CN116353288A - Heat pump air conditioning system of electric automobile - Google Patents

Heat pump air conditioning system of electric automobile Download PDF

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Publication number
CN116353288A
CN116353288A CN202310415511.9A CN202310415511A CN116353288A CN 116353288 A CN116353288 A CN 116353288A CN 202310415511 A CN202310415511 A CN 202310415511A CN 116353288 A CN116353288 A CN 116353288A
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China
Prior art keywords
expansion valve
refrigerant
valve
gas
port
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CN202310415511.9A
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Chinese (zh)
Inventor
白涛
施容轩
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Xian Jiaotong University
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Xian Jiaotong University
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Priority to CN202310415511.9A priority Critical patent/CN116353288A/en
Publication of CN116353288A publication Critical patent/CN116353288A/en
Pending legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00485—Valves for air-conditioning devices, e.g. thermostatic valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/88—Optimized components or subsystems, e.g. lighting, actively controlled glasses

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

The invention provides an electric automobile heat pump air conditioning system, which belongs to the technical field of electric automobile heat pump air conditioning, and comprises: a gas-filling compressor for driving the refrigerant; the four-way change valve comprises four passage ports a, b, c, d which are communicated in a switching way, wherein an a port is connected with the output end of the air compressor, and a c port is connected with the input end of the air compressor; the output end of the first expansion valve is connected with the d port of the four-way change valve; the output end of the second expansion valve is connected with the port b of the four-way change valve; an ejector, which inputs the gas-phase refrigerant in the refrigerant output by the ejector into a gas-supplementing port of the gas-supplementing compressor; the output liquid-phase refrigerant is throttled by a second expansion valve and then output; and the subcooler is used for exchanging heat of the refrigerant. The system can reduce throttling loss of electric automobile air conditioner for refrigerating and heating and reduce the pressure ratio of the compressor.

Description

Heat pump air conditioning system of electric automobile
Technical Field
The invention belongs to the technical field of heat pump air conditioners of electric vehicles, and particularly relates to a heat pump air conditioning system of an electric vehicle.
Background
In recent years, the electric automobile industry in China is rapidly developed, and energy conservation of electric automobiles is a focus of attention in the field of automobile air conditioners. The energy efficiency level of the air conditioning system of the electric automobile is a key for influencing the cruising mileage of the electric automobile, and the continuous improvement of the performance of the air conditioning system of the electric automobile is a key for realizing the double-carbon policy of China.
Particularly, when the vehicle air conditioner is operated in a cold region, there is a serious refrigerating capacity attenuation in a heat pump operation mode, and the compressor pressure ratio is excessively large, resulting in an excessively high exhaust temperature problem. The energy efficiency level of the electric heating auxiliary heat is lowered too much, and the endurance mileage is seriously lowered. In addition, when the temperature is too high in summer weather, the exhaust pressure is increased, the throttling loss of the traditional throttling mechanism is too large, and the refrigeration performance is obviously reduced.
The existing method for reducing the throttling loss of the refrigeration system generally adopts a heat regenerator or a mechanical supercooling method, however, the problems of overlarge throttling loss of the system under severe working conditions cannot be effectively solved by the technologies.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides the heat pump air conditioning system of the electric automobile.
In order to achieve the above object, the present invention provides the following technical solutions:
an electric vehicle heat pump air conditioning system, comprising:
a gas-filling compressor for driving the refrigerant;
the four-way change valve comprises four passage ports a, b, c, d which are communicated in a switching way, wherein an a port is connected with the output end of the air compressor, and a c port is connected with the input end of the air compressor;
the output end of the first expansion valve is connected with the d port of the four-way change valve;
the output end of the second expansion valve is connected with the port b of the four-way change valve;
the input end of the ejector is connected with the input ends of the first expansion valve and the second expansion valve; for ejecting the refrigerant out; the gas-phase refrigerant in the output refrigerant is input into the air supplementing port of the air supplementing compressor; the liquid-phase refrigerant in the output refrigerant is throttled by a third expansion valve and then is output;
the subcooler comprises two subcooling loops, wherein one subcooling loop is used for inputting the refrigerant which is output after the throttling of the third expansion valve into the injection inflow port of the ejector; the other supercooling loop connects the input end of the second expansion valve with the input end of the first expansion valve;
when the refrigerant flows from the second expansion valve side to the first expansion valve side or from the first expansion valve side to the second expansion valve side, the refrigerant exchanges heat with the refrigerant from the third expansion valve in the subcooler.
Further, the method further comprises the following steps:
a first valve connected in parallel with the first expansion valve; and the second valve is connected with the second expansion valve in parallel.
Further, the output end of the ejector is provided with a first gas-liquid separator, and the first gas-liquid separator is used for inputting the gas-phase refrigerant in the refrigerant ejected by the ejector into the air supplementing port of the air supplementing compressor and outputting the liquid-phase refrigerant in the refrigerant ejected by the ejector into the third expansion valve.
Further, the method further comprises the following steps:
the second gas-liquid separator is arranged on a connecting line between the port c of the four-way change valve and the air supplementing compressor;
the heat regenerator comprises two heat exchange loops, wherein one heat exchange loop is communicated with the first gas-liquid separator and the third expansion valve, and the other loop is communicated with the c port of the four-way exchange valve and the input end of the second gas-liquid separator.
Further, the method further comprises the following steps:
and the third valve is arranged on a connecting line of the ejector and the first expansion valve.
Further, the method further comprises the following steps:
the first indoor heat exchanger is arranged on a connecting line between the d of the four-way change valve and the first expansion valve;
the second indoor heat exchanger is arranged on a connecting line of the third expansion valve and the subcooler;
the outdoor heat exchanger is arranged on a connecting line of the port b of the second expansion valve and the four-way change valve.
Further, the first indoor heat exchanger, the second indoor heat exchanger and the outdoor heat exchanger are micro-channel heat exchangers;
further, the injector is an adjustable injector with an adjustable valve needle arranged in a nozzle or an adjustable injector with a plurality of injectors.
The heat pump air conditioning system of the electric automobile has the following beneficial effects:
in the heat pump mode, the a-d channels of the four-way reversing valve 102 are connected, and the b-c channels are connected; the first expansion valve 104 is closed; the first valve 105 is opened; at this time, the refrigerant flows from the first expansion valve side to the third expansion valve side.
In the cooling mode, the a-b channels of the four-way reversing valve 102 are connected, and the d-c channels are connected; the second expansion valve 109 is closed; the first valve 105 is closed; at this time, the refrigerant flows from the third expansion valve side to the first expansion valve side.
When the refrigerant flows from the second expansion valve to the first expansion valve or from the first expansion valve to the second expansion valve, the refrigerant exchanges heat with the refrigerant from the third expansion valve in the subcooler. The present invention reduces the inlet temperature into either the first throttle valve or the second throttle valve using the subcooler, thereby reducing the throttling loss of the refrigerant. In addition, the refrigerant from the third expansion valve is heated to a superheated gas-phase refrigerant after passing through the subcooler, and then enters the ejector; the gas in the gas-liquid two-phase refrigerant generated by the output port of the ejector is fed into the gas-supplementing port of the compressor, so that the specific work of the compressor is reduced, and the exhaust temperature of the compressor is reduced, thereby further reducing the throttling loss of the system.
Drawings
In order to more clearly illustrate the embodiments of the present invention and the design thereof, the drawings required for the embodiments will be briefly described below. The drawings in the following description are only some of the embodiments of the present invention and other drawings may be made by those skilled in the art without the exercise of inventive faculty.
Fig. 1 is a schematic diagram of an ejector and air-supplementing enthalpy-increasing coupled electric vehicle heat pump air conditioning system in a heat pump mode according to an embodiment of the present invention;
FIG. 2 is a P-h diagram of an electric vehicle heat pump air conditioning system with an ejector and air supplementing enthalpy increasing coupling in a heat pump mode according to an embodiment of the invention;
FIG. 3 is a schematic diagram of an electric vehicle heat pump air conditioning system with ejector and air make-up enthalpy coupling in a dehumidification mode according to an embodiment of the present invention;
fig. 4 is a schematic diagram of an ejector and air-supplementing enthalpy-increasing coupled heat pump air conditioning system of an electric vehicle in a heat pump defrosting mode according to an embodiment of the present invention;
fig. 5 is a schematic diagram of an electric vehicle heat pump air conditioning system with an ejector and air-supplementing enthalpy-increasing coupling in a refrigeration mode according to an embodiment of the present invention.
Detailed Description
The present invention will be described in detail below with reference to the drawings and the embodiments, so that those skilled in the art can better understand the technical scheme of the present invention and can implement the same. The following examples are only for more clearly illustrating the technical aspects of the present invention, and are not intended to limit the scope of the present invention.
Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. In the description of the present invention, it should be noted that, unless explicitly specified or limited otherwise, the terms "connected," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more, and will not be described in detail herein.
Examples:
the invention provides an electric automobile heat pump air conditioning system, which is shown in fig. 1 specifically, and comprises: a gas-filling compressor 101 for driving a refrigerant; a four-way change valve 102, which comprises four passage ports a, b, c, d which are mutually communicated in a switching way, wherein a port a is connected with the output end of the air compensating compressor 101, and a port c is connected with the input end of the air compensating compressor 101; the output end of the first expansion valve 104 is connected with the d port of the four-way change valve 102; a first valve 105 connected in parallel with the first expansion valve 104; the output end of the second expansion valve 109 is connected with the port b of the four-way change valve 102; a second valve 108 connected in parallel with the second expansion valve 109; an ejector 106, the input end of which is connected to the input ends of the first expansion valve 104 and the second expansion valve 109; for ejecting the refrigerant out; the gas-phase refrigerant in the output refrigerant is input into the air supplementing port of the air supplementing compressor 101; the liquid-phase refrigerant in the output refrigerant is throttled by the third expansion valve 112 and then output; a subcooler 107 including two subcooling circuits, one of which is used to input the refrigerant, which is throttled by the third expansion valve 112 and output, into the ejector inflow port of the ejector 106; the other subcooling circuit connects the input of the second expansion valve 109 with the input of the first expansion valve 104; when the refrigerant flows from the second expansion valve 109 side to the first expansion valve 104 side or from the first expansion valve 104 side to the second expansion valve 109 side, the refrigerant exchanges heat with the refrigerant from the third expansion valve 112 in the subcooler 107.
Specifically, the output end of the ejector 106 is provided with a first gas-liquid separator 117, and the first gas-liquid separator 117 is configured to input the gas-phase refrigerant in the refrigerant ejected from the ejector 106 into the air supply port of the air make-up compressor 101, and output the liquid-phase refrigerant in the refrigerant ejected from the ejector 106 into the third expansion valve 112.
The gas in the gas-liquid two-phase refrigerant generated at the output port of the ejector 106 passes through the gas phase port of the first gas-liquid separator 117 and is fed into the gas-supplementing port of the compressor 101, so that the compressor specific work is reduced, and the exhaust temperature of the compressor can be reduced.
Specifically, the method further comprises the following steps: the second gas-liquid separator 116 is arranged on the connecting line between the port c of the four-way change valve 102 and the air supplementing compressor 101; the regenerator 113 comprises two heat exchange loops, wherein one heat exchange loop is communicated with the first gas-liquid separator 117 and the third expansion valve 112, and the other loop is communicated with the c port of the four-way change valve 102 and the input end of the second gas-liquid separator 116.
Specifically, the method further comprises the following steps:
the first indoor heat exchanger 103 is arranged on a connecting pipeline between d of the four-way change valve 102 and the first expansion valve 104; a second indoor heat exchanger 111 provided on a connection line between the third expansion valve 112 and the subcooler 107, the second indoor heat exchanger 111 being provided with a damper 114; the outdoor heat exchanger 110 is provided in the connection line between the second expansion valve 109 and the port b of the four-way valve 102.
The ejector is used for recovering expansion work and injecting medium-pressure refrigerant of the second indoor heat exchanger 111, and gas-phase refrigerant in the refrigerant output by the ejector is input into a gas-supplementing port of the gas-supplementing compressor 101; the liquid-phase refrigerant discharged from the ejector is throttled by a pressure drop through the third expansion valve 112, and the generated latent heat of vaporization is absorbed in the second indoor evaporator 111 and the subcooler 107. The liquid-phase or gas-phase refrigerant from the second indoor heat exchanger 111 is heated to become superheated gas-phase refrigerant after passing through the subcooler 107, and then enters the ejector 106. The latent heat of the liquid-phase refrigerant at the outlet of the ejector 106 is absorbed in the second indoor heat exchanger 111 or the subcooler 107, and it is possible to provide the cooling load required for defogging and to reduce the throttling loss.
The first indoor heat exchanger 103, the second indoor heat exchanger 111, and the outdoor heat exchanger 110 are microchannel heat exchangers; the injector 106 is an adjustable injector with a built-in needle or a multi-injector.
The system can realize four modes of heat pump, refrigeration, heating, dehumidification and defrosting by switching the flow passage of the four-way reversing valve 102, switching the electromagnetic valve 105 and the electromagnetic valve 115 and switching the air passage built-in air door 114.
The following are examples of the present invention:
embodiment one:
fig. 1 shows the operation flow of the system of the invention in heat pump mode: the a-d channels of the four-way reversing valve 102 are connected, and the b-c channels are connected; the first expansion valve 104 is closed; the first valve 105 is opened; the damper 114 of the second indoor heat exchanger 111 is closed; the refrigerant is compressed by the compressor 101 in sequence, enters the first indoor heat exchanger 103 through the a-d channels of the four-way reversing valve 102 to release heat, then enters the first valve 105, and is divided into two paths: one path of refrigerant passes through the subcooler 107, the second expansion valve 109, the outdoor heat exchanger 110, the four-way reversing valve b-c channel, the regenerator 113, the second gas-liquid separator 116 and then returns to the air suction port of the compressor; the other path of refrigerant passes through the third valve 115, the nozzle of the ejector 106 and the refrigerant from the channel of the subcooler 1073, and the refrigerant enters the first gas-liquid separator 117 in a two-phase state after being mixed and boosted; the gas-phase refrigerant flowing out of the first gas-liquid separator 117 enters the compressor air-supplementing port, and the liquid-phase refrigerant sequentially passes through the third expansion valve 112 and the second indoor heat exchanger 111, and then passes through the subcooler 107 to return to the injection inlet of the ejector 106.
Fig. 2 is a pressure-enthalpy diagram p-h diagram of the system during operation in heat pump mode. The specific working process is as follows: the refrigerant 1 point is mixed with saturated gas 5 point from the first gas-liquid separator 117 through 1' point after precompression of the compressor 101 to become superheated gas 2 point, then further compressed to become high pressure superheated gas 3 point, then becomes saturated or supercooled liquid after heat release of the inner heat exchanger i 103, and is divided into two paths: one path of refrigerant is subjected to supercooling degree further increased by 6 points through a cooler 107, then is subjected to throttling through a second expansion valve 109 to become 7 points in a two-phase state, is subjected to heat absorption by an outdoor heat exchanger 110 to become 8 points of saturated gas, is subjected to heat absorption through a four-way reversing valve 102 and a connecting pipeline to become overheated gas 9, enters a heat regenerator 113 to further overheat 10 points, and then returns to a compressor air suction port through a second gas-liquid separator 116; the other path of refrigerant is changed into a supersonic gas-liquid two-phase state 11' through a third valve 115 and a nozzle of the ejector 106, pressure energy is converted into kinetic energy, 18 points of refrigerant from a passage of the subcooler 1071073 are ejected, 12 points are repeatedly mixed, and then the refrigerant enters the first gas-liquid separator 117 in a two-phase state 13 points after being diffused; the gas-phase refrigerant 5 points flowing out of the first gas-liquid separator 117 enter a compressor air supplementing port, the liquid-phase refrigerant 14 points sequentially pass through 15 points after being supercooled by the regenerator 113, enter a third expansion valve 112 and are subjected to isenthalpic expansion to be changed into a two-phase state 16 points, an air door of the second indoor heat exchanger 111 is closed, after neglecting heat leakage loss, the two-phase refrigerant 17 points enter a supercooler 107 to absorb heat to be changed into superheated gas 18 points, and then return to an injection inflow port of the ejector 106. In the process, the ejector 106 recovers part of expansion work, improves the air supplementing pressure and reduces the specific work of the compressor; meanwhile, latent heat of the refrigerant generated by throttling is recovered in the subcooler 107, so that the supercooling degree is effectively increased, the throttling loss is reduced, and meanwhile, the enthalpy difference of the refrigerant in the outdoor heat exchanger 110 is increased, and the low-temperature heating performance of the system is comprehensively improved.
Embodiment two:
fig. 3 shows the operation of the system of the present invention in a dehumidification mode. The a-d channels of the four-way reversing valve 102 are connected, and the b-c channels are connected; the expansion valve 104 is closed and the first valve 105 is opened; the damper 114 is open; the refrigerant is compressed by the compressor 101 in sequence, enters the first indoor heat exchanger 103 through the a-d channels of the four-way reversing valve 102 to release heat, then enters the first valve 105, and then is divided into two paths: one path of refrigerant passes through the subcooler 107, the second expansion valve 109, the outdoor heat exchanger 110, the four-way reversing valve b-c channel, the regenerator 113, the second gas-liquid separator 116 and then returns to the air suction port of the compressor; the other path of refrigerant passes through the third valve 115, the nozzle of the ejector 106 and the refrigerant of the 1073 channel from the subcooler 107, and enters the first gas-liquid separator 117 in a two-phase state after being mixed and boosted; the gas-phase refrigerant flowing out of the first gas-liquid separator 117 enters the compressor air-supplementing port, and the liquid-phase refrigerant sequentially passes through the third expansion valve 112 and the second indoor heat exchanger 111, and then passes through the subcooler 107 to return to the injection inlet of the ejector 106. The wet air is condensed and dehumidified when passing through the second indoor heat exchanger 111, and the temperature rises after passing through the first indoor heat exchanger 103, so that the purposes of heating and dehumidifying are achieved, and meanwhile, the outdoor heat exchanger 110 works normally, absorbs heat in the air, and can meet the condition that the heating amount of the dehumidifying working condition is not attenuated.
Embodiment III:
specifically, the method further comprises the following steps: the third valve 115 is provided in a connection line between the ejector 106 and the first expansion valve 104.
Fig. 4 shows the operation of the system of the present invention in defrost. In this mode, the a-b channels of the four-way reversing valve 102 are connected and the c-d channels are connected; the first expansion valve 104 and the second expansion valve 109 are closed; the damper 114 of the indoor heat exchanger 111 is closed; the first valve 105 is open and the third valve 115 is closed; the refrigerant is compressed by the compressor 101, enters the outdoor heat exchanger 110 through the a-b channel of the four-way reversing valve 102 to defrost, and then passes through the one-way valve 108, the subcooler 107, the first valve 105, the first indoor heat exchanger 103, the d-c channel of the four-way reversing valve, the regenerator 113, the second gas-liquid separator 116, the liquid accumulation and bottom to prevent liquid impact, and the gas returns to the air suction port of the compressor. At this time, the third valve 115 is closed, the ejector driving circuit stops operating, and the compressor air make-up mode is closed.
Embodiment four:
FIG. 5 shows the system of the present invention in a cooling mode of operation wherein the a-b passages, d-c passages, of the four-way reversing valve 102 are connected during cooling conditions; the second expansion valve 109 is closed; the first valve 105 is closed; the damper 114 is closed; the refrigerant is compressed by the compressor 101 in sequence, enters the outdoor heat exchanger 110 through the a-b channel of the four-way reversing valve 102 to release heat, passes through the one-way valve 108 and the subcooler 107, and then is divided into two paths: one path of refrigerant passes through the first expansion valve 104, the first indoor heat exchanger 103, the d-c channel of the four-way reversing valve 102, the heat regenerator 113 and the second gas-liquid separator 116, and then returns to the air suction port of the compressor 101; the other path of refrigerant passes through the third valve 115, the nozzle of the ejector 106 and the refrigerant of the 1073 channel from the subcooler 107, and enters the first gas-liquid separator 117 in a two-phase state after being mixed and boosted; the gas-phase refrigerant flowing out of the first gas-liquid separator 117 enters the compressor air-supplementing port, and the liquid-phase refrigerant sequentially passes through the third expansion valve 112 and the second indoor heat exchanger 111, and then passes through the subcooler 107 to return to the injection inlet of the ejector 106. The system can still ensure that the exhaust temperature of the compressor is moderate under the high ambient temperature in the mode, and simultaneously improves the refrigerating capacity, so as to enhance the multi-working condition adaptability of the automobile air conditioner.
The above embodiments are merely preferred embodiments of the present invention, the protection scope of the present invention is not limited thereto, and any simple changes or equivalent substitutions of technical solutions that can be obviously obtained by those skilled in the art within the technical scope of the present invention disclosed in the present invention belong to the protection scope of the present invention.

Claims (8)

1. An electric vehicle heat pump air conditioning system, comprising:
a gas-filling compressor (101) for driving a refrigerant;
the four-way change valve (102) comprises four passage ports a, b, c, d which are communicated in a switching way, wherein a port a is connected with the output end of the air supply compressor (101), and a port c is connected with the input end of the air supply compressor (101);
the output end of the first expansion valve (104) is connected with the d port of the four-way change valve (102);
the output end of the second expansion valve (109) is connected with the port b of the four-way change valve (102);
an ejector (106) with its input connected to the inputs of the first expansion valve (104) and the second expansion valve (109); for ejecting the refrigerant out; the gas-phase refrigerant in the output refrigerant is input into a gas supplementing port of a gas supplementing compressor (101); the liquid-phase refrigerant in the output refrigerant is throttled by a third expansion valve (112) and then is output;
-a subcooler (107) comprising two subcooling circuits, one of which is used to feed the refrigerant, throttled by the third expansion valve (112), to the ejector inlet of the ejector (106); the other supercooling loop connects the input end of the second expansion valve (109) with the input end of the first expansion valve (104);
when the refrigerant flows from the second expansion valve (109) side to the first expansion valve (104) side or from the first expansion valve (104) side to the second expansion valve (109) side, the refrigerant exchanges heat with the refrigerant from the third expansion valve (112) in the subcooler (107).
2. The electric vehicle heat pump air conditioning system of claim 1, further comprising:
a first valve (105) connected in parallel with the first expansion valve (104); a second valve (108) connected in parallel with the second expansion valve (109).
3. An electric vehicle heat pump air conditioning system according to claim 1, characterized in that the output end of the ejector (106) is provided with a first gas-liquid separator (117), and the first gas-liquid separator (117) is used for inputting the gas-phase refrigerant in the refrigerant ejected by the ejector (106) into the air-supplementing port of the air-supplementing compressor (101), and outputting the liquid-phase refrigerant in the refrigerant ejected by the ejector (106) into the third expansion valve (112).
4. The electric vehicle heat pump air conditioning system of claim 1, further comprising:
the second gas-liquid separator (116) is arranged on a connecting line between the port c of the four-way change valve (102) and the air supplementing compressor (101);
the heat regenerator (113) comprises two heat exchange loops, wherein one heat exchange loop is communicated with the first gas-liquid separator (117) and the third expansion valve (112), and the other loop is communicated with the c port of the four-way exchange valve (102) and the input end of the second gas-liquid separator (116).
5. The electric vehicle heat pump air conditioning system of claim 1, further comprising:
and a third valve (115) provided on a connection line between the ejector (106) and the first expansion valve (104).
6. The electric vehicle heat pump air conditioning system of claim 1, further comprising:
the first indoor heat exchanger (103) is arranged on a connecting line between d of the four-way change valve (102) and the first expansion valve (104);
a second indoor heat exchanger (111) provided on a connection line between the third expansion valve (112) and the subcooler (107);
and an outdoor heat exchanger (110) provided on the connection line between the second expansion valve (109) and the port b of the four-way change valve (102).
7. The heat pump air conditioning system of electric vehicle according to claim 6, characterized in that the first indoor heat exchanger (103), the second indoor heat exchanger (111), and the outdoor heat exchanger (110) are microchannel heat exchangers.
8. An electric vehicle heat pump air conditioning system according to claim 1, characterized in that the injector (106) is an adjustable injector with an adjustable valve needle or an adjustable injector with multiple injectors in the nozzle.
CN202310415511.9A 2023-04-18 2023-04-18 Heat pump air conditioning system of electric automobile Pending CN116353288A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310415511.9A CN116353288A (en) 2023-04-18 2023-04-18 Heat pump air conditioning system of electric automobile

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310415511.9A CN116353288A (en) 2023-04-18 2023-04-18 Heat pump air conditioning system of electric automobile

Publications (1)

Publication Number Publication Date
CN116353288A true CN116353288A (en) 2023-06-30

Family

ID=86937783

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310415511.9A Pending CN116353288A (en) 2023-04-18 2023-04-18 Heat pump air conditioning system of electric automobile

Country Status (1)

Country Link
CN (1) CN116353288A (en)

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