CN108116188B

CN108116188B - Automobile heat management system and electric automobile

Info

Publication number: CN108116188B
Application number: CN201611086445.1A
Authority: CN
Inventors: 王子源; 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: CN108116188A

Abstract

The disclosure relates to an automobile thermal management system and an electric automobile. The automobile heat management system comprises a heat pump air conditioning system and a cup holder device, the heat pump air conditioning system comprises a compressor, an indoor condenser, an indoor evaporator and an outdoor heat exchanger, an outlet of the compressor is communicated with the indoor condenser, a first outlet of the indoor condenser is selectively communicated with an inlet of the outdoor heat exchanger through a first throttling branch or a second throttling branch, a second outlet is selectively communicated with an inlet end of the cup holder heat exchange tube through a third throttling branch or a third throttling branch, the outdoor heat exchanger and the cup holder heat exchange tube are both selectively communicated with the indoor evaporator through the second throttling branch or the second throttling branch, and an outlet of the indoor evaporator is communicated with the compressor.

Description

Automobile heat management system and electric automobile

Technical Field

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

Background

Automotive interiors are often provided with cup holders to support cups. Heating or cooling of the cup holder is often required to achieve a heating, cooling or warming treatment of the water in the cup. The cup stand in the prior art is heated or cooled mainly in two ways: firstly, cooling or heating is carried out by air-conditioning blowing; and the other is to adopt a semiconductor to heat or refrigerate.

The first approach has the following drawbacks: the air that blows off with the air conditioner directly cools off or heats, can seriously influence temperature regulation in the car, and user experience is relatively poor, and the thermal efficiency to the saucer heating is on the low side simultaneously, and the work of saucer can not the independent operation in addition, and heating or refrigeration depend on the air conditioner completely to the saucer, and under the air conditioner does not operate the condition, the heating or the cooling function of saucer can't realize.

The second method has the disadvantage of high power consumption.

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, which includes a heat pump air conditioning system and a cup holder device, the heat pump air conditioning system includes a compressor, an indoor condenser, an indoor evaporator and an outdoor heat exchanger, an outlet of the compressor is communicated with an inlet of the indoor condenser, a first outlet of the indoor condenser is selectively communicated with an inlet of the outdoor heat exchanger via a first throttling branch or a first through-flow branch, a second outlet of the indoor condenser is selectively communicated with an inlet end of the cup holder heat exchange tube via a third throttling branch or a third through-flow branch, an outlet of the outdoor heat exchanger and an outlet end of the cup holder heat exchange tube are both selectively communicated with an inlet of the indoor evaporator via a second throttling branch or a second through-flow branch, the outlet of the indoor evaporator is communicated with the inlet of the compressor; or the outlet of the compressor is communicated with the inlet of the indoor condenser, the outlet of the indoor condenser is selectively communicated with the inlet end of a heat exchange water path through a first throttling branch or a first through-flow branch, the outlet end of the heat exchange water path is selectively communicated with the inlet of the indoor evaporator through a second throttling branch or a second through-flow branch, the outlet of the indoor evaporator is communicated with the inlet of the compressor, the heat exchange water path comprises a first branch and a second branch which are connected in parallel, the outdoor heat exchanger is arranged on the first branch, and the cup holder heat exchange tube is arranged on the second branch.

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

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

Optionally, a third expansion valve is disposed on the third throttling branch, and a third on-off valve is disposed on the third throttling branch.

Optionally, the automobile thermal management system further includes a third expansion switch valve, an inlet and an outlet of the third expansion switch valve are respectively communicated with the indoor condenser and the cup holder heat exchange tube, the third throttling branch is a throttling flow channel of the third expansion switch valve, and the third flow branch is a through flow channel of the third expansion switch valve.

Optionally, a fourth switch valve located at the upstream of the outdoor heat exchanger is arranged on the first branch, and a fifth switch valve located at the upstream of the cup holder heat exchange tube is arranged on the second branch.

Optionally, a first flow valve located upstream of the outdoor heat exchanger is arranged on the first branch, and a second flow valve located upstream of the cup holder heat exchange tube is arranged on the second branch.

Optionally, the automobile thermal management system further includes a first check valve and a second check valve, the first check valve is disposed between the outlet of the outdoor heat exchanger and the inlet end of the second throttling branch or the second flow branch, and the second check valve is disposed between the outlet of the cup holder heat exchange tube and the inlet end of the second throttling branch or the second flow branch.

Optionally, the heat management system further comprises a gas-liquid separator, an outlet of the 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 compressor.

Optionally, the side wall of the cup holder comprises an inner wall and an outer wall which are spaced apart from each other, and the cup holder heat exchange tube is arranged between the inner wall and the outer wall.

Optionally, the inlet end and the outlet end of the cup holder heat exchange tube respectively protrude from the outer wall.

Optionally, the inlet end and the outlet end of the cup holder heat exchange tube are respectively provided with a tube joint.

Optionally, the cup holder heat exchange tube is formed as a helical tube spiraling up around the inner wall.

Optionally, the cup holder heat exchange tube is formed as a serpentine tube disposed around the inner wall and winding up and down.

Optionally, the inner wall is made of a thermally conductive material and the outer wall is made of a thermally insulating material.

Optionally, the heat conducting material is aluminum or copper, and the heat insulating material is epoxy resin glue or silica gel.

Optionally, a rubber ring is arranged on the cup opening of the cup holder, and the inner diameter of the rubber ring is smaller than that of the cup opening.

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.

The automobile heat management system provided by the disclosure can realize the requirements of cooling in summer and heating in winter in an automobile by using the heat pump air conditioning system, and also has the functions of cup stand cooling and cup stand heating. And, compare with the mode that cools off or heat the saucer through air conditioner cold and hot wind among the prior art, adopt this disclosed technical scheme, the refrigeration of saucer and heat the effect more obviously, efficiency is higher. This is because, the cold and hot wind of air conditioner actually comes from the wind that flows through indoor evaporimeter or indoor condenser, and the technical scheme of this disclosure can understand directly as indoor evaporimeter or indoor condenser with the cup holder device, reduces to carry out the heat exchange through the wind, has consequently promoted heat exchange efficiency. In addition, in this disclosure, the cooling or heating of the cup stand can be operated independently, and is not dependent on the air conditioning system, and when the air conditioning system does not have the cooling or heating demand, the compressor can be operated at low power to satisfy the cooling or heating demand of the cup stand, so as to further improve the user experience.

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 diagram of a heat pump air conditioning system according to another embodiment of the present disclosure;

FIG. 5 is a schematic structural diagram of an automotive thermal management system according to one 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. 9A is a schematic structural view of a cup holder apparatus according to one embodiment of the present disclosure;

FIG. 9B is a schematic structural view of a cup holder apparatus according to another embodiment of the present disclosure;

FIG. 10 is a schematic structural view of a cup holder according to an embodiment of the present disclosure in a use state;

FIG. 11 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. 12 is a schematic cross-sectional view taken along line AB-AB of FIG. 11, wherein both the first and second ports are in an open state;

fig. 13 is a front structural view in one view of an expansion switching valve provided in a preferred embodiment of the present disclosure;

FIG. 14 is a schematic cross-sectional view taken along line AB-AB of FIG. 11, with the first port in an open state and the second port in a closed state;

FIG. 15 is a schematic cross-sectional view taken along line AB-AB of FIG. 11, with the first port in a closed position and the second port in an open position;

fig. 16 is a front structural view of an expansion switching valve provided in a preferred embodiment of the present disclosure from another perspective;

FIG. 17 is a schematic cross-sectional view taken along line AC-AC of FIG. 16, with the first port in an open position and the second port in a closed position;

fig. 18 is a first internal structural view of an expansion switch 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. 19 is a partially enlarged view of a portion a in fig. 18;

fig. 20 is a second internal structural view of the expansion switching valve provided in the preferred embodiment of the present disclosure, wherein the first valve port is in an open state and the second valve port is in a closed state;

fig. 21 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.

Further, in the present disclosure, the electric vehicle may include a pure electric vehicle, a hybrid vehicle, a fuel cell vehicle.

Fig. 1 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure. As shown in fig. 1, the system may include: an HVAC (Heating Ventilation and Air Conditioning) assembly 600, a compressor 604, an outdoor heat exchanger 605, and a damper mechanism (not shown). The HVAC assembly 600 may include an indoor condenser 601 and an indoor evaporator 602, wherein the damper mechanism may be used to open the air duct to the indoor condenser 601 and the indoor evaporator 602, or to open the air duct to the indoor evaporator 602.

As shown in fig. 1, an outlet of the compressor 604 communicates with an inlet of the indoor condenser 601, an outlet of the indoor condenser 601 selectively communicates with an inlet of the outdoor heat exchanger 605 via a first throttling branch or a first through-flow branch, an outlet of the outdoor heat exchanger 605 selectively communicates with an inlet of the indoor evaporator 602 via a second throttling branch or a second through-flow branch, and an outlet of the indoor evaporator 602 communicates with an inlet of the compressor 604.

In the present disclosure, the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 either via 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 indoor condenser 601, an outlet of the first expansion switch valve 603 is communicated with an inlet of the outdoor heat exchanger 605, wherein the first throttling branch is a throttling flow passage of the first expansion switch valve 603, and the first through-flow branch is a through-flow passage of the first expansion switch valve 603.

In the present disclosure, the expansion switch 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 first 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 first expansion valve 607. Specifically, as shown in fig. 2, an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a first switching valve 608 to form a first through-flow branch, and an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a first expansion valve 607 to form a first throttle branch. In the air-conditioning cooling mode, the first switching valve 608 is turned on, the first expansion valve 607 is closed, and the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via the first flow passage. In the air-conditioning heating mode, the first expansion valve 607 is on, the first on-off valve 608 is closed, and the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via the first 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, the heat pump air conditioning system may further include a second expansion switch valve 606, an inlet of the second expansion switch valve 606 is communicated with an outlet of the outdoor heat exchanger 605, an outlet of the second expansion switch valve 606 is communicated with an inlet of the indoor evaporator 602, wherein the second throttling branch is a throttling flow passage of the second expansion switch valve 606, and the second flow branch is a flow passage of the second expansion switch valve 606.

As another alternative embodiment, as shown in fig. 3, the heat pump air conditioning system may further include a second on-off valve 610 and a second expansion valve 609, wherein the second on-off valve 610 is disposed in the second bypass, and the second expansion valve 609 is disposed in the second throttle. Specifically, as shown in fig. 3, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the second switching valve 610 to form a second pass branch, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the second expansion valve 609 to form a second throttle branch. In the air-conditioning cooling mode, the second expansion valve 609 is opened, the second switching valve 610 is closed, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the second throttling branch. In the air-conditioning heating mode, the second switching valve 610 is turned on, the second expansion valve 609 is closed, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the second bypass passage.

Fig. 4 shows a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure. As shown in fig. 4, the heat pump air conditioning system may further include a gas-liquid separator 611, wherein an outlet of the indoor evaporator 602 communicates with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 communicates with an inlet of the compressor 604. In this way, the refrigerant flowing out of the 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 compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 and damaging the compressor 604, so that the service life of the compressor 604 may be extended, and the efficiency of the entire heat pump air conditioning system may be improved.

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.

FIG. 5 is a schematic structural diagram of an automotive thermal management system according to a first embodiment of the present disclosure. As shown in fig. 5, the thermal management system of the vehicle may include the heat pump air conditioning system and the cup holder device described above, and the cup holder device includes a cup holder 620 and a cup holder heat exchange tube 621 in heat exchange contact with the cup holder 620. Wherein, the first outlet 601a of the indoor condenser 601 is selectively communicated with the inlet of the outdoor heat exchanger 605 via a first throttling branch or a first through-flow branch, the second outlet 601b of the indoor condenser 601 is selectively communicated with the inlet end 621a of the cup holder heat exchange tube 621 via a third throttling branch or a third through-flow branch, and both the outlet of the outdoor heat exchanger 605 and the outlet end 621b of the cup holder heat exchange tube 621 are selectively communicated with the inlet of the indoor evaporator 602 via a second throttling branch or a second through-flow branch. Here, the indoor condenser 601 may have two outlets by itself, or may extend the two outlets by connecting a three-way valve to the outlet of the indoor condenser 601, and both cases fall within the scope of the present disclosure.

That is, as the main inventive concept in the first embodiment of the present disclosure, it is to add a refrigerant dividing branch composed of a third throttling branch, a third flow branch and a cup holder heat exchange tube 621 together for heating or cooling the cup holder 620.

As one embodiment of the third flow branch and the third throttling branch, as shown in fig. 5, a third expansion valve 622 is disposed on the third throttling branch, and a third on/off valve 623 is disposed on the third flow branch, similar to the implementation of the first flow branch and the first throttling branch. Specifically, as shown in fig. 5, the second outlet 601b of the indoor condenser 601 communicates with the inlet end 621a of the cup holder heat exchange pipe 621 via a third expansion valve 622 to form a third throttling branch, and the second outlet 601b of the indoor condenser 601 communicates with the inlet end 621a of the cup holder heat exchange pipe 621 via a third switching valve 623 to form a third circulation branch.

As another alternative embodiment, as shown in fig. 6, the heat pump air conditioning system further includes a third expansion switch valve 624, an inlet and an outlet of the third expansion switch valve 624 are respectively communicated with the indoor condenser 601 and the cup holder heat exchange tube 621, a third throttling branch is a throttling flow channel of the third expansion switch valve 624, and a third flow branch is a through flow channel of the third expansion switch valve 624.

In order to prevent the refrigerant of low temperature and low pressure from flowing back to the outdoor heat exchanger 605 in the cup stand cooling mode, as shown in fig. 5 and 6, the heat pump air conditioning system further includes a first check valve 629, and the first check valve 629 is disposed between an outlet of the outdoor heat exchanger 605 and an inlet end of the second throttling branch or the second pass branch. That is, the first check valve can only allow the refrigerant to flow from the outlet of the outdoor heat exchanger 605 to the inlet end of the second throttling branch or the second circulating branch in one direction, and cannot flow in the opposite direction.

In order to prevent the refrigerant of low temperature and low pressure from flowing back to the cup holder heat exchange tube 621 in the air-conditioning heating mode, as shown in fig. 5 and 6, the heat pump air-conditioning system further includes a second check valve 630, and the second check valve 630 is disposed between the outlet end of the cup holder heat exchange tube 621 and the inlet end of the second throttling branch or the second pass branch. That is, the second check valve 630 allows the refrigerant to flow from the outlet end of the cup holder heat exchange tube 621 to the inlet end of the second throttling branch or the second circulating branch only in one direction, but not in the opposite direction.

The cycle process and principle of the thermal management system of the vehicle provided according to the first embodiment of the present disclosure in different operation modes will be described in detail below by taking fig. 5 as an example. It should be understood that the system cycle process and principle under other embodiments (e.g., the embodiment shown in fig. 6) are similar to those in fig. 5, and are not described in detail herein.

The first mode is as follows: and (4) an air-conditioning refrigeration mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The first outlet 601a of the indoor 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 outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature and high-pressure liquid. The outlet of the outdoor heat exchanger 605 is connected with the second expansion valve 609, and the temperature is reduced by throttling through the second expansion valve 609, and the outlet of the second expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the second expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the refrigerant at the outlet of the indoor evaporator based on the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The third expansion valve 622 is closed, the third switching valve 623 is closed, the first expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, and the second expansion valve 609 is opened.

And a second mode: a cup holder cooling mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The second outlet 601b of the indoor condenser 601 is connected to the inlet of the third expansion valve 622, and is throttled by the third expansion valve 622 to reduce the temperature, and the outlet thereof is low-temperature and low-pressure liquid. The outlet of the third expansion valve 622 is connected to the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the cup holder, so that the cup holder 620 can be cooled, and the outlet end 621b of the cup holder heat exchange tube 621 is low-temperature and low-pressure gas. An outlet end 621b of the cup holder heat exchange tube 621 is connected to an inlet of the indoor evaporator 602 through the second switching valve 610, and the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The air is controlled by the damper mechanism to flow to the indoor condenser 601 and the indoor evaporator 602 at the same time, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure air. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The third expansion valve 622 is opened, the third switching valve 623 is closed, the first switching valve 608 is closed, the first expansion valve 607 is closed, the second expansion valve 609 is closed, and the second switching valve 610 is opened.

And a third mode: and (4) an air conditioning heating mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and is throttled and cooled by the first expansion valve 607, and the outlet thereof is low-temperature and low-pressure liquid. The opening degree of the first expansion valve 607 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the discharge temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion valve 607 is connected to the outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs heat of outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the outdoor heat exchanger 605 is connected to the inlet of the indoor evaporator 602 through a second switching valve 610, and the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The air is controlled by the damper mechanism to flow to the indoor condenser 601 and the indoor evaporator 602 at the same time, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure air. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow direction of the air flowing in the HVAC assembly 600 simultaneously flows through the indoor condenser 601 and the indoor evaporator 602, and the indoor evaporator 602 can be considered as a refrigerant flow passage. The third expansion valve 622 is closed, the third switching valve 623 is closed, the first switching valve 608 is closed, the first expansion valve 607 is opened, the second expansion valve 609 is closed, and the second switching valve 610 is opened.

And a fourth mode: and a cup holder heating mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The second outlet 601b of the indoor condenser 601 is connected to the inlet of the third on/off valve 623, and the outlet of the third on/off valve 623 is still high-temperature and high-pressure gas. The outlet of the third switch valve 623 is connected to the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the refrigerant, so that the cup holder 620 can be heated, and the outlet end 621b of the cup holder heat exchange tube 621 is a medium-temperature high-pressure liquid. An outlet 621b of the underpinning heat pipe 621 is connected with an inlet of the second expansion valve 609, throttling and cooling are carried out through the second expansion valve 609, and an outlet of the second expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the second expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the refrigerant at the outlet of the indoor evaporator based on the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The third expansion valve 622 is closed, the third switching valve 623 is opened, the first expansion valve 607 is closed, the second switching valve 610 is closed, the second expansion valve 609 is opened, and the second switching valve 610 is closed.

And a fifth mode: and an air conditioning refrigeration and cup holder refrigeration mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The first outlet 601a of the indoor condenser 601 is connected to the inlet of the first switching valve 608, and the second outlet 601b thereof is connected to the third expansion valve 622, and at this time, the high-temperature and high-pressure gas flowing out of the outlet of the indoor condenser 601 is divided into two: the larger flow will flow to the inlet of the first on-off valve 608, while 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 the inlet of the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid; the other flow with smaller flow rate flows to the inlet of the third expansion valve 622, and is throttled and cooled by the third expansion valve 622, and the outlet is low-temperature and low-pressure liquid. The outlet of the third expansion valve 622 is connected to the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the cup holder, so that the cup holder 620 can be cooled, and the outlet end 621b of the cup holder heat exchange tube 621 is a medium-temperature low-pressure gas. The outlet end of the cup holder heat exchange tube 621 and the outlet of the outdoor heat exchanger 605 are both connected to the inlet end of the second throttling branch or the second circulation branch, the refrigerant coming out of the outlet of the outdoor heat exchanger 605 is merged with the refrigerant coming out of the outlet end 621b of the cup holder heat exchange tube 621, and flows into the second expansion valve 609, and is throttled and cooled by the second expansion valve 609, the outlet of the second expansion valve 609 is a gas-liquid mixture (wherein the liquid occupies most), the opening degree of the second expansion valve 609 can be given a certain opening degree according to actual requirements, and the opening degree can be adjusted by calculating the superheat degree of the refrigerant at the outlet of the indoor evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor arranged between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the gas-liquid mixture is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is a low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The third expansion valve 622 is opened, the third switching valve 623 is closed, the first expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, and the second expansion valve 609 is opened.

Mode six: and an air conditioner heating and cup holder heating mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and the second outlet 601b thereof is connected to the inlet of the third switching valve 623, at which time, the medium-temperature and high-pressure liquid flowing out of the outlet of the indoor condenser 601 is divided into two: the flow with a larger flow rate flows to the inlet of the first expansion valve 607, and is throttled and cooled by the first expansion valve 607, and the outlet of the first expansion valve 607 is low-temperature and low-pressure liquid, wherein the opening degree of the first expansion valve 607 can be adjusted according to the actual requirement, and the opening degree can be adjusted according to the temperature acquisition data (namely the exhaust temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604, the outlet of the first expansion valve 607 is connected with the outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure gas; the other flow with smaller flow rate flows to the third switch valve 623, at this time, the outlet of the third switch valve 623 is still medium-temperature high-pressure liquid, the outlet of the third switch valve 623 is connected with the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the refrigerant, so that the cup holder 620 can be heated, and the outlet end 621b of the cup holder heat exchange tube 621 is low-temperature high-pressure liquid. The outlet end of the cup holder heat exchange tube 621 and the outlet of the outdoor heat exchanger 605 are both connected to the inlet end of the second throttling branch or the second circulation branch, the refrigerant coming out of the outlet of the outdoor heat exchanger 605 and the refrigerant coming out of the outlet end 621b of the cup holder heat exchange tube 621 are merged and then connected to the inlet of the indoor evaporator 602 through the second switch valve 610, and the inlet of the indoor evaporator 602 is a gas-liquid mixture (wherein the gas occupies most part). The air is controlled by a damper mechanism to flow to the indoor condenser 601 and the indoor evaporator 602 simultaneously, and the outlet of the indoor evaporator 602 is a gas-liquid mixture (the gas is the most part). The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The third expansion valve 622 is closed, the third switching valve 623 is opened, the first expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, and the second expansion valve 609 is closed.

Mode seven: and an air conditioning cooling and cup holder heating mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The first outlet 601a of the indoor condenser 601 is connected to the inlet of the first switching valve 608, and the second outlet 601b thereof is connected to the inlet of the third switching valve 623, and at this time, the high-temperature and high-pressure gas flowing out of the outlet of the indoor condenser 601 is divided into two: the flow with larger flow rate flows to the inlet of the first switch valve 608, at this time, the outlet of the first switch valve 608 is still high-temperature high-pressure gas, the outlet of the first switch valve 608 is connected with the inlet of the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid; the other flow with smaller flow rate flows to the third on/off valve 623, and at this time, the outlet of the third on/off valve 623 is still high-temperature and high-pressure gas. The outlet of the third switch valve 623 is connected to the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the refrigerant, so that the cup holder 620 can be heated, and the outlet end 621b of the cup holder heat exchange tube 621 is a medium-temperature high-pressure liquid. The outlet end of the cup holder heat exchange tube 621 and the outlet of the outdoor heat exchanger 605 are both connected to the inlet end of the second throttling branch or the second circulation branch, the refrigerant coming out of the outlet of the outdoor heat exchanger 605 is merged with the refrigerant coming out of the outlet end 621b of the cup holder heat exchange tube 621 and flows into the second expansion valve 609, and is throttled and cooled by the second expansion valve 609, the outlet of the second expansion valve 609 is low-temperature and low-pressure liquid, the opening degree of the second expansion valve 609 can be given a certain opening degree according to actual requirements, and the opening degree can be adjusted by calculating the superheat degree of the refrigerant at the outlet of the indoor evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor arranged between the outlet of the indoor evaporator 602 and the inlet of the gas-. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The third expansion valve 622 is closed, the third switching valve 623 is opened, the first expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, and the second expansion valve 609 is opened.

And a mode eight: and an air conditioner heating and cup holder refrigerating mode. As shown in fig. 5, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The first outlet 601a of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and the second outlet 601b thereof is connected to the inlet of the third expansion valve 622, at which time, the medium-temperature and high-pressure liquid flowing out of the outlet of the indoor condenser 601 is divided into two streams: the flow with a larger flow rate flows to the inlet of the first expansion valve 607, and is throttled and cooled by the first expansion valve 607, and the outlet of the first expansion valve 607 is low-temperature and low-pressure liquid, wherein the opening degree of the first expansion valve 607 can be adjusted according to the actual requirement, and the opening degree can be adjusted according to the temperature acquisition data (namely the exhaust temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604, the outlet of the first expansion valve 607 is connected with the inlet of the outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure gas; the other flow with smaller flow rate flows to the inlet of the third expansion valve 622, is throttled and cooled by the third expansion valve 622, and the outlet of the third expansion valve 622 is low-temperature and low-pressure liquid, the outlet of the third expansion valve 622 is connected with the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb the heat of the cup holder, so that the cup holder 620 can be cooled, and the outlet end 621b of the cup holder heat exchange tube 621 is low-temperature and low-pressure gas. The refrigerant from the outlet of the outdoor heat exchanger 605 is merged with the refrigerant from the outlet end 621b of the cup holder heat exchange tube 621 and is connected to the inlet of the indoor evaporator 602 through the second switching valve 610, the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The third expansion valve 622 is opened, the third switching valve 623 is closed, the first expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, and the second expansion valve 609 is closed.

FIG. 7 is a schematic structural diagram of an automotive thermal management system according to a second embodiment of the present disclosure. As shown in fig. 7, the thermal management system of the vehicle may include the heat pump air conditioning system and the cup holder device described above, and the cup holder device includes a cup holder 620 and a cup holder heat exchange tube 621 in heat exchange contact with the cup holder 620. The outlet of the indoor condenser 601 is selectively communicated with the inlet end of the heat exchange water path through a first throttling branch or a first through-flow branch, the outlet end of the heat exchange water path is selectively communicated with the inlet of the indoor evaporator 602 through a second throttling branch or a second through-flow branch, the outdoor heat exchanger 605 is arranged on the first branch, and the cup holder heat exchange tube 621 is arranged on the second branch.

That is, as a main inventive concept in the second embodiment of the present disclosure, a second branch of the heat exchange water path is added as a refrigerant branch path for heating or cooling the cup holder.

In order to allow the cup holder heat exchange system and the air conditioning system to operate independently of each other, in a second embodiment provided by the present disclosure, as shown in fig. 7, a fourth switching valve 625 is provided on the first branch upstream of the outdoor heat exchanger 605, and a fifth switching valve 626 is provided on the second branch upstream of the cup holder heat exchange pipe 621. As another alternative embodiment, a first flow valve 627 is disposed on the first branch upstream of the outdoor heat exchanger 605, and a second flow valve 628 is disposed on the second branch upstream of the cup holder heat exchange tube 621. In addition, the first flow valve and the second flow valve can also adjust the flow of the first branch and the second branch.

In order to prevent the refrigerant of low temperature and low pressure from flowing back to the cup holder heat exchange tube 621 in the air-conditioning heating mode, as shown in fig. 7 and 8, the heat pump air-conditioning system further includes a second check valve 630, and the second check valve 630 is disposed between the outlet end of the cup holder heat exchange tube 621 and the inlet end of the second throttling branch or the second pass branch. That is, the second check valve 630 allows the refrigerant to flow from the outlet end of the cup holder heat exchange tube 621 to the inlet end of the second throttling branch or the second circulating branch only in one direction, but not in the opposite direction.

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

The first mode is as follows: and (4) an air-conditioning refrigeration mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor 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 the outdoor heat exchanger 605 through a fourth switch valve 625, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The outlet of the outdoor heat exchanger 605 is connected with the second expansion valve 609, and the temperature is reduced by throttling through the second expansion valve 609, and the outlet of the second expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the second expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the refrigerant at the outlet of the indoor evaporator based on the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The first expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, the second expansion valve 609 is opened, the fourth switching valve 625 is opened, and the fifth switching valve 626 is closed.

And a second mode: a cup holder cooling mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and the temperature is reduced by throttling the first expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the first expansion valve 607 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the discharge temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion valve 607 is connected to the inlet end 621a of the cup holder heat exchange tube 621, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the cup holder, so that the cup holder 620 can be cooled, and the outlet end 621b of the cup holder heat exchange tube 621 is low-temperature and low-pressure gas. An outlet end 621b of the cup holder heat exchange tube 621 is connected to an inlet of the indoor evaporator 602 through the second switching valve 610, and the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The air is controlled by the damper mechanism to flow to the indoor condenser 601 and the indoor evaporator 602 at the same time, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure air. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The first on-off valve 608 is closed, the first expansion valve 607 is closed, the second expansion valve 609 is closed, the second on-off valve 610 is opened, the fourth on-off valve 625 is closed, and the fifth on-off valve 626 is opened.

And a third mode: and (4) an air conditioning heating mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and the temperature is reduced by throttling the first expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the first expansion valve 607 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the discharge temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion valve 607 is connected to the inlet of the outdoor heat exchanger 605 through the fourth switching valve 625, the outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure gas. The outlet of the outdoor heat exchanger 605 is connected to the inlet of the indoor evaporator 602 through a second switching valve 610, and the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The air is controlled by the damper mechanism to flow to the indoor condenser 601 and the indoor evaporator 602 at the same time, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure air. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The first on-off valve 608 is closed, the first expansion valve 607 is opened, the second expansion valve 609 is closed, the second on-off valve 610 is opened, the fourth on-off valve 625 is opened, and the fifth on-off valve 626 is closed.

And a fourth mode: and a cup holder heating mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor 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 the inlet end 621a of the cup holder heat exchange tube 621 through the fourth switch valve 625, and exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621 to absorb heat of the refrigerant, so that the cup holder 620 can be heated, and the outlet end 621b of the cup holder heat exchange tube 621 is liquid with medium temperature and high pressure. An outlet 621b of the underpinning heat pipe 621 is connected with an inlet of the second expansion valve 609, throttling and cooling are carried out through the second expansion valve 609, and an outlet of the second expansion valve 609 is low-temperature and low-pressure liquid. The opening degree of the second expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the refrigerant at the outlet of the indoor evaporator based on the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The first expansion valve 607 is closed, the second switching valve 610 is closed, the second expansion valve 609 is opened, the second switching valve 610 is closed, the fourth switching valve 625 is opened, and the fifth switching valve 626 is closed.

And a fifth mode: and an air conditioning cooling and cup holder heating mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor condenser 601 is connected to the inlet of the first switching valve 608, and the outlet of the first switching valve 608 is still high-temperature and high-pressure gas. The outlet of the first switching valve 608 is connected to the inlets of the fourth switching valve 625 and the fifth switching valve 626, respectively, and at this time, the high-temperature and high-pressure gas flowing out of the outlet of the first switching valve 608 is divided into two streams: the flow with the larger flow rate flows to the outdoor heat exchanger 605 through the fourth switching valve 625, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. The other strand with smaller flow flows to the cup holder heat exchange tube 621 through the fifth switch valve 626, exchanges heat with the cup holder 620 through the cup holder heat exchange tube 621, absorbs heat of the refrigerant, and further can realize heating of the cup holder 620, and an outlet end 621b of the cup holder heat exchange tube 621 is medium-temperature high-pressure liquid. The outlet end of the cup holder heat exchange tube 621 and the outlet of the outdoor heat exchanger 605 are both connected to the inlet end of the second throttling branch or the second circulation branch, the refrigerant coming out of the outlet of the outdoor heat exchanger 605 is merged with the refrigerant coming out of the outlet end 621b of the cup holder heat exchange tube 621 and flows into the second expansion valve 609, and is throttled and cooled by the second expansion valve 609, the outlet of the second expansion valve 609 is low-temperature and low-pressure liquid, the opening degree of the second expansion valve 609 can be given a certain opening degree according to actual requirements, and the opening degree can be adjusted by calculating the superheat degree of the refrigerant at the outlet of the indoor evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor arranged between the outlet of the indoor evaporator 602 and the inlet of the gas-. An outlet of the second expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. The first expansion valve 607 is closed, the first switching valve 608 is opened, the second switching valve 610 is closed, the second expansion valve 609 is opened, the fourth switching valve 625 is opened, and the fifth switching valve 626 is opened.

Mode six: and an air conditioner heating and cup holder refrigerating mode. As shown in fig. 7, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the indoor condenser 601 is connected to the inlet of the first expansion valve 607, and the temperature is reduced by throttling the first expansion valve 607, and the outlet is low-temperature and low-pressure liquid. The opening degree of the first expansion valve 607 may be set to a certain opening degree according to actual demand, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the discharge temperature of the compressor) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the first expansion valve 607 is connected to a fourth switching valve 625 and a fifth switching valve 626, respectively, and at this time, the low-temperature and low-pressure liquid flowing out of the outlet of the first expansion valve 607 is divided into two streams: the flow rate of the air with a large flow rate flows to the outdoor heat exchanger 605 through the fourth switching valve 625, the outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure air. The other strand with smaller flow flows to the cup stand heat exchange tube 621 through the fifth switch valve 626, exchanges heat with the cup stand 620 through the cup stand heat exchange tube 621, absorbs the heat of the cup stand, and further can realize the cooling of the cup stand 620, and the outlet end 621b of the cup stand heat exchange tube 621 is low-temperature and low-pressure gas. The refrigerant from the outlet of the outdoor heat exchanger 605 is merged with the refrigerant from the outlet end 621b of the cup holder heat exchange tube 621 and is connected to the inlet of the indoor evaporator 602 through the second switching valve 610, the inlet of the indoor evaporator 602 is low-temperature and low-pressure gas, and the outlet of the indoor evaporator 602 is still low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The flow of air in the HVAC unit 600 now flows through both the indoor condenser 601 and the indoor evaporator 602. The first expansion valve 607 is opened, the first switching valve 608 is closed, the second switching valve 610 is opened, the second expansion valve 609 is closed, the fourth switching valve 625 is opened, and the fifth switching valve 626 is opened.

In the present disclosure, in order to improve the heat exchange efficiency between the cup holder 620 and the cup holder heat exchange tube 621, as shown in fig. 9A and 9B, the cup holder heat exchange tube 621 is embedded in the cup holder 620. That is, as shown in fig. 9A and 9B, the sidewall of the cup holder 620 may include an inner wall 620a and an outer wall 620B spaced apart from each other, i.e., the sidewall of the cup holder 620 has a double-layered structure. The cup holder heat exchange tube 621 is disposed between the inner wall 620a and the outer wall 620 b.

In the present disclosure, the inlet end 621a and the outlet end 621b of the cup holder heat exchange tube 621 may or may not protrude from the outer wall 620 b. In the former case, in order to facilitate connection with an external pipe, internal threads may be respectively formed at the inlet end 621a and the outlet end 621b of the cup holder heat exchange pipe 621, and an avoiding hole may be formed in the outer wall 620b, and during installation, a refrigerant pipe having external threads may be passed through the avoiding hole and be respectively screwed to the inlet end 621a and the outlet end 621 b. In the latter case, in order to facilitate connection with external pipes, pipe joints may be respectively disposed at the inlet end 621a and the outlet end 621b of the cup holder heat exchange pipe 621, and when installing, the external pipes may be respectively connected with the corresponding pipe joints.

To further increase the contact area between the cup holder 620 and the cup holder heat exchange tube 621 and improve the heat exchange efficiency, in an exemplary embodiment, as shown in fig. 9A, the cup holder heat exchange tube 621 is formed as a spiral tube having a central axis coinciding with the central axis of the cup holder 620. That is, the volute is disposed coaxially with the cup holder 620. As the refrigerant can flow along the spiral pipe, the heat transfer area between the refrigerant and the inner wall can be increased, and the heat exchange is ensured to be carried out efficiently. The cup holder heat exchange tube 621 can be gradually wound on the inner wall 620a in a spiral manner from bottom to top, that is, the inlet end 621a of the cup holder heat exchange tube 621 is located at the bottom of the cup holder, and the outlet end 621b of the cup holder heat exchange tube 621 is located at the top of the cup holder. The cup holder heat exchange tube 621 can also be gradually wound on the inner wall 620a from top to bottom in a spiral manner, that is, the inlet end 621a of the cup holder heat exchange tube 621 is located at the top of the cup holder, and the outlet end 621b of the cup holder heat exchange tube 621 is located at the bottom of the cup holder.

In another exemplary embodiment, as shown in fig. 9B, the cup holder heat exchange tube 621 is formed as a serpentine tube disposed around the inner wall 620 a. That is, the serpentine tube is formed in a shape similar to a telephone wire wound in one turn.

To further improve the heat exchange efficiency between the refrigerant and the cup 629 and to prevent the refrigerant flowing through the heat exchange tubes of the cup holder from exchanging heat with the air outside the cup holder 620, the inner wall 620a may be made of a heat conductive material and the outer wall 620b may be made of a heat insulating material.

Wherein, in order to ensure good heat exchange effect, the cup holder heat exchange tube can be made into an aluminum tube by using an aluminum material. The aluminum pipe has good heat conductivity and can bear certain pressure, and heat release or heat absorption can be rapidly carried out in the process that the refrigerant flows through the aluminum pipe, so that the heat exchange efficiency is improved. Or the cup holder heat exchange tube can also be made of copper material into a copper tube.

Similarly, to ensure good thermal insulation, the outer wall 620b may be made of thermal insulation material such as epoxy resin glue or silica gel.

Further, in order to better isolate the air inside the cup holder from the air outside and facilitate the fixing of the water cup 629, as shown in fig. 9A, 9B and 10, a rubber ring 620c is provided on the rim of the cup holder 620, and the inner diameter of the rubber ring 620c is smaller than that of the rim. As shown in FIG. 10, when the cup 629 is placed in the cup holder, the inner ring of the rubber ring 620c presses against the cup 629, thereby better locking the hot or cold air in the gap between the cup holder 620 and the cup without affecting the temperature inside the vehicle.

In addition, in the present disclosure, the cup holder device 620 may be provided on the center console 630, for example.

It should be noted that, in the present disclosure, the cooling and heating of the air conditioning system itself are hardly affected because the volume of the cup holder heat exchange tube 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. When the air conditioner is used for refrigerating and heating, a small amount of refrigerant flows through the cup stand heat exchange tube, and the refrigerating or heating requirements of the cup stand can be met. If the air conditioner has no refrigerating requirement, the compressor is operated at low power, and the refrigerating and heating requirements of the cup stand can be met.

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. 11, 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. 11 to 16, 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. 11 to 14, 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. 15, 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. 18-21, an inlet 501 and an outlet 502 are provided on the valve body 500 perpendicular to each other. In this way, as shown in fig. 18 to 20, 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. 14 and 15, in order to realize the closing and opening of the first port 516, the first valve core 503 is arranged 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. 17, 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. 14 and 15, the second valve spool 504 includes a second valve stem 514, an end portion of the second valve stem 514 is formed into a conical head structure, and the second valve port 517 is formed into a conical hole structure matched with the conical head structure.

The opening degree of the orifice 505 of the expansion switch valve can be adjusted by the vertical movement of the second valve element 504, and the vertical movement of the second valve element 504 can be adjusted by the second electromagnetic driving unit 522. If the opening degree of the orifice 505 of the expansion switch valve is zero, as shown in fig. 14, 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. 15, a gap is formed between the orifice 505 and the tapered head structure at the end of the second valve body 504, and the refrigerant 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. 14, 17, and 20, 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. 14 and 20 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. 15 and 21, the second port 517, i.e., the choke 505, is in an open state, the first valve body 503 blocks 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. 15 and 21, 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. 12, 18 and 19, 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 the various features described in the above embodiments may be combined in any suitable manner without departing from the scope of the invention. In order to avoid unnecessary repetition, various possible combinations will not be separately described in this disclosure.

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

Claims

1. The automobile thermal management system is characterized by comprising a heat pump air-conditioning system and a cup holder device, wherein the heat pump air-conditioning system comprises a compressor (604), an indoor condenser (601), an indoor evaporator (602) and an outdoor heat exchanger (605), the cup holder device comprises a cup holder (620) and a cup holder heat exchange tube (621) which is in contact with the cup holder (620) for heat exchange,

the outlet of the compressor (604) is communicated with the inlet of the indoor condenser (601), the first outlet (601a) of the indoor condenser (601) is selectively communicated with the inlet of the outdoor heat exchanger (605) through a first throttling branch or a first through-flow branch, the second outlet (601b) of the indoor condenser (601) is selectively communicated with the inlet end (621a) of the cup holder heat exchange tube (621) through a third throttling branch or a third through-flow branch, the outlet of the outdoor heat exchanger (605) and the outlet end (621b) of the cup holder heat exchange tube (621) are both selectively communicated with the inlet of the indoor evaporator (602) through a second throttling branch or a second through-flow branch, and the outlet of the indoor evaporator (602) is communicated with the inlet of the compressor (604);

or the outlet of the compressor (604) is communicated with the inlet of the indoor condenser (601), the outlet of the indoor condenser (601) is selectively communicated with the inlet end of a heat exchange water path through a first throttling branch or a first through-flow branch, the outlet end of the heat exchange water path is selectively communicated with the inlet of the indoor evaporator (602) through a second throttling branch or a second through-flow branch, the outlet of the indoor evaporator (602) is communicated with the inlet of the compressor (604), the heat exchange water path comprises a first branch and a second branch which are connected in parallel, the outdoor heat exchanger (605) is arranged on the first branch, and the cup-holder heat exchange tube (621) is arranged on the second branch.

2. The automotive thermal management system of claim 1, wherein a first 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 indoor condenser (601) and the outdoor heat exchanger (605), the first throttling branch is a throttling flow passage of the first expansion switch valve (603), and the first through-flow branch is a through-flow passage of the first expansion switch valve (603).

4. The automotive thermal management system of claim 1, wherein a second 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, further comprising a second expansion switch valve (606), wherein an inlet and an outlet of the second expansion switch valve (606) are respectively communicated with the outdoor heat exchanger (605) and the indoor evaporator (602), the second throttling branch is a throttling flow passage of the second expansion switch valve (606), and the second through-flow branch is a through-flow passage of the second expansion switch valve (606).

6. The automotive thermal management system of claim 1, wherein a third expansion valve (622) is disposed in the third branch, and a third on/off valve (623) is disposed in the third branch.

7. The automotive thermal management system of claim 1, further comprising a third expansion switch valve (624), wherein an inlet and an outlet of the third expansion switch valve (624) are respectively communicated with the indoor condenser (601) and the cup holder heat exchange tube (621), the third throttling branch is a throttling flow passage of the third expansion switch valve (624), and the third throttling branch is a through flow passage of the third expansion switch valve (624).

8. The automotive thermal management system of claim 1, wherein the first branch is provided with a fourth switching valve (625) upstream of the outdoor heat exchanger (605), and the second branch is provided with a fifth switching valve (626) upstream of the cup holder heat exchange tube (621).

9. The automotive thermal management system of claim 1, wherein the first branch is provided with a first flow valve (627) upstream of the outdoor heat exchanger (605), and the second branch is provided with a second flow valve (628) upstream of the cup holder heat exchange tube (621).

10. The automotive thermal management system of claim 1, further comprising a first check valve (629) and a second check valve (630), the first check valve (629) being disposed between the outlet of the outdoor heat exchanger (605) and the inlet end of the second throttling or bypass branch, the second check valve (630) being disposed between the outlet of the cup holder heat exchange tube (621) and the inlet end of the second throttling or bypass branch.

11. The automotive thermal management system of claim 1, further comprising a gas-liquid separator (611), an outlet of the indoor evaporator (602) communicating with an inlet of the gas-liquid separator (611), an outlet of the gas-liquid separator (611) communicating with an inlet of the compressor (604).

12. The automotive thermal management system of claim 1, characterized in that the side walls of the cup holder (620) comprise an inner wall (620a) and an outer wall (620b) that are spaced apart from each other, the cup holder heat exchange tube (621) being disposed between the inner wall (620a) and the outer wall (620 b).

13. The automotive thermal management system of claim 12, wherein the inlet end (621a) and the outlet end (621b) of the cup holder heat exchange tube (621) each extend from the outer wall (620 b).

14. The automotive thermal management system of claim 13, wherein the inlet end (621a) and the outlet end (621b) of the cup holder heat exchange tube (621) are each provided with a tube connector.

15. The automotive thermal management system of claim 12, wherein the cup holder heat exchange tube (621) is formed as a spiral tube spiraling up around the inner wall (620 a).

16. The automotive thermal management system of claim 12, wherein the cup holder heat exchange tube (621) is formed as a serpentine tube disposed around the inner wall (620a) and spiraling up and down.

17. The automotive thermal management system of claim 12, wherein the inner wall (620a) is made of a thermally conductive material and the outer wall (620b) is made of a thermally insulating material.

18. The automotive thermal management system of claim 17, wherein the thermally conductive material is aluminum or copper and the thermally insulating material is epoxy glue or silicone glue.

19. The automotive thermal management system of claim 12, wherein a rubber ring (620c) is disposed on a cup opening of the cup holder (620), and an inner diameter of the rubber ring (620c) is smaller than an inner diameter of the cup opening.

20. An electric vehicle comprising a vehicle thermal management system according to any one of claims 1 to 19.