CN108248331B

CN108248331B - Heat pump air conditioning system and electric automobile

Info

Publication number: CN108248331B
Application number: CN201611246469.9A
Authority: CN
Inventors: 黄健; 陈雪峰; 叶梅娇
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2016-12-29
Filing date: 2016-12-29
Publication date: 2023-11-14
Anticipated expiration: 2036-12-29
Also published as: CN108248331A

Abstract

The disclosure relates to a heat pump air conditioning system and an electric automobile. The heat pump air conditioning system comprises a compressor, an indoor condenser, an indoor evaporator, an outdoor heat exchanger and an expansion switch valve, wherein the outlet of the compressor is communicated with the inlet of the indoor condenser, the outlet of the indoor condenser is communicated with the second inlet of the expansion switch valve, the outlet of the expansion switch valve is communicated with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger (605) is selectively communicated with the inlet of the compressor through a first through flow branch or is communicated with the inlet of the indoor evaporator through a first throttling branch, the outlet of the indoor evaporator is communicated with the inlet of the compressor, and the outlet of the compressor or the outlet of the indoor condenser is also communicated with the first inlet of the expansion switch valve. Therefore, the heating energy efficiency can be improved, the requirements of defrosting and demisting regulations are met, the effects of convenience in installation and the like are achieved, the pipeline connection is simplified, the cost is reduced, the refrigerant filling amount of the whole heat pump air conditioning system is reduced, and the oil return of the compressor is facilitated.

Description

Heat pump air conditioning system and electric automobile

Technical Field

The present disclosure relates to an automotive air conditioning system, in particular, to a heat pump air conditioning system, and also to an electric automobile provided with the heat pump air conditioning system.

Background

The electric automobile does not have the waste heat of the engine used for heating by the traditional automobile, and can not provide a heating heat source. Therefore, the air conditioning system of the electric vehicle must have a heating function itself, that is, heat pump type air conditioning system and/or electric heating heat supply are adopted.

The utility model patent with publication number CN102788397A discloses an electric automobile heat pump air conditioning system. Although the heat pump air conditioning system can be used in various electric automobiles, the system uses two outdoor heat exchangers (one outdoor condenser and one outdoor evaporator), so that the wind resistance of the front end module of the automobile is large, the system structure is complex, and the heating effect is influenced.

In addition, in the heat pump air conditioning system, it is sometimes necessary to control the throttling and the depressurization of the refrigerant or only pass through the throttle-free state, while the existing electronic expansion valve can only control the throttling or not pass through the refrigerant. To meet such a requirement of the heat pump system, the prior art uses a structure in which an electronic expansion valve and an electromagnetic switching valve are connected in parallel. The structure needs to use two tee joints and six pipelines, is complex and is inconvenient to install. When the electromagnetic valve is closed and the electronic expansion valve is used, the inlet of the electronic expansion valve is a medium-temperature high-pressure liquid refrigerant, the outlet of the electronic expansion valve is a low-temperature low-pressure liquid refrigerant, and because the pipelines are communicated, the inlet and the outlet of the electromagnetic valve are respectively consistent with the state of the refrigerant at the inlet and the outlet of the electronic expansion valve, the pressure and the temperature of the refrigerant at the inlet and the outlet of the electromagnetic valve are different, and the internal structure of the electromagnetic valve is easy to be damaged. In addition, because the pipelines are relatively more, the refrigerant filling amount of the whole heat pump air conditioning system can be improved, and the cost is increased. When the heat pump air conditioning system works at low temperature, oil return of the compressor can be difficult, and the complex structure is unfavorable for oil return of the heat pump air conditioning system.

Disclosure of Invention

The disclosure aims to provide a heat pump air conditioning system and an electric automobile so as to solve the technical problems.

In order to achieve the above object, according to a first aspect of the present disclosure, there is provided a heat pump air conditioning system including a compressor, an indoor condenser, an indoor evaporator, an outdoor heat exchanger, and an expansion valve including a valve body on which a first inlet, a second inlet, an outlet, and an internal flow passage communicating between the first inlet, the second inlet, and the outlet are formed, a first valve spool and a second valve spool being installed on the internal flow passage, the first valve spool causing the first inlet and the outlet to be directly communicated or to be disconnected from communication, the second valve spool causing the second inlet and the outlet to be communicated through an orifice, the outlet of the compressor to be communicated with the inlet of the indoor condenser, the outlet of the indoor condenser to be communicated with the second inlet of the expansion valve, the outlet of the expansion valve to be communicated with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger to be selectively communicated with the inlet of the compressor via a first flow passage or with the inlet of the indoor evaporator via a first flow passage, the inlet of the indoor heat exchanger to be communicated with the inlet of the compressor or the outlet of the indoor condenser via the indoor evaporator, and the expansion valve.

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

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

Optionally, the heat pump air conditioning system is applied to an electric automobile, and the first through-flow branch is further provided with a plate heat exchanger, and the plate heat exchanger is simultaneously arranged in a motor cooling system of the electric automobile.

Optionally, a first switch valve is arranged on the first through flow branch, the refrigerant inlet of the plate heat exchanger is communicated with the outlet of the outdoor heat exchanger, and the refrigerant outlet of the plate heat exchanger is communicated with the inlet of the first switch valve.

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

Optionally, the system further comprises a gas-liquid separator, the outlet of the indoor evaporator is communicated with the inlet of the gas-liquid separator, the outlet of the outdoor heat exchanger is communicated with the inlet of the gas-liquid separator via the first through-flow branch, and the outlet of the gas-liquid separator is communicated with the inlet of the compressor.

Optionally, the internal flow passage includes a first flow passage and a second flow passage respectively communicating with the first inlet and the second inlet, a first valve port cooperating with the first valve core is formed on the first flow passage, the orifice is formed on the second flow passage to form a second valve port cooperating with the second valve core, and the first flow passage and the second flow passage meet downstream of the second valve port and communicate with the outlet.

Optionally, the first valve core and the second valve core are parallel to each other.

Optionally, the second flow channel is perpendicular to the outlet, the first flow channel is formed as a first through hole parallel to the second flow channel, the second inlet is communicated with the second flow channel through a second through hole formed on the side wall of the second flow channel, and the first through hole and the second through hole are respectively communicated with the first inlet and the second inlet.

Optionally, the first through hole and the second flow channel are respectively communicated with the outlet through a third through hole and a fourth through hole, and the third through hole and the fourth through hole are coaxially and oppositely arranged and are mutually perpendicular to the outlet.

Optionally, the first inlet and the second inlet are parallel to each other and are arranged on the same side of the valve body, and the outlet is parallel to the first inlet and the second inlet respectively.

Optionally, the outlet is disposed between the first spool and the second spool.

Optionally, the first valve core is coaxially arranged with the first valve port along the moving direction so as to selectively block or separate from the first valve port.

Optionally, the second valve core is coaxially arranged with the second valve port along the moving direction so as to selectively block or separate from the second valve port.

Optionally, the first valve core includes a first valve stem and a first plug connected to an end of the first valve stem, and the first plug is used for sealing and pressing against an end face of the first valve port to seal the first flow channel.

Optionally, the second valve core includes a second valve stem, an end of the second valve stem is formed as a conical head structure, and the second valve port is formed as a conical hole structure matched with the conical head structure.

Optionally, the valve body includes a valve seat forming the internal flow passage, and a first valve housing and a second valve housing mounted on the valve seat, a first electromagnetic driving part for driving the first valve core is mounted in the first valve housing, a second electromagnetic driving part for driving the second valve core is mounted in the second valve housing, the first valve core extends from the first valve housing to the internal flow passage in the valve seat, and the second valve core extends from the second valve housing to the internal flow passage in the valve seat.

Optionally, the valve seat is formed as a polyhedral structure, the first valve housing and the second valve housing are disposed on the same surface of the polyhedral structure, the first inlet and the second inlet are disposed on the same surface of the polyhedral structure, and the first valve housing, the first inlet and the outlet are disposed on different surfaces of the polyhedral structure, respectively, wherein the mounting directions of the first valve housing and the second valve housing are parallel to each other, and the opening directions of the inlet and the outlet are parallel to each other.

According to a second aspect of the present disclosure, there is provided an electric vehicle comprising the heat pump air conditioning system provided according to the first aspect of the present disclosure.

The heat pump air conditioning system provided by the disclosure can realize the functions of refrigerating and heating of the automobile air conditioning system and defrosting of the outdoor side heat exchanger under the condition of not changing the circulation direction of the refrigerant, and can meet the requirements of simultaneous refrigerating and heating. In the bypass defrosting process of the outdoor heat exchanger, the heating requirement in the vehicle can be met. In addition, the heat pump air conditioning system disclosed by the invention only adopts one outdoor heat exchanger, so that the wind resistance of the front end module of the automobile can be reduced, the problems that the heating energy efficiency of the automobile heat pump air conditioning system of a pure electric automobile or a hybrid electric automobile without an engine waste heat circulation system in a pure electric mode is low, the requirements of defrosting and demisting regulations cannot be met, the installation is complex and the like are solved, and the effects of reducing energy consumption, simplifying the system structure and facilitating the pipeline arrangement are achieved. In addition, by installing the expansion switch valve in the heat pump air conditioning system, the pipeline connection can be simplified, the cost is reduced, the refrigerant filling amount of the whole heat pump air conditioning system is reduced, and the oil return of the compressor is facilitated; in addition, the heat pump air conditioning system provided by the disclosure has the characteristics of simple structure, so that mass production is easy.

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

Drawings

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

FIG. 1 is a schematic diagram of a heat pump air conditioning system provided in accordance with one embodiment of the present disclosure;

FIG. 2 is a schematic diagram of a heat pump air conditioning system provided in accordance with another embodiment of the present disclosure;

FIG. 3 is a schematic diagram of a heat pump air conditioning system provided in accordance with another embodiment of the present disclosure;

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

fig. 5 is a schematic perspective view of an expansion valve according to an exemplary embodiment of the present disclosure in one direction;

fig. 6 is a schematic perspective view of an expansion valve according to an exemplary embodiment of the present disclosure in another direction;

FIG. 7 is a schematic cross-sectional view of an expansion valve according to an exemplary embodiment of the present disclosure, wherein a first valve port is in an open state and a second valve port is in a closed state;

FIG. 8 is another cross-sectional schematic view of an expansion valve according to an exemplary embodiment of the present disclosure, wherein the first port is in a closed state and the second port is in an open state;

FIG. 9 is a first internal schematic diagram of an expansion valve according to an exemplary embodiment of the present disclosure, wherein the first valve port is in an open state;

fig. 10 is a second internal structural schematic diagram of an expansion valve provided according to an exemplary embodiment of the present disclosure, in which the second valve port is in an open state.

Detailed Description

Specific embodiments of the present disclosure are described in detail below with reference to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the disclosure, are not intended to limit the disclosure.

In the present disclosure, unless otherwise indicated, terms of orientation such as "up, down, left, right" are used generally with respect to the direction of the drawing sheet of the drawings, "upstream, downstream" are with respect to the direction of flow of a medium, such as a refrigerant, specifically downstream toward the direction of flow of the refrigerant, and upstream away from the direction of flow of the refrigerant, "inside, outside" refer to the inside and outside of the respective component profiles.

In the present disclosure, electric vehicles may include pure electric vehicles, hybrid electric vehicles, fuel cell vehicles.

Fig. 1 is a schematic structural view of a heat pump air conditioning system according to a first embodiment of the present disclosure. As shown in fig. 1, the system may include: HVAC (heating ventilation and air conditioning ) assembly 600 and a damper mechanism (not shown), wherein the damper mechanism can be used to open the air duct to indoor evaporator 602 and indoor condenser 601. In addition, the system includes an expansion switch valve 5, a compressor 604, and an outdoor heat exchanger 605. Wherein HVAC assembly 600 may include an indoor condenser 601 and an indoor evaporator 602. The outlet of the compressor 604 communicates with the inlet of the indoor condenser 601, the outlet of the indoor condenser 601 communicates with the second inlet 501b of the expansion valve 5, the outlet 502 of the expansion valve 5 communicates with the inlet of the outdoor heat exchanger 605, the outlet of the outdoor heat exchanger 605 selectively communicates with the inlet of the indoor evaporator 602 via the first throttle bypass or with the inlet of the compressor 604 via the first through-flow bypass, the outlet of the indoor evaporator 602 communicates with the inlet of the compressor 604, and the outlet of the indoor condenser 601 also communicates with the first inlet 501a of the expansion valve 5. In other words, the outlet of the outdoor heat exchanger 605 selectively communicates with the inlet of the outdoor heat exchanger 605 via the throttle flow passage of the expansion valve 5 or the through flow passage of the expansion valve 5.

In the present disclosure, an expansion valve is a valve having both an expansion valve function (may also be referred to as an electronic expansion valve function) and a switching valve function (may also be referred to as a solenoid valve function), and may be regarded as an integration of the switching 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 valve is used as an expansion valve, the throttle flow passage in the expansion valve is conducted, and a throttle branch is formed.

In the present disclosure, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the compressor 604 either via the first through-flow branch or with the inlet of the indoor evaporator 602 via the first throttle branch. This communication may be achieved in a number of ways. For example, in one embodiment, as shown in fig. 1, a first on-off valve 610 is provided in the first through-flow path, and a first expansion valve 609 is provided in the first throttle path. Specifically, as shown in fig. 2, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the compressor 604 via a first switching valve 610 to form a first through-flow branch, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via a first expansion valve 609 to form a first throttle branch. When the system is in the high temperature cooling mode, the first expansion valve 609 is on, the first on-off valve 610 is off, and the outlet of the outdoor heat exchanger 605 is in communication with the inlet of the indoor evaporator 602 via the first throttling branch. When the system is in a low temperature heating mode, the first switching valve 610 is turned on, the first expansion valve 609 is closed, and the outlet of the outdoor heat exchanger 605 is communicated with the inlet of the compressor 604 via the first through-flow branch.

Fig. 2 illustrates a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure. As shown in fig. 2, the heat pump air conditioning system may further include a gas-liquid separator 611 and a check valve 615, wherein an outlet of the indoor evaporator 602 is in communication with an inlet of the gas-liquid separator 611, an outlet of the outdoor heat exchanger 605 is in communication with an inlet of the gas-liquid separator 611 via a first through-flow branch, and an outlet of the gas-liquid separator 611 is in communication with an inlet of the compressor 604. In this way, the refrigerant flowing out through the indoor evaporator 602 or the first switching valve 610 may be first subjected to gas-liquid separation through the gas-liquid separator 611, and the separated gas may be returned to the compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 to damage the compressor 604, so that the service life of the compressor 604 may be prolonged, and the efficiency of the whole heat pump air conditioning system may be improved. The outlet of the indoor evaporator 602 communicates with the inlet of the gas-liquid separator 611 through a check valve 615. Here, the check valve 615 is provided to prevent the refrigerant from flowing back to the indoor evaporator 602 in a low temperature heating mode (described in detail below), affecting the heating effect.

The cycle process and principle of the first heat pump air conditioning system provided in the present disclosure in different operation modes will be described in detail with reference to fig. 2. It should be understood that the system circulation process and principle in other embodiments (e.g., the embodiment shown in fig. 1) are similar to those of fig. 2, and will not be described in detail herein.

Mode one: high temperature cooling mode. When the system is in this mode, the entire system forms a high temperature refrigeration cycle. As shown in fig. 2, first, a compressor 604 discharges high-temperature and high-pressure gas through compression, and is connected to an 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, no heat exchange is performed in the indoor condenser 601, and 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 communicates with the outlet 502 of the expansion valve 5 via the first inlet 501a of the expansion valve 5, and the expansion valve 5 functions as a switching valve and flows only as a flow passage, and the outlet 502 of the expansion valve 5 is still high-temperature and high-pressure gas. The outlet 502 of the expansion switch valve 5 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, heat is emitted to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the first on-off valve 610 is closed, the outlet of the outdoor heat exchanger 605 is connected to the first expansion valve 609, the first expansion valve 609 serves as a throttle member, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the first expansion valve 609 may be given a certain opening degree according to actual demands, and the opening degree may be adjusted by calculating the superheat degree of the refrigerant at the outlet of the evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The outlet of the first expansion valve 609 is connected to the inlet of the indoor evaporator 602, and the low-temperature low-pressure liquid evaporates in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The outlet of the indoor evaporator 602 is connected to the inlet of the check valve 615, the outlet of the check valve 615 is connected to the inlet of the gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. At this time, the flow direction of the air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 does not pass therethrough, and only flows as a refrigerant flow path.

Mode two: low temperature heating mode. When the system is in the mode, the whole system forms a low-temperature heating circulation system. As shown in fig. 2, first, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and the gas is connected to the indoor condenser 601, and at this time, the air passes through 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 communicates with the outlet 502 of the expansion valve 5 via the second inlet 501b of the expansion valve 5, and at this time, the expansion valve 5 functions as an expansion valve, and as a throttling element, the outlet thereof is a low-temperature low-pressure liquid. The opening degree of the expansion valve 5 may be set to a certain opening degree according to actual demands, and the opening degree may be adjusted according to the amount of temperature acquisition data (i.e., compressor discharge temperature) of a pressure-temperature sensor installed at the outlet of the compressor 604. The outlet 502 of the expansion valve 5 is connected to the inlet of the outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature low-pressure gas. At this time, the first switching valve 610 is opened, the first expansion valve 609 is closed, the refrigerant directly enters the gas-liquid separator 611 without passing through the indoor evaporator 602, the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas is returned to the compressor 604, thereby forming a cycle. The air in HVAC assembly 600 now flows through both indoor condenser 601 and indoor evaporator 602.

Mode three: and simultaneously, a refrigerating and heating mode. When the system is in the mode, the whole system forms a refrigerating and heating simultaneous circulation system. As shown in fig. 2, first, the compressor 604 discharges high-temperature and high-pressure gas after compression, and the high-temperature and high-pressure gas is connected to the indoor condenser 601, and 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 communicates with the outlet 502 of the expansion valve 5 via the second inlet 501b of the expansion valve 5, and at this time, the expansion valve 5 functions as an expansion valve, and as a throttling element, the outlet 502 is low-temperature low-pressure liquid. The opening degree of the expansion valve 5 may be set to a certain opening degree according to actual demands, and the opening degree may be adjusted according to the amount of temperature acquisition data (i.e., compressor discharge temperature) of a pressure-temperature sensor installed at the outlet of the compressor 604. The outlet 502 of the expansion valve 5 is connected to the outdoor heat exchanger 605, the inlet of the outdoor heat exchanger 605 is low-temperature low-pressure liquid, and the outlet of the outdoor heat exchanger 605 is low-temperature low-pressure gas-liquid mixture by incomplete evaporation. At this time, the first on-off valve 610 is closed, the first expansion valve 609 is opened, the first expansion valve 609 is throttled once more as a throttle element, and the outlet of the first expansion valve 609 is a low-temperature low-pressure gas-liquid mixture. The outlet of the first expansion valve 609 is connected with the indoor evaporator 602, and the low-temperature low-pressure gas-liquid mixture evaporates in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, the liquid which has not evaporated 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 air in HVAC assembly 600 now flows through both indoor condenser 601 and indoor evaporator 602.

Mode four: and an outdoor heat exchanger defrost mode. As shown in fig. 2, first, a compressor 604 discharges high-temperature and high-pressure gas through compression, and is connected to an indoor condenser 601. At this time, the indoor condenser 601 flows only as a flow passage, and the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor condenser 601 communicates with the outlet 502 of the expansion valve 5 via the first inlet 501a of the expansion valve 5, and the expansion valve 5 functions as a switching valve and flows only as a flow passage, and the outlet 502 of the expansion valve 5 is still high-temperature and high-pressure gas. The outlet 502 of the expansion switch valve 5 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, heat is emitted to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the first on-off valve 610 is closed, the first expansion valve 609 is opened, the first expansion valve 609 serves as a throttling element for throttling, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the first expansion valve 609 may be given a certain opening degree according to actual demands, and the opening degree may be adjusted by calculating the superheat degree of the refrigerant at the outlet of the evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The outlet of the first expansion valve 609 is connected with the indoor evaporator 602, and the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, the liquid which has not evaporated 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 HVAC assembly 600 may not be in the wind at this time.

In the low temperature heating mode and the simultaneous cooling and heating mode, it is preferable that, as shown in fig. 3, a plate heat exchanger 612 is provided in the entire heat pump air conditioning system, and the plate heat exchanger 612 is also provided in the motor cooling system of the electric vehicle at the same time. In this way, the waste heat of the motor cooling system can be used to heat the air conditioning system refrigerant, thereby increasing the suction temperature and the suction capacity of the compressor 604. The plate heat exchanger 612 may be arranged arbitrarily upstream or downstream of the first on-off valve 610. In the embodiment shown in fig. 3, a plate heat exchanger 612 is arranged upstream of the first on-off valve 610, i.e. the refrigerant inlet 612a of the plate heat exchanger 612 communicates with the outlet of the outdoor heat exchanger 605, and the refrigerant outlet 612b of the plate heat exchanger 612 communicates with the inlet of the first on-off valve 610. In another embodiment (not shown), the plate heat exchanger 612 is arranged downstream of the first on-off valve 610, i.e. the refrigerant inlet 612a of the plate heat exchanger 612 communicates with the outlet of the first on-off valve 610 and the refrigerant outlet 612b of the plate heat exchanger 612 communicates with the inlet of the gas-liquid separator 611.

At the same time, the plate heat exchanger 612 is simultaneously arranged in the motor cooling system. As shown in fig. 3, the motor cooling system may include a motor, a motor radiator 613, and a water pump 614 in series with a plate heat exchanger 612 to form a circuit. In this way, the refrigerant can exchange heat with the cooling liquid in the motor cooling system through the plate heat exchanger 612.

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

Fig. 4 is a schematic structural view of a heat pump air conditioning system provided according to a second embodiment of the present disclosure. As shown in fig. 4, the heat pump air conditioning system may include the expansion switch valve 5, HVAC assembly 600, and damper mechanism described above. As shown in fig. 2 and 4, the heat pump air conditioning system provided by the second embodiment is similar to the heat pump air conditioning system provided by the first embodiment, and only differences between the two embodiments are described. Specifically, as shown in fig. 4, in the second embodiment provided in the present disclosure, the compressor 604 has a first outlet 604a and a second outlet 604b, wherein the first outlet 604a communicates with the outdoor heat exchanger 605 via the throttle passage of the indoor condenser 601 and the expansion switch valve 5 in sequence, and the second outlet 604b communicates with the outdoor heat exchanger 605 via the through-flow passage of the expansion switch valve 5, i.e., the outlet of the compressor 604 also communicates with the first inlet 501a of the expansion switch valve. In the first embodiment provided by the present disclosure, as shown in fig. 2, the compressor 604 has only one outlet and is in communication with the indoor condenser 601, and the outlet of the indoor condenser 601 is selectively in communication with the inlet of the outdoor heat exchanger 605 via the throttle or through-flow passage of the expansion valve 5. In other words, in the second embodiment, the refrigerant flowing out of the compressor 604 does not all pass through the indoor condenser 601, but selectively flows to the indoor condenser 601 via the first outlet 604a thereof or flows to the first inlet 501a of the expansion valve 5 via the second outlet 604b thereof. For example, when the heat pump air conditioning system is in a high temperature cooling mode or an outdoor heat exchanger defrost mode, the refrigerant may bypass the indoor condenser 601 and flow directly to the outdoor heat exchanger 605, in this way the total amount of refrigerant required for the heat pump air conditioning system to circulate can be reduced. In the first embodiment, the refrigerant flowing out of the outlet of the compressor 604 must flow entirely to the indoor condenser 601 and then to the outdoor heat exchanger 605 selectively via the throttle passage or the through-flow passage of the expansion valve 5.

In the present disclosure, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the compressor 604 either via the first through-flow branch or with the inlet of the indoor evaporator 602 via the first throttle branch. This communication may be achieved in a number of ways. For example, in one embodiment, as shown in fig. 4, a first on-off valve 610 is provided in the first through-flow path, and a first expansion valve 609 is provided in the first throttle path. Specifically, as shown in fig. 4, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the compressor 604 via a first on-off valve 610 to form a first through-flow branch, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via a first expansion valve 609 to form a first throttle branch. When the system is in the high temperature cooling mode, the first expansion valve 609 is on, the first on-off valve 610 is off, and the outlet of the outdoor heat exchanger 605 is in communication with the inlet of the indoor evaporator 602 via the first throttling branch. When the system is in a low temperature heating mode, the first switching valve 610 is turned on, the first expansion valve 609 is closed, and the outlet of the outdoor heat exchanger 605 is communicated with the inlet of the compressor 604 via the first through-flow branch.

Further, as shown in fig. 4, the heat pump air conditioning system may further include a gas-liquid separator 611 and a check valve 615, wherein an outlet of the indoor evaporator 602 is in communication with an inlet of the gas-liquid separator 611, an outlet of the outdoor heat exchanger 605 is in communication with an inlet of the gas-liquid separator 611 via a first through-flow branch, and an outlet of the gas-liquid separator 611 is in communication with an inlet of the compressor 604. In this way, the refrigerant flowing out through the indoor evaporator 602 or the first switching valve 610 may be first subjected to gas-liquid separation through the gas-liquid separator 611, and the separated gas may be returned to the compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 to damage the compressor 604, so that the service life of the compressor 604 may be prolonged, and the efficiency of the whole heat pump air conditioning system may be improved. The outlet of the indoor evaporator 602 communicates with the inlet of the gas-liquid separator 611 through a check valve 615. Here, the check valve 615 is provided to prevent the refrigerant from flowing back to the indoor evaporator 602 in a low temperature heating mode (described in detail below), affecting the heating effect.

Mode one: high temperature cooling mode. When the system is in this mode, the entire system forms a high temperature refrigeration cycle. As shown in fig. 4, first, the compressor 604 discharges high-temperature and high-pressure gas after compression, and the second outlet 604b of the compressor 604 communicates with the outlet 502 of the expansion valve 5 via the first inlet 501a of the expansion valve 5, and the expansion valve 5 functions as a switching valve and flows only as a flow passage, and the outlet 502 of the expansion valve 5 is still high-temperature and high-pressure gas. The outlet 502 of the expansion switch valve 5 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, heat is emitted to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the first on-off valve 610 is closed, the outlet of the outdoor heat exchanger 605 is connected to the first expansion valve 609, the first expansion valve 609 serves as a throttle member, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the first expansion valve 609 may be given a certain opening degree according to actual demands, and the opening degree may be adjusted by calculating the superheat degree of the refrigerant at the outlet of the evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The outlet of the first expansion valve 609 is connected to the inlet of the indoor evaporator 602, and the low-temperature low-pressure liquid evaporates in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The outlet of the indoor evaporator 602 is connected to the inlet of the check valve 615, the outlet of the check valve 615 is connected to the inlet of the gas-liquid separator 611, the liquid which is not evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. At this time, the flow direction of the air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 does not pass therethrough, and only flows as a refrigerant flow path.

Mode two: low temperature heating mode. When the system is in the mode, the whole system forms a low-temperature heating circulation system. As shown in fig. 4, first, the compressor 604 discharges high-temperature and high-pressure gas after compression, and the first outlet 604a of the compressor 604 communicates with the inlet of the indoor condenser 601, and at this time, the indoor condenser 601 has wind passing therethrough, and the high-temperature and high-pressure gas condenses 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 communicates with the outlet 502 of the expansion valve 5 via the second inlet 501b of the expansion valve 5, and at this time, the expansion valve 5 functions as an expansion valve, and as a throttling element, the outlet thereof is a low-temperature low-pressure liquid. The opening degree of the expansion valve 5 may be set to a certain opening degree according to actual demands, and the opening degree may be adjusted according to the amount of temperature acquisition data (i.e., compressor discharge temperature) of a pressure-temperature sensor installed at the outlet of the compressor 604. The outlet 502 of the expansion valve 5 is connected to the inlet of the outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature low-pressure gas. At this time, the first switching valve 610 is opened, the first expansion valve 609 is closed, the refrigerant directly enters the gas-liquid separator 611 without passing through the indoor evaporator 602, the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas is returned to the compressor 604, thereby forming a cycle. The air in HVAC assembly 600 now flows through both indoor condenser 601 and indoor evaporator 602.

Mode three: and simultaneously, a refrigerating and heating mode. When the system is in the mode, the whole system forms a refrigerating and heating simultaneous circulation system. As shown in fig. 4, the compressor 604 discharges high-temperature and high-pressure gas after compression, and the first outlet 604a of the compressor 604 is communicated with the inlet of the indoor condenser 601, at this time, the indoor condenser 601 has wind passing therethrough, 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 communicates with the outlet 502 of the expansion valve 5 via the second inlet 501b of the expansion valve 5, and at this time, the expansion valve 5 functions as an expansion valve, and as a throttling element, the outlet thereof is a low-temperature low-pressure liquid. The opening degree of the expansion valve 5 may be set to a certain opening degree according to actual demands, and the opening degree may be adjusted according to the amount of temperature acquisition data (i.e., compressor discharge temperature) of a pressure-temperature sensor installed at the outlet of the compressor 604. The outlet 502 of the expansion valve 5 is connected to the outdoor heat exchanger 605, the inlet of the outdoor heat exchanger 605 is low-temperature low-pressure liquid, and the outlet of the outdoor heat exchanger 605 is low-temperature low-pressure gas-liquid mixture by incomplete evaporation. At this time, the first on-off valve 610 is closed, the first expansion valve 609 is opened, the first expansion valve 609 is throttled once more as a throttle element, and the outlet of the first expansion valve 609 is a low-temperature low-pressure gas-liquid mixture. The outlet of the first expansion valve 609 is connected with the indoor evaporator 602, and the low-temperature low-pressure gas-liquid mixture evaporates in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, the liquid which has not evaporated 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 air in HVAC assembly 600 now flows through both indoor condenser 601 and indoor evaporator 602.

Mode four: and an outdoor heat exchanger defrost mode. As shown in fig. 4, first, the compressor 604 discharges high-temperature and high-pressure gas after compression, and the second outlet 604b of the compressor 604 communicates with the outlet 502 of the expansion valve 5 via the first inlet 501a of the expansion valve 5, and the expansion valve 5 functions as a switching valve and flows only as a flow passage, and the outlet 502 of the expansion valve 5 is still high-temperature and high-pressure gas. The outlet 502 of the expansion switch valve 5 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, heat is emitted to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the first on-off valve 610 is closed, the first expansion valve 609 is opened, the first expansion valve 609 serves as a throttling element for throttling, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the first expansion valve 609 may be given a certain opening degree according to actual demands, and the opening degree may be adjusted by calculating the superheat degree of the refrigerant at the outlet of the evaporator according to the pressure and temperature acquisition data of a pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The outlet of the first expansion valve 609 is connected with the indoor evaporator 602, and the outlet of the indoor evaporator 602 is low-temperature low-pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, the liquid which has not evaporated 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 HVAC assembly 600 may not be in the wind at this time.

In the low-temperature heating mode and the simultaneous cooling and heating mode, in order to improve heating capacity, it is preferable that a plate heat exchanger is provided in the entire heat pump air conditioning system, which is also provided in the motor cooling system of the electric vehicle at the same time. In this way, the waste heat of the motor cooling system can be used to heat the air conditioning system refrigerant, thereby increasing the suction temperature and the suction capacity of the compressor 604. The plate heat exchanger may be arranged arbitrarily upstream or downstream of the first on-off valve 610. Specifically, when the plate heat exchanger is disposed upstream of the first on-off valve 610, that is, the refrigerant inlet of the plate heat exchanger communicates with the outlet of the outdoor heat exchanger 605, the refrigerant outlet of the plate heat exchanger communicates with the inlet of the first on-off valve 610. When the plate heat exchanger is disposed downstream of the first on-off valve 610, i.e., the refrigerant inlet of the plate heat exchanger communicates with the outlet of the first on-off valve 610, the refrigerant outlet of the plate heat exchanger communicates with the inlet of the gas-liquid separator 611.

At the same time, the plate heat exchanger is simultaneously arranged in the motor cooling system. The motor cooling system may comprise a motor, a motor radiator and a water pump connected in series with the plate heat exchanger to form a circuit. In this way, the refrigerant can exchange heat with the cooling liquid in the motor cooling system through the plate heat exchanger.

In summary, the heat pump air conditioning system provided by the present disclosure can realize the defrosting function of the outdoor side heat exchanger for cooling and heating the vehicle air conditioning system without changing the circulation direction of the refrigerant, and can meet the requirements of simultaneous cooling and heating. In the bypass defrosting process of the outdoor heat exchanger, the heating requirement in the vehicle can be met. In addition, the heat pump air conditioning system disclosed by the invention only adopts one outdoor heat exchanger, so that the wind resistance of the front end module of the automobile can be reduced, the problems that the heating energy efficiency of the automobile heat pump air conditioning system of a pure electric automobile or a hybrid electric automobile without an engine waste heat circulation system in a pure electric mode is low, the requirements of defrosting and demisting regulations cannot be met, the installation is complex and the like are solved, and the effects of reducing energy consumption, simplifying the system structure and facilitating the pipeline arrangement are achieved. The heat pump air conditioning system provided by the disclosure has the characteristics of simple structure, so that mass production is easy.

As described above, in the present disclosure, the expansion valve 5 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 with the expansion valve. An example embodiment of the expansion valve 5 will be provided hereinafter.

As shown in fig. 5 to 10, the present disclosure provides an expansion switching valve, including a valve body 500, wherein the valve body 500 is formed with a first inlet 501a, a second inlet 501b, an outlet 502, and an internal flow passage communicating between the first inlet 501a, the second inlet 501b, and the outlet 502, on which a first valve body 503 and a second valve body 504 are installed, the first valve body 503 directly communicates or disconnects the first inlet 501a and the outlet 502, and the second valve body 504 communicates or disconnects the second inlet 501b and the outlet 502 through an orifice 505.

Here, the "direct communication" achieved by the first valve body 503 means that the coolant entering from the first inlet 501a of the valve body 500 can flow directly to the outlet 502 of the valve body 500 over the first valve body 503 without being affected by the internal flow passage, and the "disconnection" achieved by the first valve body 503 means that the coolant entering from the first inlet 501a of the valve body 500 cannot pass over the first valve body 503 and cannot flow to the outlet 502 of the valve body 500 through the internal flow passage. The "through orifice communication" achieved by the second spool 504 means that coolant entering from the second inlet 501b of the valve body 500 can flow to the outlet 502 of the valve body 500 past the second spool 504 through the orifice's throttle, while the "off communication" achieved by the second spool 504 means that coolant entering from the second inlet 501b of the valve body 500 cannot pass the second spool 504 and cannot flow to the outlet 502 of the valve body 500 through the orifice 505.

In other words, the expansion valve has at least a first operating position, in which the first spool 503 causes the first inlet 501a and the outlet 502 to be in direct communication, a second operating position, and a third operating position, in which the second spool 504 causes the second inlet 501b and the outlet 502 to be out of communication; in the second operating position, the first spool 503 disconnects the first inlet 501a from the outlet 502 and the second spool 504 connects the second inlet 501b to the outlet 502 through the orifice 505; in the third operating position, the first spool 503 disconnects the first inlet 501a from the outlet 502 and the second spool 504 disconnects the second inlet 501b from the outlet 502.

In this way, by controlling the first spool 503 and the second spool 504, the expansion switch valve of the present disclosure can achieve at least three states in total of coolant entering from the first inlet 501a and the second inlet 501 b. Namely, 1) an off state; 2) A direct communication state across the first spool 503; and 3) throttled communication across the second spool 504.

The high-temperature and high-pressure liquid refrigerant can become a low-temperature and low-pressure vaporous hydraulic refrigerant after passing through the throttle hole 505, which can create conditions for the evaporation of the refrigerant, namely, the cross-sectional area of the throttle hole 505 is smaller than that of the first inlet 501a, the second inlet 501b and the outlet 502, and the opening degree of the throttle hole 505 can be adjusted by controlling the second valve core so as to control the flow rate flowing through the throttle hole 505, prevent the insufficient refrigeration caused by the too small refrigerant and prevent the liquid impact phenomenon caused by the too large refrigerant. That is, the cooperation of the second spool 504 and the valve body 500 may cause the expansion valve to have the function of an expansion valve.

In this way, the first valve core 503 and the second valve core 504 are installed on the internal flow channel of the same valve body 500 with the first inlet 501a, the second inlet 501b and the outlet 502, so as to realize the on-off control or throttle control function of the internal flow channel, and the expansion switch valve has a simple structure, is easy to produce and install, and can reduce the refrigerant filling amount of the whole heat pump system, reduce the cost, simplify the pipeline connection and be more beneficial to the oil return of the heat pump system when the expansion switch valve is applied to the heat pump system.

As an exemplary internal mounting structure of the valve body 500, as shown in fig. 5 to 10, 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 the first valve body 503 is mounted in the first valve housing 511, a second electromagnetic driving portion 522 for driving the second valve body 504 is mounted in the second valve housing 512, the first valve body 503 extends from the first valve housing 511 to the internal flow passage in the valve seat 510, and the second valve body 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 in the internal flow channel can be conveniently controlled by controlling the on/off of the first electromagnetic driving portion 521, such as an electromagnetic coil, so as to control the inlet 501 and the outlet 502 to be directly connected or disconnected; the position of the second spool 504 in the internal flow passage can be conveniently controlled by controlling the on-off of the second electromagnetic drive portion 522, e.g., a solenoid, to control whether the inlet 501 and the outlet 502 communicate with the orifice 505. In other words, the electronic expansion valve and the electromagnetic valve are installed in parallel in the valve body 500, so that the automatic control of the on-off and/or the 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 valve in all directions, the expansion valve is prevented from interfering with the connection of different pipelines, the valve seat 510 is formed into a polyhedral structure, the first valve housing 511 and the second valve housing 512 are arranged on the same surface of the polyhedral structure, the first inlet 501a and the second inlet 501b are arranged on the same surface of the polyhedral structure, and the first valve housing 511, the first inlet 501a and the outlet 502 are respectively arranged on different surfaces of the polyhedral structure, wherein the installation directions of the first valve housing 511 and the second valve housing 512 are parallel to each other, and the opening directions of the first inlet 501a and the outlet 502 are parallel to each other. Thus, the inlet pipeline and the outlet pipeline can be connected to different surfaces of the polyhedral structure, and the problem that the pipeline is arranged in disorder and entangled can be avoided.

As a typical internal structure of the electromagnetic expansion valve, as shown in fig. 7 to 10, the internal flow passage includes a first flow passage 506 and a second flow passage 507 communicating with a first inlet 501a and a second inlet 501b, respectively, a first valve port 516 cooperating with a first spool 503 is formed on the first flow passage 506, an orifice 505 is formed on the second flow passage 507 to form a second valve port 517 cooperating with a 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 function of opening or closing the first valve port 516 by changing the position of the first spool 503 in the internal flow passage, and thereby controlling the interruption or conduction of the first flow passage 506 that communicates the first inlet 501a and the outlet 502, can be achieved as described above. Similarly, the second valve element 504 is changed in position in the internal flow passage to close or open the second valve port 517, and the second flow passage 507 that communicates the second inlet 501b and the outlet 522 is controlled to be blocked or opened, so that the throttle function of the electronic expansion valve can be realized.

The first flow channel 506 may communicate with the first inlet 501a and the outlet 502 in any suitable arrangement, the second flow channel 507 may communicate with the second inlet 501b and the outlet 502 in any suitable arrangement, and in order to reduce the overall occupied space of the valve body, as shown in fig. 7 and 8, the second flow channel 507 is perpendicular to the outlet 502, the first flow channel 506 is formed as a first through hole 526 parallel to the second flow channel 507, the second inlet 501b communicates with the second flow channel 507 through a second through hole 527 opened on a sidewall of the second flow channel 507, and the first through hole 526 and the second through hole 527 communicate with the first inlet 501a and the second inlet 501b, respectively.

In order to shorten the total length of the internal flow channel to the greatest extent, as shown in fig. 7 and 8, the first through hole 526 and the second through hole 507 are respectively communicated with the outlet 502 through the third through hole 508 and the fourth through hole 509, and the third through hole 508 and the fourth through hole 509 are coaxially and oppositely opened and are mutually perpendicular to the outlet 502. In this way, the total length of the internal flow passage within the valve body 500 can be ensured to be minimized, thereby ensuring that the refrigerant can rapidly flow through the expansion valve.

In order to facilitate the connection of the first inlet, the second inlet and the outlet of the valve body 500 to the pipe joints of different pipes, respectively, as shown in fig. 5 to 10, the first inlet 501a and the second inlet 501b are opened on the same side of the valve body 500 in parallel with each other, and the outlet 502 is parallel to the first inlet 501a and the second inlet 501b, respectively. In this way, pipe joints of pipes located upstream and downstream of the valve body 500 can be respectively mounted to opposite sides of the valve body 500, and the mess and entanglement of different pipe arrangements can be prevented.

Further, to minimize the total length of the internal flow passage, as shown in fig. 7 and 8, the outlet 502 is provided between the first spool 503 and the second spool 504.

Here, the outlet 502 is disposed between the first spool 503 and the second spool 504, and represents a projection of the outlet 502 on a plane formed by the first spool 503 and the second spool 504, and is located between the first spool 503 and the second spool 504.

The first spool 503 and the second spool 504 may be disposed at any suitable angle, and in one exemplary embodiment, for ease of placement, as shown in fig. 7 and 8, the first spool 503 and the second spool 504 are parallel to each other.

As shown in fig. 7 and 8, to facilitate closing and opening of the first valve port 516, the first valve spool 503 is coaxially disposed with the first valve port 516 in a moving direction to selectively block or unblock the first valve port 516.

To facilitate the closing and opening of the second valve port 517, as shown in fig. 7 and 8, the second valve spool 504 is disposed coaxially with the second valve port 517 in the moving direction to selectively block or unblock the second valve port 517.

Further, as shown in fig. 7 and 8, to ensure the reliability of the first valve core 503 blocking the first flow channel 506, the first valve core 503 may include a first valve stem 513 and a first plug 523 connected to an end of the first valve stem 513, where the first plug 523 is used to seal against an end surface of the first valve port 516 to block the first flow channel 506.

To facilitate adjusting the opening size of the orifice 505 of the expansion valve, as shown in fig. 7 and 8, the second valve body 504 includes a second valve stem 514, an end portion of the second valve stem 514 is formed in a cone-shaped head structure, and the second valve port 517 is formed in a cone-shaped hole structure to be fitted with the cone-shaped head structure.

The opening degree of the orifice 505 of the expansion valve may be adjusted by the up-and-down movement of the second spool 504, and the up-and-down movement of the second spool 504 may be adjusted by the second electromagnetic driving portion 522. If the opening of the orifice 505 of the expansion valve is zero, as shown in fig. 8, the second valve element 504 is at the lowest position, and the second valve element 504 blocks the second valve port 517, so that the refrigerant cannot pass through the orifice 505, i.e., the second valve port 517 at all; if the expansion valve orifice 505 has an opening degree, as shown in fig. 9, a gap is provided between the tapered head structure of the end portion of the second valve body 504 and the orifice 505, and the refrigerant flows to the outlet 502 after being throttled. If the throttle opening of the expansion valve needs to be increased, the second electromagnetic driving portion 522 can be controlled to enable the second valve element 504 to move upwards, so that the conical head structure is far away from the throttle hole 505, and the increase of the throttle hole 505 opening is achieved; conversely, when it is necessary to reduce the opening degree of the orifice 505 of the expansion valve, the second valve element 504 may be driven to move downward.

When the electromagnetic valve function of the expansion valve is only needed, that is, when the expansion valve is located at the first working position, as shown in fig. 7 and 9, the first electromagnetic driving portion 521 is powered off, the first plug 523 of the first valve core 503 is separated from the first valve port 516, and the first valve port 516 is in an open state; the second electromagnetic driving portion 522 is energized, the second valve body 504 is at the lowest position, the second valve body 504 closes the orifice 505, and the refrigerant cannot flow from the second inlet 501b to the outlet 502 through the second flow passage 507, but can flow from the first inlet 501a into the outlet 502 through the first valve port 516, the first through hole 526, and the third through hole 508 in this order.

The dashed lines with arrows in fig. 7 and 9 represent the flow path and the direction of the refrigerant when the solenoid valve function is used.

When only the electronic expansion valve function of the expansion valve is needed, that is, when the expansion valve is located at the second working position, as shown in fig. 8 and 10, the first electromagnetic driving portion 521 is electrified, the first plug 523 of the first valve core 503 plugs the first valve port 516, and the first valve port 516 is in a closed state; the second electromagnetic driving portion 522 is de-energized, the second valve body 504 is at the highest position, the second valve body 504 is separated from the orifice 505, the refrigerant cannot flow from the first inlet 501a to the outlet 502 through the first flow passage 506, the refrigerant can only flow from the second inlet 501b into the outlet 502 through the second through hole 527, the orifice 505 and the fourth through hole 509 in this order, and the second valve body 504 can be moved up and down to adjust the opening degree of the orifice 505.

The dashed lines with arrows in fig. 8 and 10 represent the flow path and the direction of the refrigerant when the electronic expansion valve function is used.

When the electromagnetic valve function and the electronic expansion valve function of the expansion valve are not needed to be used simultaneously, that is, when the expansion valve is located at the third working position, the first electromagnetic driving portion 521 is electrified, the first plug 523 of the first valve core 503 plugs the first valve port 516, and the first valve port 516 is in a closed state; the second electromagnetic driving portion 522 is energized, the second spool 504 is at the lowest position, the second spool 504 closes the orifice 505, and the refrigerant cannot flow from the first inlet 501a or the second inlet 501b to the outlet 502, that is, the internal flow passage is in a shut-off state.

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

The disclosure also provides an electric automobile, comprising the heat pump air conditioning system provided by the 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 have been described in detail above with reference to the accompanying drawings, but the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solutions of the present disclosure within the scope of the technical concept of the present disclosure, and all the simple modifications belong to the protection scope of the present disclosure.

In addition, the specific features described in the foregoing embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, the present disclosure does not further describe various possible combinations.

Moreover, any combination between the various embodiments of the present disclosure is possible as long as it does not depart from the spirit of the present disclosure, which should also be construed as the disclosure of the present disclosure.

Claims

1. A heat pump air conditioning system, characterized by comprising a throttle mechanism, a compressor (604), an indoor condenser (601), an indoor evaporator (602), an outdoor heat exchanger (605) and an expansion switch valve (5), wherein the throttle mechanism is used for conducting an air channel leading to the indoor evaporator (602) and the indoor condenser (601);

the expansion switch valve (5) comprises a valve body (500), wherein a first inlet (501 a), a second inlet (501 b), an outlet (502) and an internal flow passage communicated between the first inlet (501 a), the second inlet (501 b) and the outlet (502) are formed on the valve body (500), a first valve core (503) and a second valve core (504) are arranged on the internal flow passage, the first valve core (503) enables the first inlet (501 a) and the outlet (502) to be directly communicated or disconnected, the second valve core (504) enables the second inlet (501 b) and the outlet (502) to be communicated or disconnected through an orifice (505),

the outlet of the compressor (604) is communicated with the inlet of the indoor condenser (601), the outlet of the indoor condenser (601) is communicated with the second inlet (501 b) of the expansion switch valve (5), the outlet (502) of the expansion switch valve (5) is communicated with the inlet of the outdoor heat exchanger (605), the outlet of the outdoor heat exchanger (605) is selectively communicated with the inlet of the compressor (604) via a first through-flow branch or is communicated with the inlet of the indoor evaporator (602) via a first throttling branch, the outlet of the indoor evaporator (602) is communicated with the inlet of the compressor (604), and the outlet of the compressor (604) or the outlet of the indoor condenser (601) is also communicated with the first inlet (501 a) of the expansion switch valve (5).

2. The heat pump air conditioning system according to claim 1, characterized in that a first on-off valve (610) is provided on the first through-flow branch, and a first expansion valve (609) is provided on the first throttle branch.

3. The heat pump air conditioning system according to claim 1, characterized in that the outlet of the indoor evaporator (602) communicates with the inlet of the compressor (604) via a one-way valve (615).

4. The heat pump air conditioning system according to claim 1, characterized in that the heat pump air conditioning system is applied to an electric vehicle, and a plate heat exchanger (612) is further arranged on the first through-flow branch, and the plate heat exchanger (612) is simultaneously arranged in a motor cooling system of the electric vehicle.

5. The heat pump air conditioning system according to claim 4, characterized in that a first on-off valve (610) is provided on the first through-flow branch, a refrigerant inlet (612 a) of the plate heat exchanger (612) communicates with an outlet of the outdoor heat exchanger (605), and a refrigerant outlet (612 b) of the plate heat exchanger (612) communicates with an inlet of the first on-off valve (610).

6. The heat pump air conditioning system according to claim 4, characterized in that the motor cooling system comprises a motor, a motor radiator (613) and a water pump (614) connected in series with the plate heat exchanger (612) to form a circuit.

7. The heat pump air conditioning system according to claim 1, further comprising a gas-liquid separator (611), wherein an outlet of the indoor evaporator (602) is in communication with an inlet of the gas-liquid separator (611), wherein an outlet of the outdoor heat exchanger (605) is in communication with an inlet of the gas-liquid separator (611) via the first through-flow branch, and wherein an outlet of the gas-liquid separator (611) is in communication with an inlet of the compressor (604).

8. The heat pump air conditioning system according to claim 1, wherein the internal flow passage includes a first flow passage (506) and a second flow passage (507) that communicate with the first inlet (501 a) and the second inlet (501 b), respectively, the first flow passage (506) has a first valve port (516) formed thereon that mates with the first spool (503), the orifice (505) is formed on the second flow passage (507) to form a second valve port (517) that mates with the second spool (504), 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).

9. The heat pump air conditioning system according to claim 8, characterized in that the second flow passage (507) is perpendicular to the outlet (502), the first flow passage (506) is formed as a first through hole (526) parallel to the second flow passage (507), the second inlet (501 b) communicates with the second flow passage (507) through a second through hole (527) opened on a side wall of the second flow passage (507), and the first through hole (526) and the second through hole (527) communicate with the first inlet (501 a) and the second inlet (501 b), respectively.

10. The heat pump air conditioning system according to claim 9, characterized in that the first through hole (526) and the second flow channel (507) are respectively communicated with the outlet (502) through a third through hole (508) and a fourth through hole (509), and the third through hole (508) and the fourth through hole (509) are coaxially and oppositely opened and are mutually perpendicular to the outlet (502).

11. The heat pump air conditioning system according to any of claims 1 or 8-10, characterized in that the first inlet (501 a) and the second inlet (501 b) are open parallel to each other on the same side of the valve body (500), the outlet (502) being parallel to the first inlet (501 a) and the second inlet (501 b), respectively.

12. The heat pump air conditioning system according to claim 11, wherein the outlet (502) is provided between the first spool (503) and the second spool (504).

13. The heat pump air conditioning system according to any of claims 8-10, wherein the first valve spool (503) is coaxially arranged with the first valve port (516) in the direction of movement to selectively block or unblock the first valve port (516).

14. The heat pump air conditioning system according to any of claims 8-10, wherein the second valve spool (504) is coaxially arranged with the second valve port (517) in the direction of movement to selectively block or unblock the second valve port (517).

15. The heat pump air conditioning system according to claim 13, characterized in that the first valve spool (503) comprises a first valve stem (513) and a first plug (523) connected to an end of the first valve stem (513), the first plug (523) being adapted to be sealingly pressed against an end face of the first valve port (516) to close the first flow channel (506).

16. The heat pump air conditioning system according to claim 14, wherein the second valve spool (504) includes a second valve stem (514), an end of the second valve stem (514) being formed as a conical head structure, and the second valve port (517) being formed as a conical bore structure that mates with the conical head structure.

17. The heat pump air conditioning system according to claim 1, characterized in that the valve body (500) includes a valve seat (510) forming the 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 the first valve core (503) being mounted in the first valve housing (511), a second electromagnetic driving portion (522) for driving the second valve core (504) being mounted in the second valve housing (512), the first valve core (503) extending from the first valve housing (511) to the internal flow passage in the valve seat (510), the second valve core (504) extending from the second valve housing (512) to the internal flow passage in the valve seat (510).

18. The heat pump air conditioning system according to claim 17, wherein the valve seat (510) is formed in a polyhedral structure, the first valve housing (511) and the second valve housing (512) are disposed on the same surface of the polyhedral structure, the first inlet (501 a) and the second inlet (501 b) are disposed on the same surface of the polyhedral structure, and the first valve housing (511), the first inlet (501 a) and the outlet (502) are disposed on different surfaces of the polyhedral structure, respectively, wherein the mounting directions of the first valve housing (511) and the second valve housing (512) are parallel to each other, and the opening directions of the first inlet (501 a) and the outlet (502) are parallel to each other.

19. An electric vehicle comprising a heat pump air conditioning system according to any one of claims 1-18.