system according to an embodiment of the present invention. As shown in fig. 1, the system may include: an HVAC (Heating Ventilation and Air Conditioning) assembly 600 and a damper mechanism (not shown), wherein the damper mechanism can be used to open a duct leading to an Air Conditioning indoor evaporator 602 and an Air Conditioning indoor condenser 601, or to open a duct leading to an Air Conditioning indoor evaporator 602. In addition, the system includes an air conditioning compressor 604 and an air conditioning outdoor heat exchanger 605. The HVAC assembly 600 may include, among other things, an air conditioning indoor condenser 601 and an air conditioning indoor evaporator 602. An outlet of the air conditioner compressor 604 is communicated with an inlet of the air conditioner indoor condenser 601, an outlet of the air conditioner indoor condenser 601 is selectively communicated with an inlet of the air conditioner outdoor heat exchanger 605 via a first throttling branch or a first through-flow branch, an outlet of the air conditioner outdoor heat exchanger 605 is selectively communicated with an inlet of the air conditioner indoor evaporator 602 via a second throttling branch or communicated with an inlet of the air conditioner compressor 604 via a second through-flow branch, and an outlet of the air conditioner indoor evaporator 602 is communicated with an inlet of the air conditioner compressor 604.

In the present invention, the outlet of the air conditioning indoor condenser 601 communicates with the inlet of the air conditioning outdoor heat exchanger 605 via either the first throttling branch or the first through-flow branch. This communication may be accomplished in a number of ways. For example, in one embodiment, as shown in fig. 1, 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 air conditioner indoor condenser 601, an outlet of the first expansion switch valve 603 is communicated with an inlet of the air conditioner 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 first on-off valve 608 and a third expansion valve 607, wherein the first through-flow branch is provided with the first on-off valve 608, and the first throttle branch is provided with the third expansion valve 607. Specifically, as shown in fig. 2, the outlet of the air conditioning indoor condenser 601 communicates with the inlet of the air conditioning outdoor heat exchanger 605 via the first switching valve 608 to form a first through-flow branch, and the outlet of the air conditioning indoor condenser 601 communicates with the inlet of the air conditioning outdoor heat exchanger 605 via the third expansion valve 607 to form a first throttle branch. In the air-conditioning cooling mode, the first switching valve 608 is turned on, the third expansion valve 607 is closed, and the outlet of the air-conditioning indoor condenser 601 communicates with the inlet of the air-conditioning outdoor heat exchanger 605 via the first through-flow branch. In the air-conditioning heating mode, the third expansion valve 607 is on, the first switching valve 608 is closed, and the outlet of the air-conditioning indoor condenser 601 communicates with the inlet of the air-conditioning outdoor heat exchanger 605 via the first throttle 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. 1, a second on-off valve 610 is disposed on the second flow branch, and a fourth expansion valve 609 is disposed on the second throttling branch. Specifically, as shown in fig. 3, the outlet of the air-conditioning outdoor heat exchanger 605 communicates with the inlet of the air-conditioning compressor 604 via the second switching valve 610 to form a second flow branch, and the outlet of the air-conditioning outdoor heat exchanger 605 communicates with the inlet of the air-conditioning indoor evaporator 602 via the fourth expansion valve 609 to form a second throttle branch. In the air-conditioning cooling mode, the fourth expansion valve 609 is opened, the second switching valve 610 is closed, and the outlet of the air-conditioning outdoor heat exchanger 605 communicates with the inlet of the air-conditioning indoor evaporator 602 via the second throttling branch. In the air-conditioning heating mode, the second switching valve 610 is turned on, the fourth expansion valve 609 is closed, and the outlet of the air-conditioning outdoor heat exchanger 605 communicates with the inlet of the air-conditioning compressor 604 via the second flow branch.

Fig. 3 shows a schematic configuration diagram of a heat pump air conditioning system according to another embodiment of the present invention. As shown in fig. 3, the heat pump air conditioning system may further include a gas-liquid separator 611 and a first check valve 615, wherein an outlet of the air-conditioning indoor evaporator 602 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 air-conditioning compressor 604. In this way, the refrigerant flowing out of the air conditioner indoor evaporator 602 may first pass through the gas-liquid separator 611 to undergo gas-liquid separation, and the separated gas may then flow back into the air conditioner compressor 604, so as to prevent the liquid refrigerant from entering the air conditioner compressor 604 and damaging the air conditioner compressor 604, thereby prolonging the service life of the air conditioner compressor 604 and improving the efficiency of the whole heat pump air conditioning system. An outlet of the air conditioner indoor evaporator 602 communicates with an inlet of the gas-liquid separator 611 through a first check valve 615. Here, the first check valve 615 is provided to prevent a refrigerant from flowing back to the air conditioning indoor evaporator 602 in an air conditioning heating mode (described in detail below), affecting a heating effect.

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

Herein, as shown in fig. 4 to 9, the present disclosure also provides an in-vehicle refrigerator system, which may include a refrigerator compressor 620, a refrigerator condenser 621, a first expansion valve 622, and a refrigerator evaporator 623, an outlet of the refrigerator compressor 620 communicating with an inlet of the refrigerator condenser 621, an outlet of the refrigerator condenser 621 communicating with an inlet of the refrigerator evaporator 623 through the first expansion valve 622, and an outlet of the refrigerator evaporator 623 communicating with an inlet of the refrigerator compressor 620.

As is well known to those skilled in the art, an on-board refrigerator cold storage/freezer is generally made of a heat conductive material (e.g., aluminum), and the outer surface of the on-board refrigerator cold storage/freezer is generally covered with the refrigerator evaporator, and a low-temperature and low-pressure refrigerant enters the refrigerator evaporator to evaporate to exchange heat with the refrigerator cold storage/freezer to reduce the temperature inside the refrigerator cold storage/freezer, thereby performing a cold storage/freezing function.

Fig. 4 is a schematic structural diagram of an automotive thermal management system provided according to a first embodiment of the present disclosure. As shown in FIG. 4, the thermal management system of the vehicle may include the heat pump air conditioning system and the on-board refrigeration system described above. Wherein the outlet of the condenser 601 is also communicated with the inlet of the refrigerator evaporator 623 via the second expansion valve 624, and the outlet of the refrigerator evaporator 623 is also communicated with the inlet of the evaporator 602. That is, as shown in fig. 4, the condenser 601 in the air-conditioning compartment has a first outlet 601a and a second outlet 601 b. Wherein, the first outlet 601a of the air conditioner indoor condenser 601 is selectively communicated with the inlet of the air conditioner outdoor heat exchanger 605 via the first throttling branch or the first through-flow branch. The second outlet 601b of the air conditioner interior condenser 601 communicates with the inlet of the refrigerator evaporator 623 via the second expansion valve 624.

Here, the hvac room condenser 601 may have two outlets, or may have two outlets expanded by connecting a three-way valve to the outlet of the hvac room condenser 601, and both cases fall within the scope of the present disclosure.

That is, as a main inventive concept in the first embodiment of the present disclosure, a vehicle-mounted refrigerator system is added, and a refrigerator evaporator of the vehicle-mounted refrigerator system is connected in series to a refrigerator cooling bypass formed between an air-conditioning indoor condenser and an air-conditioning indoor evaporator. In the first embodiment of the thermal management system for the automobile, the refrigerator cooling bypass includes a refrigerant bypass branch for refrigerator cooling, which is composed of the second expansion valve 624 and the refrigerator evaporator 623 together.

In order to prevent the refrigerant of low temperature and low pressure from flowing to the air conditioning indoor evaporator 602 in the cooling mode of the refrigerator system, as shown in fig. 4, the thermal management system of the vehicle further includes a third switching valve 625, and the third switching valve 625 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning indoor evaporator 602.

In order to prevent the refrigerant of low temperature and low pressure from flowing back to the refrigerator evaporator 623 in the air conditioner refrigeration refrigerator bypass cooling mode, as shown in fig. 4, the thermal management system of the vehicle further includes a second check valve 626, and the second check valve 626 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioner vehicle interior evaporator 602. That is, the second check valve 626 permits the refrigerant to flow from the outlet of the refrigerator evaporator 623 to the inlet of the interior evaporator 602 of the air-conditioned vehicle only in one direction, and does not permit the refrigerant to flow in the opposite direction.

As another alternative embodiment, as shown in fig. 5, in a second embodiment provided by the present disclosure, the vehicle thermal management system may also include the heat pump air conditioning system and the on-board refrigerator system described above. Here, the outlet of the condenser 601 in the air-conditioning room is also communicated with the inlet of the refrigerator evaporator 623 via the second expansion valve 624, and the outlet of the refrigerator evaporator 623 is also communicated with the inlet of the air-conditioning compressor 604.

That is, as shown in fig. 4 and 5, the first and second embodiments described above differ only in the connection manner of the outlet of the refrigerator evaporator 623. Specifically, in the first embodiment, as shown in fig. 4, the outlet of the refrigerator evaporator 623 communicates with the inlet of the air conditioning indoor evaporator 602. In the second embodiment, as shown in fig. 5, the outlet of the refrigerator evaporator 623 communicates with the air conditioner compressor 604 bypassing the air conditioner indoor evaporator 602.

Similar to the implementation of the first embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing to the air conditioner indoor evaporator 602 in the cooling mode of the refrigerator system, as shown in fig. 5, the thermal management system of the automobile further includes a third on/off valve 625, and the third on/off valve 625 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioner compressor 604.

Similar to the implementation of the first embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing back to the refrigerator evaporator 623 in the air conditioning refrigeration refrigerator bypass cooling mode, as shown in fig. 5, the thermal management system of the automobile further includes a second check valve 626, and the second check valve 626 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning compressor 604. That is, the second check valve 626 permits the refrigerant to flow from the outlet of the refrigerator evaporator 623 to the inlet of the air conditioner compressor 604 only in one direction, but not in the opposite direction.

In order to prevent the refrigerant of low temperature and low pressure flowing out of the outlet of the first expansion valve 622 from flowing to the air conditioner indoor condenser 601 in the refrigerator extreme speed cooling mode, as shown in fig. 4 and 5, the thermal management system of the automobile further includes a third check valve 627, and the third check valve 627 is disposed between the outlet of the second expansion valve 624 and the inlet of the refrigerator evaporator 623. That is, the first check valve 626 permits the refrigerant to flow from the outlet of the air conditioner interior condenser 601 to the inlet of the refrigerator evaporator 623 only in one direction, but not in the opposite direction.

In order to prevent the low-temperature and low-pressure refrigerant from flowing to the refrigerator compressor 620 in the air-conditioning bypass heating refrigerator bypass cooling mode, as shown in fig. 4 and 5, the in-vehicle refrigerator system further includes a fourth switching valve 634, and the fourth switching valve 634 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the refrigerator compressor 620.

In order to prevent the low-temperature and low-pressure refrigerant from flowing to the refrigerator condenser 621 in the air conditioner bypass heating refrigerator bypass cooling mode, as shown in fig. 4 and 5, the in-vehicle refrigerator system further includes a fourth check valve 635, and the fourth check valve 635 is disposed between the outlet of the first expansion valve 622 and the inlet of the refrigerator evaporator 623. That is, the fourth check valve 635 allows the refrigerant to flow from the outlet of the first expansion valve 622 to the inlet of the refrigerator evaporator 623 only in one direction, but not in the opposite direction.

The cycle process, principle and control strategy of the thermal management system of the vehicle in different operation modes according to the first embodiment of the present disclosure will be described in detail below by taking fig. 4 as an example. It should be understood that the system loop process, the principle and the control strategy in other embodiments (for example, the embodiment shown in fig. 5) are similar to those in fig. 4, and thus the description thereof is omitted.

The first mode is as follows: and (4) an air-conditioning refrigeration mode.

As shown in fig. 4, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601. At this time, the air is controlled by the damper mechanism so as not to pass through the air-conditioning indoor condenser 601, and since no air passes through the air-conditioning indoor condenser 601, heat exchange does not occur in the air-conditioning indoor condenser 601, the air-conditioning indoor condenser 601 is used only as a flow path, and the outlet of the air-conditioning indoor condenser 601 is still high-temperature and high-pressure gas. The first outlet 601a of the condenser 601 is connected to the inlet of the first on-off valve 608, and the outlet of the first on-off valve 608 is still high-temperature and high-pressure gas. The outlet of the first switch valve 608 is connected with an air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the air-conditioning outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the air-conditioning outdoor heat exchanger 605 is connected with the fourth expansion valve 609, and the temperature is reduced by throttling through the fourth expansion valve 609, and the outlet of the fourth expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the fourth expansion valve 609 may be given a certain opening degree according to actual demand, and the opening degree may be adjusted by calculating a superheat degree of refrigerant at an outlet of the indoor evaporator of the air conditioner based on pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 of the air conditioner and an inlet of the gas-liquid separator 611. The outlet of the fourth expansion valve 609 is connected to the inlet of the air-conditioning indoor evaporator 602, and the low-temperature and low-pressure liquid evaporates in the air-conditioning indoor evaporator 602, so that the outlet of the air-conditioning indoor evaporator 602 is low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the air conditioning indoor evaporator 602, and the air conditioning indoor condenser 601 flows only as a refrigerant flow path without passing through the air conditioning indoor evaporator. The second expansion valve 624 is closed, the first expansion valve 622 is closed, the third switching valve 625 is closed, the fourth switching valve 634 is closed, the third expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, the fourth expansion valve 609 is opened, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a second mode: a refrigeration mode of the refrigerator system.

As shown in fig. 4, first, high-temperature and high-pressure gas is compressed and discharged from the refrigerator compressor 620, and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. The outlet of the first expansion valve 622 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, thereby realizing refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the refrigerator compressor 620 through the fourth switching valve 634. Finally, the low-temperature and low-pressure gas is returned to the refrigerator compressor 620, thereby forming a cycle. The fourth switching valve 634 is opened, the first expansion valve 622 is opened, the second expansion valve 624 is closed, the first switching valve 608 is closed, the third switching valve 625 is closed, the third expansion valve 607 is closed, the second switching valve 610 is closed, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is operated, and the air conditioner compressor 604 is not operated.

And a third mode: and the air conditioner bypass heating refrigerator bypass refrigeration mode.

As shown in fig. 4, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The second outlet 601b of the condenser 601 is connected to the inlet of the second expansion valve 624, and the outlet is low-temperature and low-pressure liquid after being throttled and cooled by the second expansion valve 624. The outlet of the second expansion valve 624 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so as to realize refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the air conditioner indoor evaporator 602 through a third switching valve 625. The air is controlled by the damper mechanism to flow to the air conditioner indoor condenser 601 and the air conditioner indoor evaporator 602 at the same time, and the outlet of the air conditioner indoor evaporator 602 is still low-temperature and low-pressure air. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The second expansion valve 624 is opened, the first expansion valve 622 is closed, the third switching valve 625 is opened, the fourth switching valve 634 is closed, the third expansion valve 607 is closed, the first switching valve 608 is closed, the second switching valve 610 is closed, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a fourth mode: and (4) a bypass refrigeration mode of the air-conditioning refrigeration refrigerator.

As shown in fig. 4, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the condenser 601 in the air-conditioning chamber is connected to the inlet of the first switching valve 608, and the second outlet 601b thereof is connected to the second expansion valve 624, and at this time, the medium-temperature and high-pressure liquid flowing out of the outlet of the condenser 601 in the air-conditioning chamber is divided into two streams: the larger flow will flow to the inlet of the first switch valve 608, while the outlet of the first switch valve 608 is still medium temperature and high pressure liquid. The outlet of the first switch valve 608 is connected with the inlet of the air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature high-pressure liquid. The outlet of the air-conditioning outdoor heat exchanger 605 is connected with the fourth expansion valve 609, and is throttled and cooled by the fourth expansion valve 609, and the outlet of the fourth expansion valve 609 is low-temperature and low-pressure liquid; the other flow with smaller flow rate flows to the second expansion valve 624, and is throttled and cooled by the second expansion valve 624, and the outlet of the second expansion valve is low-temperature and low-pressure liquid. The outlet of the second expansion valve 624 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so as to realize refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. An outlet of the refrigerator evaporator 623 is connected to a third switching valve 625. The refrigerant flowing out of the outlet of the fourth expansion valve 609 is merged with the refrigerant flowing out of the outlet of the third switching valve 625, and flows into the air-conditioning indoor evaporator 602. The low-temperature and low-pressure gas-liquid mixture (in which the liquid occupies the most part) evaporates in the air-conditioned indoor evaporator 602, so that the outlet of the air-conditioned indoor evaporator 602 is low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor evaporator 602 and the air conditioning indoor condenser 601. The second expansion valve 624 is opened, the first expansion valve 622 is closed, the third switching valve 625 is opened, the fourth switching valve 634 is closed, the third expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, the fourth expansion valve 609 is opened, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a fifth mode: and a refrigerator top-speed refrigerating mode.

As shown in fig. 4, the refrigerator compressor 620 and the air conditioner compressor 604 are operated simultaneously. On the one hand, the high-temperature and high-pressure gas is discharged from the refrigerator compressor 620 through compression and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is the medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. Meanwhile, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The second outlet 601b of the condenser 601 is connected to the inlet of the second expansion valve 624, and the outlet is low-temperature and low-pressure liquid after being throttled and cooled by the second expansion valve 624. The refrigerant flowing out of the outlet of the first expansion valve 622 and the refrigerant flowing out of the outlet of the second expansion valve 624 are merged and flow to the inlet of the refrigerator evaporator 623, and then exchange heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so that refrigeration of the refrigerator is realized, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The low-temperature and low-pressure gas flowing out of the outlet of the refrigerator evaporator 623 is divided into two: the larger flow rate flows to the inlet of the third on/off valve 625, and the outlet of the third on/off valve 625 is connected to the inlet of the air conditioner indoor evaporator 602. The air flow direction is controlled by the damper mechanism to simultaneously flow through the air conditioner indoor condenser 601 and the air conditioner indoor evaporator 602, and the outlet of the air conditioner indoor evaporator 602 is low-temperature and low-pressure air. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. The other flow of the smaller flow rate flows to the inlet of the fourth switching valve 634, and the outlet of the fourth switching valve 634 is connected to the inlet of the refrigerator compressor 620. Finally, the low-temperature and low-pressure gas is returned to the refrigerator compressor 620, thereby forming another cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor evaporator 602 and the air conditioning indoor condenser 601. The second expansion valve 624 is opened, the first expansion valve 622 is opened, the third switching valve 625 is opened, the fourth switching valve 634 is opened, the third expansion valve 607 is closed, the first switching valve 608 is closed, the second switching valve 610 is closed, and the fourth expansion valve 609 is closed.

Mode six: and a top-speed refrigerating mode of the air-conditioning and refrigerating refrigerator.

As shown in fig. 4, the refrigerator compressor 620 and the air conditioner compressor 604 are operated simultaneously. On the one hand, the high-temperature and high-pressure gas is discharged from the refrigerator compressor 620 through compression and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is the medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. Meanwhile, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the condenser 601 in the air-conditioning chamber is connected to the inlet of the first switching valve 608, and the second outlet 601b thereof is connected to the second expansion valve 624, and at this time, the medium-temperature and high-pressure liquid flowing out of the outlet of the condenser 601 in the air-conditioning chamber is divided into two streams: the larger flow will flow to the inlet of the first switch valve 608, while the outlet of the first switch valve 608 is still medium temperature and high pressure liquid. The outlet of the first switch valve 608 is connected to the inlet of the air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature high-pressure liquid. The outlet of the air-conditioning outdoor heat exchanger 605 is connected with the fourth expansion valve 609, and is throttled and cooled by the fourth expansion valve 609, and the outlet of the fourth expansion valve 609 is low-temperature and low-pressure liquid; the other flow with smaller flow rate flows to the second expansion valve 624, and is throttled and cooled by the second expansion valve 624, and the outlet of the second expansion valve is low-temperature and low-pressure liquid. The refrigerant flowing out of the outlet of the first expansion valve 622 and the refrigerant flowing out of the outlet of the second expansion valve 624 are merged and flow to the inlet of the refrigerator evaporator 623, and then exchange heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so that refrigeration of the refrigerator is realized, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The low-temperature and low-pressure gas flowing out of the outlet of the refrigerator evaporator 623 is divided into two: the other flow of the smaller flow rate flows to the inlet of the fourth switching valve 634, and the outlet of the fourth switching valve 634 is connected to the inlet of the refrigerator compressor 620. Finally, the low-temperature and low-pressure gas returns to the refrigerator compressor 620, thereby forming a cycle; the other flow having a larger flow rate flows to the inlet of the third switching valve 625. The refrigerant flowing out of the outlet of the fourth expansion valve 609 is merged with the refrigerant flowing out of the outlet of the third switching valve 625, and flows into the air-conditioning indoor evaporator 602. The low-temperature and low-pressure gas-liquid mixture (in which the liquid occupies the most part) evaporates in the air-conditioned indoor evaporator 602, so that the outlet of the air-conditioned indoor evaporator 602 is low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming another circulation. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor evaporator 602 and the air conditioning indoor condenser 601. The second expansion valve 624 is opened, the first expansion valve 622 is opened, the third switching valve 625 is opened, the fourth switching valve 634 is opened, the third expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, and the fourth expansion valve 609 is opened.

Mode seven: and (4) an air conditioning heating mode.

As shown in fig. 4, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the condenser 601 in the air-conditioning chamber is connected to the inlet of the third expansion valve 607, and is throttled and cooled by the third expansion valve 607, and the outlet thereof is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to the air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected to the inlet of the gas-liquid separator 611 through the second switching valve 610. The refrigerant directly enters the gas-liquid separator 611 without passing through the indoor evaporator 602 of the air conditioner, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas returns to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The second expansion valve 624 is closed, the first expansion valve 622 is closed, the third switching valve 625 is closed, the fourth switching valve 634 is closed, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a mode eight: and the air conditioner is in a bypass refrigeration mode of the refrigerator.

As shown in fig. 4, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The medium-temperature and high-pressure liquid flowing out from the outlet of the condenser 601 in the air conditioner room is divided into two parts: the higher flow rate of the refrigerant flows from the first outlet 601a of the condenser 601 in the air conditioner room to the inlet of the third expansion valve 607, and the refrigerant is throttled and cooled by the third expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to the air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected to the inlet of the second switching valve 610. The other flow with a smaller flow rate flows from the second outlet 601b of the condenser 601 in the air-conditioning room to the inlet of the second expansion valve 624, and is throttled and cooled by the second expansion valve 624, and the outlet is low-temperature and low-pressure liquid. The outlet of the second expansion valve 624 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so as to realize refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the air conditioner indoor evaporator 602 through a third switching valve 625. The refrigerant flowing out of the outlet of the second switching valve 610 and the refrigerant flowing out of the outlet of the air conditioner indoor evaporator 602 are joined and flow to the inlet of the gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The second expansion valve 624 is opened, the first expansion valve 622 is closed, the third switching valve 625 is opened, the fourth switching valve 634 is closed, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

The mode nine: and a super-speed refrigerating mode of the air conditioner super-speed heating refrigerator.

As shown in fig. 4, the refrigerator compressor 620 and the air conditioner compressor 604 are operated simultaneously. On the one hand, the high-temperature and high-pressure gas is discharged from the refrigerator compressor 620 through compression and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is the medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. Meanwhile, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The medium-temperature and high-pressure liquid flowing out from the outlet of the condenser 601 in the air conditioner room is divided into two parts: the higher flow rate of the refrigerant flows from the first outlet 601a of the condenser 601 in the air conditioner room to the inlet of the third expansion valve 607, and the refrigerant is throttled and cooled by the third expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to the air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected to the inlet of the second switching valve 610. The other flow with a smaller flow rate flows from the second outlet 601b of the condenser 601 in the air-conditioning room to the inlet of the second expansion valve 624, and is throttled and cooled by the second expansion valve 624, and the outlet is low-temperature and low-pressure liquid. The refrigerant flowing out of the outlet of the first expansion valve 622 and the refrigerant flowing out of the outlet of the second expansion valve 624 are merged and flow to the inlet of the refrigerator evaporator 623, and then exchange heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, so that refrigeration of the refrigerator is realized, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The low-temperature and low-pressure gas flowing out of the outlet of the refrigerator evaporator 623 is divided into two: the flow of the smaller one flows to the inlet of the fourth switching valve 634, and the outlet of the fourth switching valve 634 is connected to the inlet of the refrigerator compressor 620. Finally, the low-temperature and low-pressure gas returns to the refrigerator compressor 620, thereby forming a cycle; the other side having a larger flow rate flows to the inlet of the air conditioning indoor evaporator 602 through the third switching valve 625. The refrigerant flowing out of the outlet of the air conditioner indoor evaporator 602 and the refrigerant flowing out of the outlet of the second switching valve 610 are joined and flow to the gas-liquid separator 611, the liquid that has not been evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the air conditioner compressor 604, thereby forming another cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The second expansion valve 624 is opened, the first expansion valve 622 is opened, the third switching valve 625 is opened, the fourth switching valve 634 is opened, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is operated, and the air conditioner compressor 604 is operated.

The specific structure of the thermal management system for the vehicle provided according to the first embodiment of the present disclosure, and the cycle process and principle thereof in different operation modes are described above. How to control the heat pump air conditioning system to be in the specific working mode according to the remaining driving energy value (such as the remaining electric quantity value and the remaining oil quantity value) of the whole vehicle will be described below, so as to fully utilize the whole vehicle resources, reduce the energy waste, and meet the refrigeration requirements of the refrigerator of different degrees of the user.

In the thermal management system of the vehicle according to the first embodiment provided by the present disclosure, the air conditioning compressor is a dual-drive compressor, which may further include a control device. The control device can preset an electric quantity threshold value and an oil quantity threshold value. When the vehicle works, the residual electric quantity value and the residual oil quantity value of the whole vehicle can be obtained firstly. For example, the remaining electric quantity value can be obtained from a battery management system through a can bus, and the remaining oil quantity value can be obtained from a vehicle instrument through the can bus. When the obtained residual electric quantity value is larger than the electric quantity threshold value, the control device can control the electric compressor of the double-drive compressor to operate so as to drive the refrigerator cold-making bypass to work.

And when the obtained residual electric quantity value is less than or equal to the electric quantity threshold value and the obtained residual oil quantity value is greater than the residual oil quantity value, the control device can control the mechanical compressor of the double-drive compressor to operate so as to drive the refrigeration bypass of the refrigerator to work.

And when the obtained residual electric quantity value is less than or equal to the electric quantity threshold value and the obtained residual oil quantity value is less than or equal to the residual oil quantity value, the control device can control the double-drive compressor to stop running and control the refrigerator compressor to run so as to drive the vehicle-mounted refrigerator system to work and realize primary refrigeration.

In addition, on the premise that the energy of the whole vehicle is sufficient, whether the heat pump air conditioning system is in a working state or not and specifically in an air conditioning heating mode or an air conditioning cooling mode can be further detected. The above detection purpose may be achieved by an air conditioner controller, for example. When the air conditioner controller detects that the heat pump air conditioning system is in a working state, the control device preferentially utilizes the air conditioner compressor to drive the refrigeration bypass of the refrigerator to work so as to realize secondary refrigeration. Furthermore, when the refrigeration bypass of the refrigerator cannot meet the refrigeration requirement of the refrigerator, the control device can control the air conditioner compressor and the refrigerator compressor to operate simultaneously so as to realize three-stage refrigeration.

More specifically, when the air conditioner controller detects that the heat pump air conditioning system is in the cooling mode, the control device can control the automobile thermal management system to be in the bypass cooling mode (secondary cooling) of the air conditioning and cooling refrigerator or in the top speed cooling mode (tertiary cooling) of the air conditioning and cooling refrigerator.

When the air conditioner controller detects that the heat pump air conditioning system is in a heating mode, the control device can control the automobile heat management system to be in the bypass refrigeration mode (secondary refrigeration) of the air conditioner bypass heating refrigerator, or in the extreme speed refrigeration mode (tertiary refrigeration) of the air conditioner extreme speed heating refrigerator.

In conclusion, when the energy of the whole vehicle is sufficient, the control device preferentially selects the electric compressor of the double-drive compressor to operate so as to drive the refrigeration bypass of the refrigerator to work. Therefore, the rapid refrigeration of the vehicle-mounted refrigerator can be realized, the noise generated by the running of the whole vehicle can be reduced, the environment pollution is prevented, and the cost is saved. When the energy of the whole vehicle is insufficient, the vehicle-mounted refrigerator system is utilized. When the heat pump air conditioning system of the whole vehicle runs, the refrigerator refrigeration bypass is preferentially utilized to realize the refrigerator refrigeration. Therefore, the energy consumption ratio of the heat pump air-conditioning system can be improved to 3, the whole vehicle resources are fully utilized, and the energy consumption ratio is improved. In addition, because the heat pump air conditioning system that this disclosure provided has above-mentioned three refrigeration grades, can satisfy user's refrigeration demand of different degrees.

Fig. 6 is a schematic structural diagram of an automotive thermal management system according to a third embodiment of the present disclosure. As shown in FIG. 6, the thermal management system of the vehicle may include the heat pump air conditioning system and the on-board refrigeration system described above. The outlet ends of the first throttling branch and the first through-flow branch are also communicated with the inlet of the refrigerator evaporator 623, and the outlet of the refrigerator evaporator 623 is also communicated with the inlet of the air-conditioning indoor evaporator 602. That is, as shown in fig. 6, the outlet ends of the first throttle branch and the first through-flow branch each have two outlets, one of which communicates with the inlet of the refrigerator evaporator 623 and the other of which communicates with the inlet of the air conditioner outdoor heat exchanger 605.

That is, as a main inventive concept in the third embodiment of the present disclosure, a vehicle-mounted refrigerator system is added, and a refrigerator evaporator of the vehicle-mounted refrigerator system is connected in series to a refrigerator cooling bypass formed between an air-conditioning indoor condenser and an air-conditioning indoor evaporator. In the third embodiment of the automobile thermal management system, the refrigerator cooling bypass includes a refrigerant bypass branch for refrigerator cooling, which is composed of the first throttling branch and the refrigerator evaporator 623 in common.

In order that the refrigerator refrigeration bypass and the air conditioning system may operate independently of each other, in a third embodiment provided by the present disclosure, as shown in fig. 6, the car thermal management system further includes a fifth switching valve 628 and a sixth switching valve 629, the fifth switching valve 628 is disposed between the outlet ends of the first throttling branch and the first circulating branch and the inlet of the air conditioner outdoor heat exchanger 605, and the sixth switching valve 629 is disposed between the outlet ends of the first throttling branch and the first circulating branch and the inlet of the refrigerator evaporator 623.

Further, in order to prevent the low-temperature and low-pressure refrigerant flowing out of the outlet of the first expansion valve 622 from flowing to the air conditioning indoor condenser 601 in the extreme speed cooling mode of the refrigerator, the thermal management system of the vehicle further includes a fifth check valve 630, and the fifth check valve 630 is disposed between the outlet of the sixth switching valve 629 and the inlet of the refrigerator evaporator 623. That is, the fifth check valve 630 allows the refrigerant to flow from the outlet of the air conditioner interior condenser 601 to the inlet of the refrigerator evaporator 623 only in one direction, but not in the opposite direction.

As another alternative fourth embodiment, as shown in fig. 8, the car thermal management system further includes a first flow valve 631 and a second flow valve 632, wherein the first flow valve 631 is disposed between the outlet ends of the first throttling branch and the first circulating branch and the inlet of the air conditioner outdoor heat exchanger 605, and the second flow valve 632 is disposed between the outlet ends of the first throttling branch and the first circulating branch and the inlet of the refrigerator evaporator 623. In addition, the first flow valve 631 and the second flow valve 632 can also adjust the flow of the branch in which the valves are located.

Further, in order to prevent the low-temperature and low-pressure refrigerant flowing out of the outlet of the first expansion valve 622 from flowing to the air conditioning indoor condenser 601 in the refrigerator extreme speed cooling mode, as shown in fig. 8, the thermal management system of the automobile further includes a sixth check valve 633, and the sixth check valve 633 is disposed between the outlet of the second flow valve 632 and the inlet of the refrigerator evaporator 623. That is, the sixth check valve 633 allows the refrigerant to flow from the outlet of the air conditioner interior condenser 601 to the inlet of the refrigerator evaporator 623 only in one direction, and does not flow in the opposite direction.

In order to prevent the refrigerant of low temperature and low pressure from flowing to the air conditioning interior evaporator 602 in the cooling mode of the refrigerator system, as shown in fig. 6 and 8, the thermal management system of the automobile further includes a third on/off valve 625, and the third on/off valve 625 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning interior evaporator 602.

In order to prevent the refrigerant of low temperature and low pressure from flowing back to the refrigerator evaporator 623 in the air conditioner refrigeration refrigerator bypass cooling mode, as shown in fig. 6 and 8, the thermal management system of the vehicle further includes a second check valve 626, and the second check valve 626 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioner vehicle interior evaporator 602. That is, the second check valve 626 permits the refrigerant to flow from the outlet of the refrigerator evaporator 623 to the inlet of the interior evaporator 602 of the air-conditioned vehicle only in one direction, and does not permit the refrigerant to flow in the opposite direction.

As another alternative embodiment, as shown in fig. 7, in a fifth embodiment provided by the present disclosure, the vehicle thermal management system may also include the heat pump air conditioning system and the on-board refrigerator system described above. Here, the outlet of the condenser 601 in the air-conditioning room is also communicated with the inlet of the refrigerator evaporator 623 via the second expansion valve 624, and the outlet of the refrigerator evaporator 623 is also communicated with the inlet of the air-conditioning compressor 604.

That is, as shown in fig. 6 and 7, the above-described third and fifth embodiments are different only in the connection manner of the outlet of the refrigerator evaporator 623. Specifically, in the third embodiment, as shown in fig. 6, the outlet of the refrigerator evaporator 623 communicates with the inlet of the air conditioning indoor evaporator 602. In the fifth embodiment, as shown in fig. 7, the outlet of the refrigerator evaporator 623 communicates with the air conditioner compressor 604, bypassing the air conditioner indoor evaporator 602.

Similar to the implementation manner of the third embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing to the air conditioning indoor evaporator 602 in the cooling mode of the refrigerator system, as shown in fig. 7, the thermal management system of the automobile further includes a third switching valve 625, and the third switching valve 625 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning compressor 604.

Similar to the implementation manner of the third embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing back to the refrigerator evaporator 623 in the air conditioning refrigeration refrigerator bypass cooling mode, as shown in fig. 7, the thermal management system of the automobile further includes a second check valve 626, and the second check valve 626 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning compressor 604. That is, the second check valve 626 permits the refrigerant to flow from the outlet of the refrigerator evaporator 623 to the inlet of the air conditioner compressor 604 only in one direction, but not in the opposite direction.

As another alternative embodiment, as shown in fig. 9, in a sixth embodiment provided by the present disclosure, the thermal management system of the automobile may also include the heat pump air conditioning system and the on-board refrigerator system described above. Here, the outlet of the condenser 601 in the air-conditioning room is also communicated with the inlet of the refrigerator evaporator 623 via the second expansion valve 624, and the outlet of the refrigerator evaporator 623 is also communicated with the inlet of the air-conditioning compressor 604.

That is, as shown in fig. 8 and 9, the above-described fourth embodiment and sixth embodiment differ only in the connection manner of the outlet of the refrigerator evaporator 623. Specifically, in the fourth embodiment, as shown in fig. 8, the outlet of the refrigerator evaporator 623 communicates with the inlet of the air conditioning indoor evaporator 602. In the sixth embodiment, as shown in fig. 9, the outlet of the refrigerator evaporator 623 communicates with the air conditioner compressor 604 bypassing the air conditioner indoor evaporator 602.

Similar to the implementation of the fourth embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing to the air conditioning indoor evaporator 602 in the cooling mode of the refrigerator system, as shown in fig. 7, the thermal management system of the automobile further includes a third switching valve 625, and the third switching valve 625 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning compressor 604.

Similar to the implementation of the fourth embodiment, in order to prevent the refrigerant of low temperature and low pressure from flowing back to the refrigerator evaporator 623 in the air conditioning refrigeration refrigerator bypass cooling mode, as shown in fig. 7, the thermal management system of the automobile further includes a second check valve 626, and the second check valve 626 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the air conditioning compressor 604. That is, the second check valve 626 permits the refrigerant to flow from the outlet of the refrigerator evaporator 623 to the inlet of the air conditioner compressor 604 only in one direction, but not in the opposite direction.

In order to prevent the low-temperature and low-pressure refrigerant from flowing to the refrigerator compressor 620 in the air-conditioning bypass heating refrigerator bypass cooling mode, as shown in fig. 6 to 9, the in-vehicle refrigerator system further includes a fourth switching valve 634, and the fourth switching valve 634 is disposed between the outlet of the refrigerator evaporator 623 and the inlet of the refrigerator compressor 620.

In order to prevent the low-temperature and low-pressure refrigerant from flowing to the refrigerator condenser 621 in the air conditioner bypass heating refrigerator bypass cooling mode, as shown in fig. 6 to 9, the in-vehicle refrigerator system further includes a fourth check valve 635, and the fourth check valve 635 is disposed between the outlet of the first expansion valve 622 and the inlet of the refrigerator evaporator 623. That is, the fourth check valve 635 allows the refrigerant to flow from the outlet of the first expansion valve 622 to the inlet of the refrigerator evaporator 623 only in one direction, but not in the opposite direction.

The cycle process, principle and control strategy of the thermal management system of the automobile provided by the third embodiment provided by the present disclosure in different operation modes will be described in detail by taking fig. 6 as an example. It should be understood that the system loop process, principle and control strategy in other embodiments (e.g., the embodiments shown in fig. 7 to 9) are similar to those in fig. 6, and thus are not described in detail herein.

The first mode is as follows: and (4) an air-conditioning refrigeration mode.

As shown in fig. 6, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601. At this time, the air is controlled by the damper mechanism so as not to pass through the air-conditioning indoor condenser 601, and since no air passes through the air-conditioning indoor condenser 601, heat exchange does not occur in the air-conditioning indoor condenser 601, the air-conditioning indoor condenser 601 is used only as a flow path, and the outlet of the air-conditioning indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the condenser 601 in the air conditioner room is connected to the inlet of the first on-off valve 608, and the outlet of the first on-off valve 608 is still high-temperature and high-pressure gas. The outlet of the first switch valve 608 is connected with an air-conditioning outdoor heat exchanger 605, the air-conditioning outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the air-conditioning outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the air-conditioning outdoor heat exchanger 605 is connected with the fourth expansion valve 609, and the temperature is reduced by throttling through the fourth expansion valve 609, and the outlet of the fourth expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the fourth expansion valve 609 may be given a certain opening degree according to actual demand, and the opening degree may be adjusted by calculating a superheat degree of refrigerant at an outlet of the indoor evaporator of the air conditioner based on pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 of the air conditioner and an inlet of the gas-liquid separator 611. The outlet of the fourth expansion valve 609 is connected to the inlet of the air-conditioning indoor evaporator 602, and the low-temperature and low-pressure liquid evaporates in the air-conditioning indoor evaporator 602, so that the outlet of the air-conditioning indoor evaporator 602 is low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the air conditioning indoor evaporator 602, and the air conditioning indoor condenser 601 flows only as a refrigerant flow path without passing through the air conditioning indoor evaporator. The first expansion valve 622 is closed, the third switching valve 625 is closed, the fourth switching valve 634 is closed, the third expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, the fourth expansion valve 609 is opened, the fifth switching valve 628 is opened, the sixth switching valve 629 is closed, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a second mode: a refrigeration mode of the refrigerator system.

As shown in fig. 6, first, high-temperature and high-pressure gas is compressed and discharged from the refrigerator compressor 620, and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. The outlet of the first expansion valve 622 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, thereby realizing refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the refrigerator compressor 620 through the fourth switching valve 634. Finally, the low-temperature and low-pressure gas is returned to the refrigerator compressor 620, thereby forming a cycle. The fourth switching valve 634 is opened, the first expansion valve 622 is opened, the first switching valve 608 is closed, the third switching valve 625 is closed, the third expansion valve 607 is closed, the second switching valve 610 is closed, the fourth expansion valve 609 is closed, the fifth switching valve 628 is closed, the sixth switching valve 629 is closed, the refrigerator compressor 620 is operated, and the air conditioner compressor 604 is not operated.

As shown in fig. 6, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the condenser 601 in the air-conditioning room is connected with the inlet of the third expansion valve 607, and the outlet is low-temperature and low-pressure liquid after throttling and cooling by the third expansion valve 607. The outlet of the third expansion valve 607 is connected to the inlet of the refrigerator evaporator 623, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, thereby realizing refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the air conditioner indoor evaporator 602 through a third switching valve 625. The air is controlled by the damper mechanism to flow to the air conditioner indoor condenser 601 and the air conditioner indoor evaporator 602 at the same time, and the outlet of the air conditioner indoor evaporator 602 is still low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The first expansion valve 622 is closed, the third switching valve 625 is opened, the fourth switching valve 634 is closed, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is closed, the fourth expansion valve 609 is closed, the fifth switching valve 628 is closed, the sixth switching valve 629 is opened, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

And a fourth mode: and a refrigerator top-speed refrigerating mode.

As shown in fig. 6, the refrigerator compressor 620 and the air conditioner compressor 604 are operated simultaneously. On the one hand, the high-temperature and high-pressure gas is discharged from the refrigerator compressor 620 through compression and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is the medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. Meanwhile, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the condenser 601 is connected to the inlet of the third expansion valve 607, the temperature of the outlet is reduced by throttling the third expansion valve 607, the outlet is low-temperature and low-pressure liquid, and the outlet of the third expansion valve 607 is connected to the inlet of the sixth switching valve 629. The refrigerant flowing out of the outlet of the first expansion valve 622 and the refrigerant flowing out of the outlet of the sixth switching valve 629 join and flow to the inlet of the refrigerator evaporator 623, and exchange heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, thereby realizing refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The low-temperature and low-pressure gas flowing out of the outlet of the refrigerator evaporator 623 is divided into two: the larger flow rate flows to the inlet of the third on/off valve 625, and the outlet of the third on/off valve 625 is connected to the inlet of the air conditioner indoor evaporator 602. The air is controlled by the damper mechanism to flow to the air conditioner indoor condenser 601 and the air conditioner indoor evaporator 602 at the same time, and the outlet of the air conditioner indoor evaporator 602 is low-temperature and low-pressure gas. The evaporator 602 in the air conditioner room is connected with a gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the gas with low temperature and low pressure returns to the air conditioner compressor 604, thereby forming a cycle. The other flow of the smaller flow rate flows to the inlet of the fourth switching valve 634, and the outlet of the fourth switching valve 634 is connected to the inlet of the refrigerator compressor 620. Finally, the low-temperature and low-pressure gas is returned to the refrigerator compressor 620, thereby forming another cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor evaporator 602 and the air conditioning indoor condenser 601. The first expansion valve 622 is opened, the third switching valve 625 is opened, the fourth switching valve 634 is opened, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is closed, the fourth expansion valve 609 is closed, the fifth switching valve 628 is closed, and the sixth switching valve 629 is opened.

And a fifth mode: and (4) an air conditioning heating mode.

As shown in fig. 6, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the condenser 601 in the air-conditioning room is connected with the inlet of the third expansion valve 607, and the outlet is low-temperature and low-pressure liquid after throttling and cooling by the third expansion valve 607. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to the air-conditioning outdoor heat exchanger 605 through a fifth switching valve 628, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected with the inlet of the gas-liquid separator 611 through the second on-off valve 610, 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 air conditioner compressor 604, thereby forming a circulation. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The first expansion valve 622 is closed, the third switching valve 625 is closed, the fourth switching valve 634 is closed, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the refrigerator compressor 620 is not operated, the air conditioner compressor 604 is operated, the fifth switching valve 628 is opened, and the sixth switching valve 629 is closed.

Mode six: and a bypass refrigeration mode of the air conditioner extremely-fast heating refrigerator.

First, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet flow from the condenser 601 flows to the inlet of the third expansion valve 607, and is throttled and cooled by the third expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to a fifth switching valve 628 and a sixth switching valve 629, respectively. The low-temperature and low-pressure liquid flowing out of the outlet of the third expansion valve 607 is divided into two: the larger flow rate flows to the inlet of the air-conditioning outdoor heat exchanger 605 through the fifth switching valve 628, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected to the inlet of the second switching valve 610. The other strand with smaller flow rate flows to the inlet of the refrigerator evaporator 623 through the sixth switch valve 629, and exchanges heat with the refrigerator body through the refrigerator evaporator 623 to absorb the heat of the refrigerator body, so that refrigeration of the refrigerator is realized, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The outlet of the refrigerator evaporator 623 is connected to the inlet of the air conditioner indoor evaporator 602 through a third switching valve 625. The refrigerant flowing out of the outlet of the second switching valve 610 and the refrigerant flowing out of the outlet of the air conditioner indoor evaporator 602 are joined and flow to the inlet of the gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the air conditioner compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The first expansion valve 622 is closed, the third switching valve 625 is opened, the fourth switching valve 634 is closed, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the fifth switching valve 628 is opened, the sixth switching valve 629 is opened, the refrigerator compressor 620 is not operated, and the air conditioner compressor 604 is operated.

Mode seven: and a super-speed refrigerating mode of the air conditioner super-speed heating refrigerator.

As shown in fig. 6, the refrigerator compressor 620 and the air conditioner compressor 604 are operated simultaneously. On the one hand, the high-temperature and high-pressure gas is discharged from the refrigerator compressor 620 through compression and is connected to the refrigerator condenser 621, and the high-temperature and high-pressure gas is condensed in the refrigerator condenser 621, so that the outlet of the refrigerator condenser 621 is the medium-temperature and high-pressure liquid. The outlet of the condenser 621 of the refrigerator is connected to the inlet of the first expansion valve 622, and is throttled and cooled by the first expansion valve 622, and the outlet is low-temperature and low-pressure liquid. Meanwhile, the air conditioner compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the air conditioner indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the air conditioner indoor condenser 601, so that the outlet of the air conditioner indoor condenser 601 is medium-temperature and high-pressure liquid. Flows from the outlet of the condenser 601 to the inlet of the third expansion valve 607, is throttled and cooled by the third expansion valve 607, and the outlet thereof is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 607 may be 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 air-conditioning compressor 604. The outlet of the third expansion valve 607 is connected to a fifth switching valve 628 and a sixth switching valve 629, respectively. The low-temperature and low-pressure liquid flowing out of the outlet of the third expansion valve 607 is divided into two: the larger flow rate flows to the inlet of the air-conditioning outdoor heat exchanger 605 through the fifth switching valve 628, the air-conditioning outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the air-conditioning outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the air conditioner outdoor heat exchanger 605 is connected to the inlet of the second switching valve 610. The other, which has a smaller flow rate, flows to the inlet of the sixth switching valve 629. The refrigerant flowing out of the outlet of the sixth switching valve 629 and the refrigerant flowing out of the outlet of the first expansion valve 622 join and flow to the inlet of the refrigerator evaporator 623, and exchange heat with the refrigerator body through the refrigerator evaporator 623 to absorb heat of the refrigerator body, thereby realizing refrigeration of the refrigerator, and the outlet of the refrigerator evaporator 623 is low-temperature and low-pressure gas. The low-temperature and low-pressure gas flowing out of the outlet of the refrigerator evaporator 623 is divided into two: the other flow of the smaller flow rate flows to the inlet of the fourth switching valve 634, and the outlet of the fourth switching valve 634 is connected to the inlet of the refrigerator compressor 620. Finally, the low-temperature and low-pressure gas returns to the refrigerator compressor 620, thereby forming a cycle; the other side of the larger flow rate is connected to the air conditioning indoor evaporator 602 through the third on/off valve 625. The refrigerant flowing out of the outlet of the second switching valve 610 and the refrigerant flowing out of the outlet of the air conditioner indoor evaporator 602 are joined and flow to the inlet of the gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the air conditioner compressor 604, thereby forming another cycle. The flow of air in the HVAC unit 600 then flows through both the air conditioning indoor condenser 601 and the air conditioning indoor evaporator 602. The first expansion valve 622 is opened, the third switching valve 625 is opened, the fourth switching valve 634 is opened, the third expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the fourth expansion valve 609 is closed, the fifth switching valve 628 is opened, the sixth switching valve 629 is opened, the refrigerator compressor 620 is operated, and the air conditioner compressor 604 is operated.

The specific structure of the thermal management system for the vehicle provided according to the third embodiment of the present disclosure, and the cycle process and principle thereof in different operation modes are described above. How to control the heat pump air conditioning system to be in the specific working mode according to the remaining driving energy value (such as the remaining electric quantity value and the remaining oil quantity value) of the whole vehicle will be described below, so as to fully utilize the whole vehicle resources, reduce the energy waste, and meet the refrigeration requirements of the refrigerator of different degrees of the user.

In the thermal management system of the vehicle according to the third embodiment provided by the present disclosure, the air conditioning compressor is a dual-drive compressor, which may further include a control device. The control strategy of the control device is similar to that of the first embodiment, and is not described herein again, but only the difference between the control strategies of the second embodiment is described.

When the air conditioner controller detects that the automobile thermal management system is in a heating mode, the control device can only control the automobile thermal management system to be in the refrigeration mode (primary refrigeration) of the refrigerator system.

In conclusion, the vehicle-mounted refrigerator system is added, and the refrigerator evaporator of the vehicle-mounted refrigerator system is connected in series on the refrigerator refrigeration bypass formed between the air-conditioning indoor condenser and the air-conditioning indoor evaporator. Therefore, in the bypass refrigeration mode of the air-conditioning bypass heating refrigerator, the refrigerator evaporator can replace an air-conditioning outdoor heat exchanger, so that the waste heat generated by refrigeration of the refrigerator is utilized to heat the refrigerant of the air-conditioning system, and the refrigeration of the refrigerator and the heating of the air conditioner are realized simultaneously on the basis of saving energy consumption. In addition, in the present disclosure, the in-vehicle refrigerator system and the air conditioner system operate independently of each other without interfering with each other. In addition, due to the fact that the refrigerator refrigeration bypass is additionally arranged, the refrigerator can be switched to multiple working modes during refrigeration, and the refrigeration requirements of users in different degrees are met.

It should be noted that in the present disclosure, the refrigeration of the air conditioning system itself is hardly affected because the volume of the evaporator of the refrigerator is small, and the air conditioning system is a key component for heating and cooling: the volumes of the indoor condenser and the indoor evaporator are relatively large, and the physical change of the refrigerant and the heat absorption and release of the refrigerant are mainly accomplished in the two components.

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

As shown in fig. 10, 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.

In this way, the expansion switching valve of the present disclosure 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 disclosure 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. 10 to 15, 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 portion 521 for driving a first valve core 503 is mounted in the first valve housing 511, a second electromagnetic driving portion 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. 10 to 13, 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. 14, 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 and the second through hole 527 may be spatially disposed perpendicularly or in parallel, which is not limited by the present disclosure and falls within the protection scope of the present disclosure.

To further simplify the overall footprint of the valve body 500, as shown in fig. 17-20, an inlet 501 and an outlet 502 are provided on the valve body 500 perpendicular to each other. Thus, as shown in fig. 17 to 19, 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. 13 and 14, 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. 16, 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. 13 and 14, the second valve core 504 includes a second valve rod 514, an end portion of the second valve rod 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. 13, 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. 17, a gap is formed between the tapered head structure at the end of the second valve body 504 and the orifice 505, and the refrigerant throttles and 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. 13, 16, and 19, 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. 13 and 19 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. 14 and 20, 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. 14 and 20, 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. 11, 17 and 18, 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 one example of the expansion on-off valve, and is not intended to limit the present disclosure, and other expansion on-off valves having both the expansion valve function and the on-off valve function are equally applicable to the present disclosure.

The present disclosure also provides an electric vehicle including the above vehicle thermal management system provided according to the present disclosure. The electric automobile can comprise a pure electric automobile, a hybrid electric automobile and a fuel cell automobile.

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

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

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

Claims

1. A vehicle thermal management system is characterized by comprising a heat pump air conditioning system and a vehicle-mounted refrigerator system, wherein the heat pump air conditioning system comprises an air conditioner compressor (604), an air conditioner indoor condenser (601), an air conditioner indoor evaporator (602) and an air conditioner outdoor heat exchanger (605), an outlet of the air conditioner compressor (604) is communicated with an inlet of the air conditioner indoor condenser (601), an outlet of the air conditioner indoor condenser (601) is selectively communicated with an inlet of the air conditioner outdoor heat exchanger (605) through a first throttling branch or a first through-flow branch, an outlet of the air conditioner outdoor heat exchanger (605) is selectively communicated with an inlet of the air conditioner compressor (604) through a second through-flow branch or communicated with an inlet of the air conditioner indoor evaporator (602) through a second throttling branch, an outlet of the air conditioner indoor evaporator (602) is communicated with an inlet of the air conditioner compressor (604),

the vehicle-mounted refrigerator system comprises a refrigerator compressor (620), a refrigerator condenser (621), a first expansion valve (622) and a refrigerator evaporator (623), wherein an outlet of the refrigerator compressor (620) is communicated with an inlet of the refrigerator condenser (621), an outlet of the refrigerator condenser (621) is communicated with an inlet of the refrigerator evaporator (623) through the first expansion valve (622), an outlet of the refrigerator evaporator (623) is communicated with an inlet of the refrigerator compressor (620),

the outlet of the condenser (601) in the air conditioner room is communicated with the inlet of the refrigerator evaporator (623) through a second expansion valve (624), and the outlet of the refrigerator evaporator (623) is also communicated with the inlet of the evaporator (602) in the air conditioner room or the inlet of the air conditioner compressor (604); or the outlet ends of the first throttling branch and the first through flow branch are also communicated with the inlet of the refrigerator evaporator (623), and the outlet of the refrigerator evaporator (623) is also communicated with the inlet of the air-conditioning indoor evaporator (602) or the inlet of the air-conditioning compressor (604).

2. The automotive thermal management system of claim 1, wherein a third expansion valve (607) is disposed in the first throttle branch, and a first on-off valve (608) is disposed in the first throttle branch.

3. The automotive thermal management system of claim 1, further comprising a first expansion switch valve (603), wherein an inlet and an outlet of the first expansion switch valve (603) are respectively communicated with the air-conditioning indoor condenser (601) and the air-conditioning 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).

4. The automotive thermal management system of claim 1, wherein a fourth expansion valve (609) is disposed in the second throttle branch, and a second on-off valve (610) is disposed in the second bypass branch.

5. The automotive thermal management system of claim 1, wherein an outlet of the air conditioner indoor evaporator (602) communicates with an inlet of the air conditioner compressor (604) via a first one-way valve (615).

6. The automotive thermal management system of claim 1, further comprising a gas-liquid separator (611), an outlet of the air conditioner indoor evaporator (602) being in communication with an inlet of the gas-liquid separator (611), an outlet of the gas-liquid separator (611) being in communication with an inlet of the air conditioner compressor (604).

7. The automotive thermal management system of claim 1, further comprising a third switching valve (625) and a fourth switching valve (634), wherein an outlet of the refrigerator evaporator (623) communicates with an inlet of the air conditioning indoor evaporator (602) or an inlet of the air conditioning compressor (604) through the third switching valve (625), and an outlet of the refrigerator evaporator (623) communicates with an inlet of the refrigerator compressor (620) through the fourth switching valve (634).

8. The automotive thermal management system of claim 7, further comprising a second one-way valve (626), wherein an outlet of the refrigerator evaporator (623) is communicated with an inlet of the air conditioner indoor evaporator (602) or an inlet of the air conditioner compressor (604) sequentially through the third switching valve (625) and the second one-way valve (626).

9. The automotive thermal management system of claim 1, further comprising a third one-way valve (627) and a fourth one-way valve (635), wherein an outlet of the air conditioner indoor condenser (601) is communicated with an inlet of the refrigerator evaporator (623) sequentially through the second expansion valve (624) and the third one-way valve (627), and the first expansion valve (622) is communicated with an inlet of the refrigerator evaporator (623) through the fourth one-way valve (635).

10. The automotive thermal management system of claim 1, wherein the outlet ends of the first throttling branch and the first through-flow branch are also communicated with an inlet of the refrigerator evaporator (623), the automotive thermal management system further comprising a fifth switching valve (628) and a sixth switching valve (629), the outlet ends of the first throttling branch and the first through-flow branch are communicated with an inlet of the air-conditioning outdoor heat exchanger (605) through the fifth switching valve (628), and the outlet ends of the first throttling branch and the first through-flow branch are communicated with an inlet of the refrigerator evaporator (623) through the sixth switching valve (629).

11. The automotive thermal management system of claim 10, further comprising a fourth check valve (635) and a fifth check valve (630), wherein the first expansion valve (622) is communicated with an inlet of the refrigerator evaporator (623) through the fourth check valve (635), and outlet ends of the first throttling branch and the second flow branch are communicated with an inlet of the refrigerator evaporator (623) through the sixth switching valve (629) and the fifth check valve (630) in sequence.

12. The automotive thermal management system of claim 1, characterized in that the outlet ends of the first throttle branch and the first through-flow branch are also in communication with an inlet of the refrigerator evaporator (623), the automotive thermal management system further comprising a first flow valve (631) and a second flow valve (632), the outlet ends of the first throttle branch and the first through-flow branch being in communication with an inlet of the air-conditioning outdoor heat exchanger (605) through the first flow valve (631), the outlet ends of the first throttle branch and the first through-flow branch being in communication with an inlet of the refrigerator evaporator (623) through the second flow valve (632).

13. The automotive thermal management system of claim 12, further comprising a fourth check valve (635) and a sixth check valve (633), wherein the first expansion valve (622) is communicated with an inlet of the refrigerator evaporator (623) through the fourth check valve (635), and outlet ends of the first throttling branch and the second flow branch are communicated with an inlet of the refrigerator evaporator (623) through the second flow valve (632) and the sixth check valve (633) in sequence.

14. An electric vehicle, characterized in that it comprises a vehicle thermal management system according to any one of claims 1 to 13.