CN108248332B

CN108248332B - Heat pump air conditioning system and electric automobile

Info

Publication number: CN108248332B
Application number: CN201611248326.1A
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: 2023-10-17
Anticipated expiration: 2036-12-29
Also published as: CN108248332A

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 two expansion switch valves, 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 flow passage opening of the first expansion switch valve, the third flow passage opening of the first expansion switch valve is communicated with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger is communicated with the third flow passage opening of the second expansion switch valve, the first flow passage opening of the second expansion switch valve is communicated with the inlet of the compressor, the second flow passage opening of the second expansion switch valve is communicated with the inlet of the indoor evaporator, 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 flow passage opening of the first expansion switch valve. Therefore, the heating energy efficiency can be improved, the requirements of defrosting and demisting regulations can be met, the installation is convenient, the pipeline connection is simplified, the oil return effect of the compressor is convenient, and the like.

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 invention 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 two expansion switching valves, each of which includes a valve body on which a first flow passage, a second flow passage, a third flow passage, and an internal flow passage communicating between the first flow passage, the second flow passage, and the third flow passage are formed, a first valve element and a second valve element are installed on the internal flow passage, the first valve element causes the first flow passage and the third flow passage to be in direct communication or to be out of communication, the second valve element causes the second flow passage and the third flow passage to be in communication or to be out of communication through an orifice, the two expansion switching valves include a first expansion switching valve and a second expansion switching valve, an outlet of the compressor is in communication with an inlet of the indoor condenser, an outlet of the first expansion switching valve communicates with a second flow passage, an outlet of the first expansion switching valve communicates with an outlet of the second expansion switching valve, an outlet of the first expansion switching valve communicates with an inlet of the second flow passage, an outlet of the second expansion switching valve communicates with an outlet of the second flow passage, and an outlet of the second expansion switching valve.

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 a plate heat exchanger is further arranged between the first flow passage of the second expansion switch valve and the compressor, and the plate heat exchanger is simultaneously arranged in a motor cooling system of the electric automobile.

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, wherein the outlet of the indoor evaporator and the first flow passage of the second expansion switch valve are respectively communicated with the inlet of the gas-liquid separator, and the outlet of the gas-liquid separator is communicated with the inlet of the compressor.

Optionally, the third flow orifice of each expansion valve is disposed between the first valve spool and the second valve spool.

Optionally, the internal flow passage of each expansion valve includes a first flow passage and a second flow passage which are respectively communicated with the first flow passage and the second flow passage, a first valve port matched with the first valve core is formed on the first flow passage, the orifice is formed on the second flow passage so as to form a second valve port matched with the second valve core, and the first flow passage and the second flow passage are intersected at the downstream of the second valve port and are communicated with the third flow passage.

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

Optionally, the first valve core of each expansion switch valve 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 first valve core of each expansion switch valve comprises a first valve rod and a first plug connected to the end of the first valve rod, and the first plug is used for sealing and pressing against the end face of the first valve port to seal the first flow channel.

Optionally, the second valve core of each expansion switch valve 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 second valve element of each expansion valve comprises a second valve stem, an end of which is formed as a conical head structure, and the second valve port is formed as a conical bore structure cooperating with the conical head structure.

Optionally, the second flow passage of the first expansion valve is perpendicular to the third flow passage, the first flow passage of the first expansion valve is formed as a first through hole parallel to the second flow passage of the first expansion valve, the second flow passage of the first expansion valve is communicated with the second flow passage of the first expansion valve through a second through hole formed on the side wall of the second flow passage of the first expansion valve, and the first through hole and the second through hole of the first expansion valve are respectively communicated with the first flow passage and the second flow passage of the first expansion valve.

Optionally, the first through hole and the second flow passage of the first expansion switch valve are respectively communicated with the third flow passage opening of the first expansion switch valve through the third through hole and the fourth through hole of the first expansion switch valve, and the third through hole and the fourth through hole of the first expansion switch valve are coaxially and oppositely opened and are mutually perpendicular to the third flow passage opening of the first expansion switch valve.

Optionally, the first flow passage opening and the second flow passage opening of the first expansion switch valve are parallel to each other and are arranged on the same side of the valve body of the first expansion switch valve, and the third flow passage opening of the first expansion switch valve is parallel to the first flow passage opening and the second flow passage opening of the first expansion switch valve respectively.

Optionally, the second flow passage of the second expansion valve is opened in the same direction as the second flow passage, the first flow passage of the second expansion valve is opened in the same direction as the first flow passage, and is formed as a first through hole parallel to the second flow passage of the second expansion valve, the third flow passage of the second expansion valve is communicated with the second flow passage of the second expansion valve through a second through hole opened on the side wall of the second flow passage of the second expansion valve, and the first through hole and the second through hole of the second expansion valve are respectively communicated with the third flow passage of the second expansion valve.

Optionally, the third flow passage opening of the second expansion switch valve is communicated with the first through hole of the second expansion switch valve through the third through hole of the second expansion switch valve, the third flow passage opening of the second expansion switch valve is communicated with the second through hole of the second expansion switch valve through the fourth through hole of the second expansion switch valve, the third through hole of the second expansion switch valve, the fourth through hole of the second expansion switch valve and the second through hole of the second expansion switch valve are coaxially arranged, and the third through hole of the second expansion switch valve is opened with the fourth through hole Kong Fanxiang and is perpendicular to the first through hole of the second expansion switch valve.

Optionally, the first flow passage opening and the second flow passage opening of the second expansion switch valve are parallel to each other and are arranged on the same side of the valve body of the second expansion switch valve, and the third flow passage opening of the second expansion switch valve is perpendicular to the first flow passage opening and the second flow passage opening of the second expansion switch valve respectively.

Optionally, the valve body of each expansion valve 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 portion for driving the first valve core is mounted in the first valve housing, a second electromagnetic driving portion 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 of the first expansion valve is formed as a polyhedral structure, the first valve casing and the second valve casing of the first expansion valve are disposed on the same surface of the polyhedral structure, the first flow passage opening and the second flow passage opening of the first expansion valve are disposed on the same surface of the polyhedral structure, and the first valve casing, the first flow passage opening and the third flow passage opening of the first expansion valve are disposed on different surfaces of the polyhedral structure, wherein the mounting directions of the first valve casing and the second valve casing of the first expansion valve are parallel to each other, and the opening directions of the first flow passage opening and the third flow passage opening of the first expansion valve are parallel to each other.

Optionally, the valve seat of the second expansion valve is formed as a polyhedral structure, the first valve casing and the second valve casing of the second expansion valve are disposed on the same surface of the polyhedral structure, the first flow passage opening and the second flow passage opening of the second expansion valve are disposed on the same surface of the polyhedral structure, and the first valve casing, the first flow passage opening and the third flow passage opening of the second expansion valve are disposed on different surfaces of the polyhedral structure, wherein the mounting directions of the first valve casing and the second valve casing of the second expansion valve are parallel to each other, and the opening directions of the first flow passage opening and the third flow passage opening of the second expansion valve are perpendicular 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 first expansion switch valve and the second expansion switch valve in the heat pump air conditioning system, the pipeline connection can be greatly 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 a first expansion valve according to an exemplary embodiment of the present disclosure in one direction;

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

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

FIG. 8 is another schematic cross-sectional view of a first 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 a first expansion valve provided in accordance with an exemplary embodiment of the present disclosure, wherein the first valve port is in an open state;

FIG. 10 is a second internal schematic diagram of a first expansion valve provided in accordance with an exemplary embodiment of the present disclosure, wherein the second valve port is in an open state;

fig. 11 is a schematic perspective view of a second expansion valve according to an exemplary embodiment of the present disclosure in one direction;

fig. 12 is a schematic perspective view of a second expansion valve according to an exemplary embodiment of the present disclosure in another direction;

FIG. 13 is a schematic cross-sectional view of a second expansion valve according to an exemplary embodiment of the present disclosure, wherein the first port is in an open state and the second port is in a closed state;

FIG. 14 is another schematic cross-sectional view of a second expansion valve provided in accordance with 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. 15 is a first internal schematic view of a second expansion valve provided in accordance with an exemplary embodiment of the present disclosure, wherein the first valve port is in an open state;

fig. 16 is a second internal structural schematic diagram of a second 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 one 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 further includes a first expansion switch valve 1, a second expansion switch valve 2, 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 flow passage port 10b of the first expansion valve 1, the third flow passage port 10c of the first expansion valve 1 communicates with the inlet of the outdoor heat exchanger 605, the outlet of the outdoor heat exchanger 605 communicates with the third flow passage port 20c of the second expansion valve 2, the first flow passage port 20a of the second expansion valve 2 communicates with the inlet of the compressor 604, the second flow passage port 20b of the second expansion valve 2 communicates with the inlet of the indoor evaporator 602, 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 flow passage port 10a of the first expansion valve 1. In other words, the outlet of the outdoor heat exchanger 605 selectively communicates with the inlet of the outdoor heat exchanger 605 via the through flow passage or the throttle flow passage of the first expansion valve 1.

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.

The "first fluid passage opening", "second fluid passage opening" and "third fluid passage opening" mentioned above refer to the end of the internal flow passage of the expansion valve, and may be used for connection to a pipe, for example, the "first fluid passage opening", "second fluid passage opening" and "third fluid passage opening" may be the inlet or the outlet of the expansion valve.

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. 3, 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 and the first flow passage port 20a of the second expansion valve 2 are respectively communicated with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 is communicated with an inlet of the compressor 604. In this way, the refrigerant flowing out through the first flow port 20a of the indoor evaporator 602 or the second expansion valve 2 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 entire 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 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 third flow passage 10c of the first expansion valve 1 via the first flow passage 10a of the first expansion valve 1, and the first expansion valve 1 functions as a switching valve and flows only as a flow passage, and the third flow passage 10c of the first expansion valve 1 is still high-temperature and high-pressure gas. The third channel port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, and the heat is dissipated to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c communicates with the second flow passage port 20b, the second expansion valve 2 serves as a throttling element for throttling, and the outlet is a low-temperature low-pressure liquid. The second expansion valve 2 may be provided with 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 based on 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 second fluid passage port 20b of the second expansion valve 2 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 third flow passage port 10c of the first expansion valve 1 via the second flow passage port 10b of the first expansion valve 1, and at this time, the first expansion valve 1 functions as an expansion valve, as a throttling element, and the outlet thereof is a low-temperature low-pressure liquid. The opening degree of the first expansion valve 1 may be set to a certain opening degree according to actual demands, and this 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 third flow passage port 10c of the first expansion valve 1 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 outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c is connected to the first flow passage port 20a, 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 third flow passage port 10c of the first expansion valve 1 via the second flow passage port 10b of the first expansion valve 1, and at this time, the first expansion valve 1 functions as an expansion valve, as a throttling element, and as a low-temperature low-pressure liquid. The opening degree of the first expansion valve 1 may be set to a certain opening degree according to actual demands, and this 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 third flow passage port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, and the outlet of the outdoor heat exchanger 605 is a low-temperature low-pressure liquid, and the outlet thereof is a low-temperature low-pressure gas-liquid mixture by incomplete evaporation. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c communicates with the second flow passage port 20b of the second expansion valve 2, the second expansion valve 2 is throttled once more as a throttle element, and the outlet of the second flow passage port 20b of the second expansion valve 2 is a low-temperature low-pressure gas-liquid mixture. The second fluid passage port 20b of the second expansion valve 2 is connected to the indoor evaporator 602, and the low-temperature and low-pressure liquid evaporates 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 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 third flow passage 10c of the first expansion valve 1 via the first flow passage 10a of the first expansion valve 1, and the first expansion valve 1 functions as a switching valve and flows only as a flow passage, and the third flow passage 10c of the first expansion valve 1 is still high-temperature and high-pressure gas. The third channel port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, and the heat is dissipated to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c communicates with the second flow passage port 20b of the second expansion valve 2, the second expansion valve 2 serves as a throttle element, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the second expansion valve 2 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 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. The outlet of the second flow passage opening 20b of the second expansion valve 2 is connected to 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. A plate heat exchanger 612 may be provided between the first flow port 20a of the second expansion valve 2 and the compressor 604, i.e. the refrigerant inlet 612a of the plate heat exchanger 612 communicates with the first flow port 10a of the second expansion valve, 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 first heat pump air conditioning system provided in the present disclosure, various refrigerants such as R134a, R410a, R32, R290 and the like may 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, which may include the first expansion switch valve 1, the second expansion switch valve 2, the HVAC assembly 600, and the damper mechanism described above, as shown in fig. 4. 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 indoor condenser 601 and the throttle passage of the first expansion switching valve 1 in sequence, and the second outlet 604b communicates with the outdoor heat exchanger 605 via the through-flow passage of the first expansion switching valve 1, that is, the outlet of the compressor 604 also communicates with the first flow passage 10a of the first expansion switching valve 1. In the first embodiment provided in 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 flow passage or the through flow passage of the first expansion valve 1. In other words, in the second embodiment, not all of the refrigerant flowing out of the compressor 604 passes through the indoor condenser 601, but flows selectively to the indoor condenser 601 via the first outlet 604a thereof or flows to the first expansion valve 1 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 indoor condenser 601 must flow entirely to the indoor condenser 601 and then flow to the outdoor heat exchanger 605 selectively via the throttle passage or the through-flow passage of the first expansion valve 1.

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 and the first flow passage port 20a of the second expansion valve 2 are respectively communicated with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 is communicated with an inlet of the compressor 604. In this way, the refrigerant flowing out through the first flow port 20a of the indoor evaporator 602 or the second expansion valve 2 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 entire 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 following will take fig. 4 as an example to describe the circulation process and principle of the heat pump air conditioning system provided in the present disclosure in different operation modes.

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 third flow passage 10c of the first expansion valve 1 via the first flow passage 10a of the first expansion valve 1, and at this time, the first expansion valve 1 functions as a switching valve and flows only as a flow passage, and at this time, the third flow passage 10c of the first expansion valve 1 is still high-temperature and high-pressure gas. The third channel port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, and the heat is dissipated to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c communicates with the second flow passage port 20b, the second expansion valve 2 serves as a throttling element for throttling, and the outlet is a low-temperature low-pressure liquid. The second expansion valve 2 may be provided with 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 based on 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 second fluid passage port 20b of the second expansion valve 2 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 third flow passage port 10c of the first expansion valve 1 via the second flow passage port 10b of the first expansion valve 1, and at this time, the first expansion valve 1 functions as an expansion valve, as a throttling element, and the outlet thereof is a low-temperature low-pressure liquid. The opening degree of the first expansion valve 1 may be set to a certain opening degree according to actual demands, and this 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 third flow passage port 10c of the first expansion valve 1 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 outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c is connected to the first flow passage port 20a, the first flow passage port 20a is connected to the gas-liquid separator 611, 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, 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 third flow passage port 10c of the first expansion valve 1 via the second flow passage port 10b of the first expansion valve 1, and at this time, the first expansion valve 1 functions as an expansion valve, as a throttling element, and as a low-temperature low-pressure liquid. The opening degree of the first expansion valve 1 may be set to a certain opening degree according to actual demands, and this 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 third flow passage port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, and the outlet of the outdoor heat exchanger 605 is a low-temperature low-pressure liquid, and the outlet thereof is a low-temperature low-pressure gas-liquid mixture by incomplete evaporation. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage port 20c communicates with the second flow passage port 20b of the second expansion valve 2, the second expansion valve 2 is throttled once more as a throttle element, and the outlet of the second flow passage port 20b of the second expansion valve 2 is a low-temperature low-pressure gas-liquid mixture. The second fluid passage port 20b of the second expansion valve 2 is connected to the indoor evaporator 602, and the low-temperature and low-pressure liquid evaporates 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 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 third flow passage 10c of the first expansion valve 1 via the first flow passage 10a of the first expansion valve 1, and at this time, the first expansion valve 1 functions as a switching valve and flows only as a flow passage, and at this time, the third flow passage 10c of the first expansion valve 1 is still high-temperature and high-pressure gas. The third channel port 10c of the first expansion valve 1 is connected to the outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with the outdoor air, and the heat is dissipated to the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the outlet of the outdoor heat exchanger 605 is connected to the third flow passage port 20c of the second expansion valve 2, the third flow passage cry 20c is connected to the second flow passage port 20b of the second expansion valve 2, the second expansion valve 2 serves as a throttle element, and the outlet thereof is low-temperature low-pressure liquid. The opening degree of the second expansion valve 2 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 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. The outlet of the second flow passage opening 20b of the second expansion valve 2 is connected to 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 in the simultaneous cooling and heating mode, it is preferable that a plate heat exchanger (not shown) which is also provided in a motor cooling system of the electric vehicle is provided in the entire heat pump air conditioning system in order to improve heating capacity. 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. A plate heat exchanger may be provided between the first flow port 20a of the second expansion valve 2 and the compressor 604, i.e., the refrigerant inlet of the plate heat exchanger communicates with the first flow port 10a of the second expansion valve, and 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 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 with the expansion valve. Hereinafter, an example embodiment of the first expansion switching valve 1 and the second expansion switching valve 2 will be described in order.

[ first expansion valve 1]

As shown in fig. 5 to 10, the present disclosure provides an expansion switching valve, including a valve body 10, wherein the valve body 10 is formed with a first flow passage port 10a, a second flow passage port 10b, a third flow passage port 10c, and an internal flow passage communicating between the first flow passage port 10a, the second flow passage port 10b, and the third flow passage port 10c, and a first valve body 11a and a second valve body 12a are installed on the internal flow passage, the first valve body 11a directly communicates or disconnects the first flow passage port 10a and the third flow passage port 10c, and the second valve body 12a communicates or disconnects the second flow passage port 10b and the third flow passage port 10c through an orifice 13 a.

Here, the "direct communication" achieved by the first valve element 11a means that the coolant entering from the first flow passage 10a of the valve body 10 can flow directly to the third flow passage 10c of the valve body 10 without being affected by the internal flow passage beyond the first valve element 11a, and the "disconnection" achieved by the first valve element 11a means that the coolant entering from the first flow passage 10a of the valve body 10 cannot pass beyond the first valve element 11a and cannot flow to the third flow passage 10c of the valve body 10 through the internal flow passage. The "through orifice communication" achieved by the second valve element 12a means that the coolant entering from the second orifice 10b of the valve body 10 can flow to the third orifice 10c of the valve body 10 after passing through the orifice beyond the second valve element 12a, and the "off communication" achieved by the second valve element 12a means that the coolant entering from the second orifice 10b of the valve body 10 cannot pass beyond the second valve element 12a and cannot flow to the third orifice 10c of the valve body 10 through the orifice 13 a.

In other words, the expansion valve has at least a first operation position in which the first spool 11a directly communicates the first fluid passage port 10a with the third fluid passage port 10c, a second operation position in which the second spool 12a disconnects the second fluid passage port 10b from the third fluid passage port 10c, and a third operation position; in the second operating position, the first spool 11a disconnects the first orifice 10a from the third orifice 10c, and the second spool 12a connects the second orifice 10b from the third orifice 10c through the orifice 13 a; in the third operating position, the first spool 11a disconnects the first orifice 10a from the third orifice 10c, and the second spool 12a disconnects the second orifice 10b from the third orifice 10 c.

In this way, by controlling the first spool 11a and the second spool 12a, the expansion switch valve provided by the present disclosure can realize at least three states in total of the coolant entering from the first flow passage 10a and the second flow passage 10 b. Namely, 1) an off state; 2) A direct communication state across the first spool 11 a; and 3) a throttle communication mode across the second spool 12 a.

The high-temperature and high-pressure liquid refrigerant can become a low-temperature and low-pressure vaporous hydraulic refrigerant after being throttled by the throttle hole 13a, which can create conditions for the evaporation of the refrigerant, namely, the cross section area of the throttle hole 13a is smaller than the cross section areas of the first flow passage opening 10a, the second flow passage opening 10b and the third flow passage opening 10c, and the opening degree of the throttle hole 13a can be adjusted by controlling the second valve core so as to control the flow rate flowing through the throttle hole 13a, prevent the insufficient refrigeration caused by the too small amount of the refrigerant and prevent the liquid impact phenomenon of the compressor caused by the too large amount of the refrigerant. That is, the cooperation of the second valve body 12a and the valve body 10 may cause the expansion switching valve to have the function of an expansion valve.

In this way, the first valve core 11a and the second valve core 12a are installed on the inner flow channel of the same valve body 10 with the first flow channel opening 10a, the second flow channel opening 10b and the third flow channel opening 10c, so that the on-off control or throttling control function among the first flow channel opening, the second flow channel opening and the third flow channel opening 10c is realized, the structure is simple, the production and the installation are easy, and when the expansion switch valve provided by the present disclosure is applied to a heat pump system, the refrigerant filling amount 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 more facilitated.

As an exemplary internal mounting structure of the valve body 10, as shown in fig. 5 to 10, the valve body 10 includes a valve seat 100a forming an internal flow passage, and a first valve housing 101a and a second valve housing 102a mounted on the valve seat 100a, a first electromagnetic driving portion 103a for driving a first valve element 11a is mounted in the first valve housing 101a, a second electromagnetic driving portion 104a for driving a second valve element 12a is mounted in the second valve housing 102a, the first valve element 11a extends from the first valve housing 101a to the internal flow passage in the valve seat 100a, and the second valve element 12a extends from the second valve housing 102a to the internal flow passage in the valve seat 100 a.

The position of the first valve core 11a in the internal flow passage can be conveniently controlled by controlling the on/off of the first electromagnetic driving part 103a, such as an electromagnetic coil, so as to control the first flow passage opening 10a and the third flow passage opening 10c to be directly connected or disconnected; the position of the second valve element 12a in the internal flow passage can be controlled conveniently by controlling the on/off of the second electromagnetic drive portion 104a, e.g., an electromagnetic coil, so as to control whether or not the second flow passage port 10b and the third flow passage port 10c communicate with the orifice 13 a. In other words, the electronic expansion valve and the electromagnetic valve are installed in parallel in the valve body 10, 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 valve seat 100a is formed in a polyhedral structure, the first valve housing 101a and the second valve housing 102a are disposed on the same surface of the polyhedral structure, the first fluid passage port 10a and the second fluid passage port 10b are disposed on the same surface of the polyhedral structure, and the first valve housing 101a, the first fluid passage port 10a and the third fluid passage port 10c are disposed on different surfaces of the polyhedral structure, respectively, wherein the mounting directions of the first valve housing 101a and the second valve housing 102a are parallel to each other, and the opening directions of the first fluid passage port 10a and the third fluid passage port 10c 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 14a and a second flow passage 15a communicating with a first flow passage port 10a and a second flow passage port 10b, respectively, the first flow passage 14a is formed with a first valve port 16a engaging with a first valve spool 11a, an orifice 13a is formed on the second flow passage 15a to form a second valve port 17a engaging with a second valve spool 12a, and the first flow passage 14a and the second flow passage 15a meet downstream of the second valve port 17a and communicate with a third flow passage port 10 c.

That is, the function of opening or closing the solenoid valve described above can be achieved by changing the position of the first valve element 11a in the internal flow passage to close or open the first valve port 16a and thereby controlling the shut-off or conduction of the throttle flow passage that communicates the first flow passage port 10a and the third flow passage port 10 c. Similarly, the second valve element 12a is changed in position of the inner flow passage to close or open the second valve port 17a, and the flow passage communicating with the second flow passage port 10b and the third flow passage port 10c is controlled to be blocked or opened, whereby the throttle function of the electronic expansion valve can be realized.

The first flow passage 14A may communicate with the first flow passage 10a and the third flow passage 10c in any suitable arrangement, the second flow passage 15A may communicate with the second flow passage 10b and the third flow passage 10c 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 passage 15A and the third flow passage 10c are perpendicular to each other, the first flow passage 14A is formed as a first through hole 14A parallel to the second flow passage 15A, the second flow passage 10b communicates with the second flow passage 15A through a second through hole 15A opened on a sidewall of the second flow passage 15A, and the first through hole 14A and the second through hole 15A communicate with the first flow passage 10a and the second flow passage 10b, respectively.

In order to minimize the total length of the internal flow path, as shown in fig. 7 and 8, the first through hole 14A and the second flow path 15a are respectively communicated with the third flow path opening 10c through the third through hole 18a and the fourth through hole 19a, and the third through hole 18a and the fourth through hole 19a are coaxially and oppositely opened and are perpendicular to the third flow path opening 10 c. In this way, the total length of the internal flow passage in the valve body 10 can be ensured to be the shortest, thereby ensuring that the refrigerant can flow through the expansion valve promptly.

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

Further, in order to shorten the total length of the inner flow passage to the maximum extent, as shown in fig. 7 and 8, a third flow passage port 10c is provided between the first spool 11a and the second spool 12 a.

Here, the third fluid passage port 10c is provided between the first valve element 11a and the second valve element 12a, and indicates a projection of the third fluid passage port 10c on a plane formed by the first valve element 11a and the second valve element 12a, and is located between the first valve element 11a and the second valve element 12 a.

The first and second spools 11a and 12a may be disposed at any suitable angle, and in one exemplary embodiment, for ease of placement, the first and second spools 11a and 12a are parallel to each other as shown in fig. 7 and 8.

As shown in fig. 7 and 8, to facilitate closing and opening of the first valve port 16a, the first valve spool 11a is coaxially arranged with the first valve port 16a in the moving direction to selectively block or unblock the first valve port 16a.

To facilitate the closing and opening of the second valve port 17a, as shown in fig. 7 and 8, the second valve spool 12a is coaxially arranged with the second valve port 17a in the moving direction to selectively block or unblock the second valve port 17a.

Further, as shown in fig. 7 and 8, to ensure the reliability of the first valve element 11a blocking the first flow passage 14a, the first valve element 11a may include a first valve stem 110a and a first stopper 111a connected to an end of the first valve stem 110a, the first stopper 111a being for sealing and pressing against an end face of the first valve port 16a to block the first flow passage 14a.

In order to adjust the opening size of the orifice 13a of the expansion valve, as shown in fig. 7 and 8, the second valve body 12a includes a second valve stem 120a, and an end portion of the second valve stem 120a is formed in a cone-shaped head structure, and the second valve port 17a is formed in a cone-shaped hole structure to be fitted with the cone-shaped head structure.

The opening degree of the orifice 13a of the expansion valve can be adjusted by the upward and downward movement of the second valve body 12a, and the upward and downward movement of the second valve body 12a can be adjusted by the second electromagnetic drive portion 104 a. If the opening of the orifice 13a of the expansion valve is zero, as shown in fig. 8, the second valve element 12a is at the lowest position, and the second valve element 12a closes the second valve port 17a, the refrigerant cannot pass through the orifice 13a at all, that is, the second valve port 17a; if the expansion switching valve orifice 13a 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 12a and the orifice 13a, and the refrigerant flows to the third orifice 10c after being throttled. If the throttle opening of the expansion valve needs to be increased, the second electromagnetic driving portion 104a can be controlled to enable the second valve core 12a to move upwards, so that the conical head structure is far away from the throttle hole 13a, and the opening of the throttle hole 13a is increased; conversely, when it is necessary to reduce the opening degree of the orifice 13a of the expansion valve, the second valve element 12a may be driven to move downward.

When the electromagnetic valve function of the expansion valve is only needed, namely, when the expansion valve is located at the first working position, as shown in fig. 7 and 9, the first electromagnetic driving portion 103a is powered off, the first plug 111a of the first valve core 11a is separated from the first valve port 16a, and the first valve port 16a is in an open state; the second electromagnetic drive portion 104A is energized, the second valve element 12a is at the lowest position, the second valve element 12a closes the orifice 13a, and the refrigerant cannot flow from the second orifice 10b to the third orifice 10c through the second flow passage 15a, but can flow from the first orifice 10a into the third orifice 10c through the first valve port 16a, the first through hole 14A, and the third through hole 18a 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 103a is energized, the first plug 111a of the first valve core 11a plugs the first valve port 16a, and the first valve port 16a is in a closed state; the second electromagnetic drive portion 104a is deenergized, the second valve element 12a is at the highest position, the second valve element 12a is separated from the orifice 13a, the refrigerant cannot flow from the first orifice 10a to the third orifice 10c through the first passage 14a, only the refrigerant can flow from the second orifice 10b into the third orifice 10c through the second through hole 15A, the orifice 13a and the fourth through hole 19a in this order, and the second valve element 12a can be moved up and down to adjust the opening degree of the orifice 13 a.

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 required to be used simultaneously, that is, when the expansion valve is located at the third working position, the first electromagnetic driving portion 103a is electrified, the first plug 111a of the first valve core 11a plugs the first valve port 16a, and the first valve port 16a is in a closed state; the second electromagnetic drive portion 104a is energized, the second valve element 12a is at the lowest position, the second valve element 12a closes the orifice 13a, and the refrigerant cannot flow from the first orifice 10a or the second orifice 10b to the third orifice 10c, that is, the internal flow passage is in a closed state.

[ second expansion valve 2]

As shown in fig. 11 to 16, the present disclosure also provides an expansion valve having substantially the same structure as the first expansion valve described in detail above, and only the differences therebetween will be described herein.

In the second expansion valve 2, in order to shorten the total length of the internal flow passage to the greatest extent, as shown in fig. 13 and 14, the second flow passage 25A is opened in the same direction as the second flow passage port 20b, the first flow passage 24A is opened in the same direction as the first flow passage port 20a, and is formed as a first through hole 24A parallel to the second flow passage 25A, the third flow passage port 20c communicates with the second flow passage 25A through a second through hole 25A opened on a side wall of the second flow passage 25A, and the first through hole 24A and the second through hole 25A communicate with the third flow passage port 20c, respectively.

Further, in order to shorten the total length of the inner flow passage to the greatest extent, as shown in fig. 13 and 14, the third flow passage port 20c communicates with the first through hole 24A through the third through hole 28a, the third flow passage port 20c communicates with the second through hole 25A through the fourth through hole 29a, the third through hole 28a, the fourth through hole 29a and the second through hole 25A are coaxially disposed, and the third through hole 28a is opened in the opposite direction to the fourth through hole 29a and is perpendicular to the first through hole 24A. That is, the first flow passage port 20a, the second flow passage port 20b, the first through hole 24A, the second through hole 25A, the third through hole 28a, and the fourth through hole 29A enclose a U-shaped structure, and both corners of the U-shaped structure are right angles. In this way, the total length of the internal flow passage within the valve body 20 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, second and third fluid ports of the valve body 20 to the pipe joints of different pipes, respectively, as shown in fig. 11 to 16, the first and second fluid ports 20a and 20b are opened on the same side of the valve body 20 in parallel with each other, and the third fluid port 20c is perpendicular to the first and second fluid ports 20a and 20b, respectively. In this way, pipe joints of pipes located upstream and downstream of the valve body 20 can be respectively mounted to opposite sides of the valve body 500, and the mess and entanglement of different pipe arrangements can be prevented.

In addition, in order to fully utilize the spatial positions of the expansion valve in various directions, the valve seat 200a is formed in a polyhedral structure, the first and second valve casings 201a and 202a are disposed on the same surface of the polyhedral structure, the first and second fluid ports 20a and 20b are disposed on the same surface of the polyhedral structure, and the first, first and third fluid ports 201a, 20a and 20c are disposed on different surfaces of the polyhedral structure, respectively, wherein the installation directions of the first and second valve casings 201a and 202a are parallel to each other, and the opening directions of the first and third fluid ports 20a and 20c are perpendicular 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.

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 an air door mechanism, a compressor (604), an indoor condenser (601), an indoor evaporator (602), an outdoor heat exchanger (605) and two expansion switch valves, wherein the air door mechanism is used for conducting an air channel leading to the indoor evaporator (602) and the indoor condenser (601);

each expansion switching valve includes a valve body (10, 20) on which a first flow passage port (10 a,20 a), a second flow passage port (10 b,20 b), a third flow passage port (10 c,20 c), and an internal flow passage communicating between the first flow passage port (10 a,20 a), the second flow passage port (10 b,20 b), and the third flow passage port (10 c,20 c) are formed, a first spool (11 a,21 a) and a second spool (12 a,22 a) are mounted on the internal flow passage, the first spool (11 a,21 a) causes the first flow passage port (10 a,20 a) and the third flow passage port (10 c,20 c) to communicate directly or to disconnect, the second spool (12 a,22 a) causes the second flow passage port (10 b,20 b) and the third flow passage port (10 c,20 c) to communicate or to disconnect through an orifice (13 a,23 a),

The two expansion switch valves comprise a first expansion switch valve (1) and a second expansion switch valve (2), 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 flow port (10 b) of the first expansion switch valve (1), the third flow port (10 c) of the first expansion switch valve (1) is communicated with the inlet of the outdoor heat exchanger (605), the outlet of the outdoor heat exchanger (605) is communicated with the third flow port (20 c) of the second expansion switch valve (2), the first flow port (20 a) of the second expansion switch valve (2) is communicated with the inlet of the compressor (604), the second flow port (20 b) of the second expansion switch valve (2) is communicated with the inlet of the indoor evaporator (602), the outlet of the indoor evaporator (602) is communicated with the inlet of the compressor (604), and the outlet of the first flow port (604) of the second expansion switch valve (1) is also communicated with the inlet of the first flow port (601).

2. 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).

3. 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 between the first flow passage opening (20 a) of the second expansion switch valve (2) and the compressor (604), and the plate heat exchanger (612) is simultaneously arranged in a motor cooling system of the electric vehicle.

4. A heat pump air conditioning system according to claim 3, characterized in that the motor cooling system comprises a motor, a motor radiator (613) and a water pump (614) in series with the plate heat exchanger (612) to form a circuit.

5. The heat pump air conditioning system according to claim 1, further comprising a gas-liquid separator (611), the outlet of the indoor evaporator (602) and the first flow port (20 a) of the second expansion valve (2) being respectively connected to

The inlet of the gas-liquid separator (611) is communicated, and the outlet of the gas-liquid separator (611) is communicated with the inlet of the compressor (604).

6. The heat pump air conditioning system according to claim 1, characterized in that a third flow passage opening (10 c,20 c) of each expansion switch valve is provided between the first valve spool (11 a,21 a) and the second valve spool (12 a,22 a).

7. The heat pump air conditioning system according to claim 1, characterized in that the internal flow passage of each expansion switching valve includes a first flow passage (14 a,24 a) and a second flow passage (15 a,25 a) communicating with the first flow passage (10 a,20 a) and the second flow passage (10 b,20 b), respectively, the first flow passage (14 a,24 a) being formed with a first valve port (16 a,26 a) that mates with the first spool (11 a,21 a), the orifice (13 a,23 a) being formed on the second flow passage (15 a,25 a) to form a second valve port (17 a,27 a) that mates with the second spool (12 a,22 a), the first flow passage (14 a,24 a) and the second flow passage (15 a,25 a) intersecting downstream of the second valve port (17 a,27 a) and communicating with the third flow passage (10 c,20 c).

8. The heat pump air conditioning system according to claim 7, characterized in that the first valve spool (11 a,21 a) of each expansion switch valve is coaxially arranged with the first valve port (16 a,26 a) in the moving direction to selectively block or unblock the first valve port (16 a,26 a).

9. The heat pump air conditioning system according to claim 8, characterized in that the first valve spool (11 a,21 a) of each expansion switch valve comprises a first valve stem (110 a,210 a) and a first plug (111 a,211 a) connected to an end of the first valve stem (110 a,210 a), the first plug (111 a,211 a) being adapted to be sealingly pressed against an end face of the first valve port (16 a,26 a) to close the first flow passage (14 a,24 a).

10. The heat pump air conditioning system according to claim 7, characterized in that the second valve spool (12 a,22 a) of each expansion switch valve is coaxially arranged with the second valve port (17 a,27 a) in the moving direction to selectively block or unblock the second valve port (17 a,27 a).

11. The heat pump air conditioning system according to claim 10, wherein the second valve element (12 a,22 a) of each expansion valve includes a second valve stem (120 a,220 a), an end of the second valve stem (120 a,220 a) being formed in a cone head configuration, and the second valve port (17 a,27 a) being formed in a cone hole configuration that mates with the cone head configuration.

12. The heat pump air conditioning system according to claim 7, characterized in that the second flow passage (15A) of the first expansion valve (1) is perpendicular to the third flow passage opening (10 c), the first flow passage (14A) of the first expansion valve (1) is formed as a first through hole (14A) parallel to the second flow passage (15A) of the first expansion valve (1), the second flow passage opening (10 b) of the first expansion valve (1) is communicated with the second flow passage (15A) of the first expansion valve (1) through a second through hole (15A) opened on a side wall of the second flow passage (15A) of the first expansion valve (1), and the first through hole (14A) and the second through hole (15A) of the first expansion valve (1) are respectively communicated with the first flow passage opening (10 a) and the second flow passage opening (10 b) of the first expansion valve (1).

13. The heat pump air conditioning system according to claim 12, wherein the first through hole (14A) and the second flow passage (15 a) of the first expansion valve (1) are respectively communicated with the third flow passage opening (10 c) of the first expansion valve (1) through the third through hole (18 a) and the fourth through hole (19 a) of the first expansion valve (1), and the third through hole (18 a) and the fourth through hole (19 a) of the first expansion valve (1) are coaxially and oppositely opened and are mutually perpendicular to the third flow passage opening (10 c) of the first expansion valve (1).

14. The heat pump air conditioning system according to any of claims 1 or 6-13, characterized in that the first flow opening (10 a) and the second flow opening (10 b) of the first expansion valve (1) are open parallel to each other on the same side of the valve body (10) of the first expansion valve (1), and the third flow opening (10 c) of the first expansion valve (1) is parallel to the first flow opening (10 a) and the second flow opening (10 b) of the first expansion valve (1), respectively.

15. The heat pump air conditioning system according to claim 7, wherein the second flow passage (25A) of the second expansion valve (2) is opened in the same direction as the second flow passage (20 b), the first flow passage (24A) of the second expansion valve (2) is opened in the same direction as the first flow passage (20 a) and is formed as a first through hole (24A) parallel to the second flow passage (25A) of the second expansion valve (2), the third flow passage (20 c) of the second expansion valve (2) is communicated with the second flow passage (25A) of the second expansion valve (2) through a second through hole (25A) opened on a side wall of the second flow passage (25A) of the second expansion valve (2), and the first through hole (24A) and the second through hole (25A) of the second expansion valve (2) are respectively communicated with the third flow passage (20 c) of the second expansion valve (2).

16. The heat pump air conditioning system according to claim 15, wherein the third flow passage opening (20 c) of the second expansion switch valve (2) is communicated with the first through hole (24A) of the second expansion switch valve (2) through the third through hole (28 a) of the second expansion switch valve (2), the third flow passage opening (20 c) of the second expansion switch valve (2) is communicated with the second through hole (25A) of the second expansion switch valve (2) through the fourth through hole (29 a) of the second expansion switch valve (2), the third through hole (28 a) of the second expansion switch valve (2), the fourth through hole (29 a) and the second through hole (25A) of the second expansion switch valve (2) are coaxially arranged, and the third through hole (28 a) of the second expansion switch valve (2) is opened in a direction opposite to the fourth through hole (29 a) and is perpendicular to the first through hole (24A) of the second expansion switch valve (2).

17. The heat pump air conditioning system according to any of claims 1, 6-11, 15-16, characterized in that the first flow passage opening (20 a) and the second flow passage opening (20 b) of the second expansion valve (2) are opened in parallel to each other on the same side of the valve body (20) of the second expansion valve (2), and the third flow passage opening (20 c) of the second expansion valve (2) is perpendicular to the first flow passage opening (20 a) and the second flow passage opening (20 b) of the second expansion valve (2), respectively.

18. The heat pump air conditioning system according to claim 1, characterized in that the valve body (10, 20) of each expansion switching valve includes a valve seat (100 a,200 a) forming the internal flow passage, and a first valve housing (101 a,201 a) and a second valve housing (102 a,202 a) mounted on the valve seat (100 a,200 a), a first electromagnetic drive portion (103 a,203 a) for driving the first valve spool (11 a,21 a) being mounted in the first valve housing (101 a,201 a), a second electromagnetic drive portion (104 a,204 a) for driving the second valve spool (12 a,22 a) being mounted in the second valve housing (102 a,202 a), the first valve spool (11 a,21 a) extending from the first valve housing (101 a,201 a) to the internal flow passage in the valve seat (100 a,200 a), and the second valve housing (12 a,22 a) extending from the second valve housing (202 a ) to the internal flow passage in the valve seat (100 a,200 a).

19. The heat pump air conditioning system according to claim 18, wherein the valve seat (100 a) of the first expansion valve (1) is formed in a polyhedral structure, the first valve housing (101 a) and the second valve housing (102 a) of the first expansion valve (1) are disposed on the same surface of the polyhedral structure, the first flow passage opening (10 a) and the second flow passage opening (10 b) of the first expansion valve (1) are disposed on the same surface of the polyhedral structure, and the first valve housing (101 a), the first flow passage opening (10 a) and the third flow passage opening (10 c) of the first expansion valve (1) are disposed on different surfaces of the polyhedral structure, respectively, wherein the mounting directions of the first valve housing (101 a) and the second valve housing (102 a) of the first expansion valve (1) are parallel to each other, and the opening directions of the first flow passage opening (10 a) and the third flow passage opening (10 c) of the first expansion valve (1) are parallel to each other.

20. The heat pump air conditioning system according to claim 18, wherein the valve seat (200 a) of the second expansion switching valve (2) is formed in a polyhedral structure, the first valve housing (201 a) and the second valve housing (202 a) of the second expansion switching valve (2) are disposed on the same surface of the polyhedral structure, the first flow passage opening (20 a) and the second flow passage opening (20 b) of the second expansion switching valve (2) are disposed on the same surface of the polyhedral structure, and the first valve housing (201 a), the first flow passage opening (20 a) and the third flow passage opening (20 c) of the second expansion switching valve (2) are disposed on different surfaces of the polyhedral structure, respectively, wherein the mounting directions of the first valve housing (201 a) and the second valve housing (202 a) of the second expansion switching valve (2) are parallel to each other, and the opening directions of the first flow passage opening (20 a) and the third flow passage opening (20 c) of the second expansion switching valve (2) are perpendicular to each other.

21. An electric vehicle comprising a heat pump air conditioning system according to any one of claims 1-20.