JP7095845B2 - Combined valve and vehicle air conditioner using it - Google Patents

Description

The present invention relates to a composite valve applied to a refrigerant circuit and a heat pump type air conditioner for vehicles using the same.

As an air conditioner that can be applied to vehicles such as hybrid vehicles and electric vehicles, it is equipped with a refrigerant circuit to which a compressor, a radiator, a heat absorber, and an outdoor heat exchanger are connected, and is discharged from the compressor. A heating mode in which the refrigerant is dissipated in the radiator and the refrigerant dissipated in the radiator is absorbed in the outdoor heat exchanger to heat the vehicle interior, and the refrigerant discharged from the compressor is dissipated in the outdoor heat exchanger. An air conditioner for vehicles has been developed that switches and executes a cooling mode for cooling the vehicle interior by absorbing heat in a heat exchanger. Further, such switching of the operation mode in the vehicle interior is performed by using a large number of solenoid valves (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 2011-237052 JP-A-2015-45453

In this way, conventional air conditioners for vehicles use a large number of solenoid valves to switch the operation mode, resulting in a large number of parts, high costs, and a limited engine room (in the case of an electric vehicle, in the case of an electric vehicle). Although there is no engine, there was the inconvenience of occupying the space outside the vehicle interior where devices related to driving and air conditioning are installed.

On the other hand, an integrated valve (composite valve) for driving a plurality of valve bodies with a single driving means has also been developed (see, for example, Patent Document 2).

The present invention has been made to solve the conventional technical problem, and aims to reduce the number of parts by combining a plurality of electromagnetic valves conventionally used in a vehicle air conditioner. It is an object of the present invention to provide a composite valve capable of being capable of, and an air conditioner for a vehicle using the compound valve.

The composite valve of the present invention is applied to a refrigerant circuit, and is formed in a housing having a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, and a second refrigerant outlet, and in the housing. , A first refrigerant passage that extends between the first refrigerant inlet and the first refrigerant outlet, a second refrigerant passage that is formed in the housing and extends between the second refrigerant inlet and the second refrigerant outlet, and a first refrigerant passage. , A first on-off valve portion that opens and closes the first refrigerant passage, a second on-off valve portion that is provided in the second refrigerant passage and opens and closes the second refrigerant passage, a first on-off valve portion via an actuator, and , A drive device for driving the second on-off valve portion, a first refrigerant passage formed in the housing on the first refrigerant inlet side from the first on-off valve portion, and a second refrigerant outlet side from the second on-off valve portion. It is characterized by being provided with a communication passage that communicates with the two refrigerant passages and a check valve that is provided in the communication passage and has a forward direction in the direction of the second refrigerant passage.

In the compound valve of the second aspect of the present invention, in the above invention, the first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side from the second on-off valve portion are housings. It is characterized in that it is formed adjacent to each other within.

In each of the above inventions, the composite valve according to the third aspect of the present invention has a housing including a first refrigerant inlet, a first refrigerant outlet, a first refrigerant passage, and a first housing member provided with a first on-off valve portion. 2 Refrigerant inlet, 2nd refrigerant outlet, 2nd refrigerant passage, and 2nd housing member provided with a 2nd on-off valve portion are coupled, and an actuator is provided across each housing member, and each on-off valve is provided. It is characterized by driving a unit.

In the compound valve of the invention of claim 4, in the above invention, the first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion is formed in the first housing member in close proximity to one surface of the first housing member. The second refrigerant passage on the second refrigerant outlet side from the second on-off valve portion is formed in the second housing member in the vicinity of one surface of the second housing member, and the first housing member is the first on-off valve. The second housing member has a first communication portion extending from the first refrigerant passage on the first refrigerant inlet side to one surface of the first housing member, and the second housing member has a second refrigerant on the second refrigerant outlet side from the second on-off valve portion. It has a second communication portion extending from the passage to one surface of the second housing member, and one surface of each housing member is connected to each other, and in that state, the communication portions match to form a communication passage.

The vehicle air conditioner according to claim 5 is a vehicle in which the composite valve of each of the above inventions, a compressor for compressing the refrigerant, and a refrigerant inlet are connected to a refrigerant pipe on the discharge side of the compressor to dissipate the refrigerant. A radiator for heating the air supplied to the room, a heat absorber for cooling the air supplied to the vehicle interior by absorbing the refrigerant by connecting the refrigerant outlet to the refrigerant pipe on the suction side of the compressor, and heat dissipation. An outdoor heat exchanger connected to the refrigerant pipe on the refrigerant outlet side of the vessel and provided outside the vehicle interior, an outdoor expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger, and a refrigerant flowing into the heat absorber. It is equipped with an indoor expansion valve for reducing pressure, a bypass circuit branched from the refrigerant pipe on the refrigerant outlet side of the radiator, and a control device, and the refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger is at the first refrigerant inlet of the composite valve. Connected, the refrigerant pipe on the suction side of the compressor is connected to the first refrigerant outlet of the composite valve, the bypass circuit is connected to the second refrigerant inlet of the composite valve, and the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve is the composite valve. It is characterized in that it is connected to the second refrigerant outlet of the above and the drive device of the compound valve is controlled by the control device.

In the vehicle air conditioner according to claim 6, in the above invention, the control device controls the drive device of the compound valve to obtain the first on-off valve portion of the composite valve and the first on-off valve portion. With the refrigerant passage and the second refrigerant passage opened and the inflow of the refrigerant to the heat absorber is blocked, the refrigerant discharged from the compressor is dissipated by the radiator, and the dissipated refrigerant is depressurized by the outdoor expansion valve. After that, a heating mode in which heat is absorbed by the outdoor heat exchanger, a first refrigerant passage and a second refrigerant passage are opened by the first on-off valve portion and the second on-off valve portion of the composite valve, and discharged from the compressor. The radiated refrigerant is radiated by the radiator, the radiated refrigerant is decompressed by the outdoor expansion valve, then the heat is absorbed by the outdoor heat exchanger, the refrigerant from the bypass circuit is decompressed by the indoor expansion valve, and then the heat absorber is used. The dehumidifying and heating mode that absorbs heat and the first on-off valve portion of the composite valve and the second on-off valve portion close the first refrigerant passage and the second refrigerant passage, and the refrigerant discharged from the compressor is used as a radiator. A dehumidifying cooling mode in which heat is dissipated by an outdoor heat exchanger, the dissipated refrigerant flows through a check valve of a compound valve to an indoor expansion valve, decompression is performed by this indoor expansion valve, and then heat is absorbed by a heat absorber. The first on-off valve section and the second on-off valve section close the first refrigerant passage and the second refrigerant passage, dissipate the refrigerant discharged from the compressor with the outdoor heat exchanger, and combine the dissipated refrigerant. It is characterized by switching between a cooling mode in which heat is passed through the check valve of the valve to the indoor expansion valve, the pressure is reduced by the indoor expansion valve, and then heat is absorbed by the heat exchanger.

The vehicle air conditioner according to claim 7 is provided with the temperature control target cooling device for cooling the temperature control target mounted on the vehicle by using the refrigerant in the invention of claim 5 or 6. The temperature control target cooling device is a heat exchanger for temperature control for absorbing heat of the refrigerant to cool the target for temperature control, and an auxiliary expansion valve for reducing the pressure of the refrigerant flowing into the heat exchanger for temperature control. The refrigerant inlet of the heat exchanger for temperature control is connected to the branch pipe branched from the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve, and the refrigerant outlet of the heat exchanger for temperature control is of the compressor. It is connected to the refrigerant pipe on the suction side, and the control device controls the drive device of the composite valve to form the first on-off valve portion of the composite valve and the first on-off valve portion to the first refrigerant passage and the second on-off valve portion. The second refrigerant passage is closed, the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is passed through the check valve of the composite valve to the indoor expansion valve and the auxiliary expansion valve, and the indoor expansion valve is used. After depressurizing, heat is absorbed by the heat absorber, and after decompressing by the auxiliary expansion valve, heat is absorbed by the heat exchanger for temperature control. The outdoor heat exchanger dissipates the refrigerant discharged from the compressor in a state where the first refrigerant passage and the second refrigerant passage are closed by the second on-off valve portion and the inflow of the refrigerant to the heat absorber is blocked. The heat radiated refrigerant flows through the check valve of the composite valve to the auxiliary expansion valve, the pressure is reduced by the auxiliary expansion valve, and then the heat is absorbed by the heat exchanger for the temperature control target. It is characterized by performing.

According to the present invention, in a composite valve applied to a refrigerant circuit, a housing having a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, and a second refrigerant outlet, and a housing formed in the housing, the first The first refrigerant passage that extends between the first refrigerant inlet and the first refrigerant outlet, the second refrigerant passage that is formed in the housing and extends between the second refrigerant inlet and the second refrigerant outlet, and the first refrigerant passage are provided. A first on-off valve portion that opens and closes the first refrigerant passage, a second on-off valve portion that is provided in the second refrigerant passage and opens and closes the second refrigerant passage, a first on-off valve portion via an actuator, and a first 2 A drive device for driving the on-off valve portion, a first refrigerant passage formed in the housing on the first refrigerant inlet side from the first on-off valve portion, and a second refrigerant on the second refrigerant outlet side from the second on-off valve portion. Since it is provided with a communication passage that communicates with the passage and a check valve that is provided in the communication passage and has a forward direction in the direction of the second refrigerant passage, for example, compression for compressing the refrigerant as in the invention of claim 5. The machine and the refrigerant inlet are connected to the refrigerant pipe on the discharge side of the compressor, the radiator for radiating the refrigerant and heating the air supplied to the passenger compartment, and the refrigerant outlet to the refrigerant pipe on the suction side of the compressor. A heat absorber that is connected to absorb heat from the refrigerant and cool the air supplied to the vehicle interior, an outdoor heat exchanger that is connected to the refrigerant pipe on the refrigerant outlet side of the radiator, and is installed outside the vehicle interior, and this outdoor unit. Control: an outdoor expansion valve for reducing the pressure of the refrigerant flowing into the heat exchanger, an indoor expansion valve for reducing the pressure of the refrigerant flowing into the heat absorber, and a bypass circuit branched from the refrigerant pipe on the refrigerant outlet side of the radiator. Applicable to a vehicle air conditioner equipped with a device, the refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger is connected to the first refrigerant inlet of the compound valve, and the refrigerant pipe on the suction side of the compressor is connected to the first refrigerant pipe of the compound valve. If it is connected to the refrigerant outlet, the bypass circuit is connected to the second refrigerant inlet of the compound valve, and the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve is connected to the second refrigerant outlet of the compound valve, the compound valve is driven by the control device. By controlling the device, it is possible to switch between the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode as in the invention of claim 6.

Further, as in the invention of claim 7, a temperature control target cooling device for cooling the temperature control target mounted on the vehicle by using the refrigerant is provided, and the temperature control target cooling device absorbs the refrigerant to be heated. A heat exchanger for temperature control to cool the target and an auxiliary expansion valve for reducing the pressure of the refrigerant flowing into the heat exchanger for temperature control are provided to provide a refrigerant inlet for the heat exchanger for temperature control. Is connected to the branch pipe branched from the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve, and the refrigerant outlet of the heat exchanger for temperature control is connected to the refrigerant pipe on the suction side of the compressor. By controlling the drive device of the above, it is possible to switch between the cooling / temperature-controlled cooling mode and the temperature-controlled cooling mode.

That is, the function of switching the operation mode of the air conditioner for vehicles, which was conventionally carried out by multiple solenoid valves, can be integrated into the compound valve, and the parts cost and production cost can be reduced by reducing the number of parts. It will be possible to reduce the installation space.

In this case, as in the invention of claim 2, the first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side from the second on-off valve portion are adjacent to each other in the housing. If it is formed in this way, the first refrigerant passage and the second refrigerant passage can be communicated with each other by a communication passage having a short dimension, and loss such as pressure loss in the communication passage can be suppressed to the minimum. ..

Further, as in the invention of claim 3, the housing is provided with a first refrigerant inlet, a first refrigerant outlet, a first refrigerant passage, a first on-off valve portion, a first housing member, and a second refrigerant inlet. 2 The refrigerant outlet, the second refrigerant passage, and the second housing member provided with the second on-off valve portion are coupled to each other, and an actuator is provided across each housing member to drive each on-off valve portion. If this is the case, the manufacturing / assembling work of the compound valve becomes easy.

In particular, as in the invention of claim 4, the first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion is formed in the first housing member close to one surface of the first housing member, and the second on-off valve is formed. A second refrigerant passage on the second refrigerant outlet side from the portion is formed in the second housing member in close proximity to one surface of the second housing member, and the first refrigerant inlet from the first on-off valve portion is formed in the first housing member. A first communication portion is formed from the first refrigerant passage on the side to one surface of the first housing member, and the second housing member is connected to the second on-off valve portion from the second refrigerant passage on the second refrigerant outlet side to the second housing member. If a second communication portion leading to one surface is formed so that the communication portions match when one surface of each housing member is connected to form a communication passage, a communication passage having a short size can be easily configured. It will be possible to do so, and it will be easier to install the check valve.

It is sectional drawing of the composite valve of one Example to which this invention was applied (the state which the 1st on-off valve part and the 2nd on-off valve part were open). It is sectional drawing of the composite valve of FIG. 1 in the state which the 1st on-off valve part and the 2nd on-off valve part were closed. It is a block diagram of the Example of the air conditioner for a vehicle to which the compound valve of FIG. 1 is applied. FIG. 3 is a block diagram of an air conditioning controller as a control device for the vehicle air conditioner of FIG. It is a figure explaining the heating mode by the air-conditioning controller of FIG. It is a figure explaining the dehumidifying heating mode by the air-conditioning controller of FIG. It is a figure explaining the dehumidifying cooling mode / cooling mode by the air-conditioning controller of FIG. It is a figure explaining the cooling / temperature control target cooling mode by the air-conditioning controller of FIG. It is a figure explaining the cooling mode to be temperature-controlled by the air-conditioning controller of FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
(1) Composite valve 81
1 and 2 show a cross-sectional view of a composite valve 81 of an embodiment to which the present invention is applied. The composite valve 81 of the present invention is applied to a refrigerant circuit R of a vehicle air conditioner 1 or the like described later, and has a housing 82 made of a metal such as aluminum and a reverse valve provided in the housing 82. It includes a check valve 18, a first on-off valve portion 21, a second on-off valve portion 22, and a drive device 83 for driving the first and second on-off valve portions 21, 22.

The drive device 83 drives the first and second on-off valve portions 21 and 22 to open and close via the actuator 84. Although the drive device 83 of this embodiment is configured by a solenoid, it may be configured by a stepping motor.

Further, the housing 82 of the embodiment is configured by connecting two parts, a first housing member 86 made of a metal block such as aluminum and a second housing member 87, and is one of the first housing members 86. A first refrigerant inlet 88 and a first refrigerant outlet 89 are formed on the side surface and the other side surface, respectively, and a first refrigerant inlet 88 and a first refrigerant outlet 89 are formed inside the first housing member 86, respectively. The refrigerant passage 91 is formed. Further, a second refrigerant inlet 92 and a second refrigerant outlet 93 are formed on the other side surface and one side surface of the second housing member 87, respectively, and the second refrigerant inlet 92 and the second refrigerant inlet 92 are formed inside the second housing member 87, respectively. A second refrigerant passage 94 is formed between the two refrigerant outlets 93.

The first on-off valve portion 21 comes from a first valve seat 21A provided in the first refrigerant passage 91 and a first valve body 21B for opening and closing the first refrigerant passage 91 in contact with the first valve seat 21A. The second on-off valve portion 22 is configured to contact the second valve seat 22A provided in the second refrigerant passage 94 and the second valve seat 22A to open and close the second refrigerant passage 94. It is composed of a two-valve body 22B.

The first housing member 86 and the second housing member 87 form a housing 82 in which one surface thereof is combined to form an integrated housing 82, and the drive device 83 is attached to the other surface of the second housing member 87. The actuator 84 of the drive device 83 is provided through the second housing member 87 from the second housing member 87 to the first housing member 86, and the first valve body 21B of the first on-off valve portion 21 is provided at the tip thereof. The second valve body 22B of the second on-off valve portion 22 is attached to the drive device 83 side from the first valve body 21B (the actuator 84 ahead of the second valve body 22B is shown in a thin and simplified manner). ..

When the drive device 83 is energized and controlled, the actuator 84 simultaneously drives the first valve body 21B and the second valve body 22B. That is, in the embodiment, when the drive device 83 is not energized, the actuator 84 protrudes, the first valve body 21B abuts on the first valve seat 21A, the first on-off valve portion 21 closes the first refrigerant passage 91, and , The second valve body 22B comes into contact with the second valve seat 22A, and the second on-off valve portion 22 closes the second refrigerant passage 94 (FIG. 2). On the other hand, when the drive device 83 is energized, the actuator 84 is sucked, the first valve body 21B is separated from the first valve seat 21A, the first on-off valve portion 21 opens the first refrigerant passage 91, and the first The two valve body 22B is separated from the second valve seat 22A, and the second on-off valve portion 22 opens the second refrigerant passage 94 (FIG. 1). As described above, the compound valve 81 is configured so that the two on-off valve portions 21 and 22 are simultaneously opened and closed by a single drive device 83.

Further, the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first valve seat 21A is formed close to one surface of the first housing member 86, and the first communication portion extending from the adjacent portion to one surface. 96A is formed. Further, the second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the second valve seat 22A is formed close to one surface of the second housing member 87, and the second communication portion extending from the adjacent portion to one surface. 96B is formed. Then, the communication portions 96A and 96B meet each other in a state where one surface of each housing member 86 and 87 is connected to each other to form a communication passage 96. At this time, the check valve 18 is attached to one of the communication portions (96A or 96B), and when the housing members 86 and 87 are connected, the check valve 18 is inside the other communication portion (96B or 96A). If the check valve 18 is allowed to enter, the check valve 18 can be easily attached. Further, in such a configuration, the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first valve seat 21A and the second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the second valve seat 22A are adjacent to each other in the housing 82. It will be in the form of doing. The communication passage 96 communicates the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first valve seat 21A and the second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the second valve seat 22A. A check valve 18 is provided in the communication passage 96, and the direction of the second refrigerant passage 94 is set as the forward direction.

As shown in FIG. 1, in the composite valve 81, the first valve body 21B of the first on-off valve portion 21 and the second valve body 22B of the second on-off valve portion 22 are driven by the drive device 83, and the first refrigerant passage 91 and the second refrigerant are driven. When the passage 94 is opened, the refrigerant flowing in from the first refrigerant inlet 88 passes through the first on-off valve portion 21 and flows out from the first refrigerant outlet 89, and the refrigerant flowing in from the second refrigerant inlet 92 passes through the second on-off valve portion. It passes through 22 and flows out from the second refrigerant outlet 93 (indicated by a white arrow in FIG. 1). On the other hand, when the first valve body 21B of the first on-off valve portion 21 and the second valve body 22B of the second on-off valve portion 22 are closed by the drive device 83, the second refrigerant passage 91 and the second refrigerant passage 94 are closed, and the first refrigerant is used. The refrigerant flowing into the first refrigerant passage 91 from the inlet 88 reaches the second refrigerant passage 94 via the check valve 18 and flows out from the second refrigerant outlet 93 (indicated by a white arrow in FIG. 2).

(2) Circuit Configuration of Air Conditioning Device 1 for Vehicles Next, the air conditioning device 1 for vehicles to which the composite valve 81 of the present invention is applied will be described with reference to FIG. FIG. 3 shows a configuration diagram of an air conditioner 1 for a vehicle according to an embodiment. Here, the vehicle to which the vehicle air conditioner 1 of the embodiment is applied is an electric vehicle (EV) without an engine (internal engine), and the vehicle is equipped with a battery (for example, a lithium battery). It is driven and traveled by supplying the electric power charged in the battery from an external power source to the traveling motor (electric motor).

That is, the vehicle air conditioner 1 performs a heating mode by operating a heat pump using the refrigerant circuit R in an electric vehicle that cannot be heated by waste heat of the engine, and further performs a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, and cooling /. By selectively executing each operation mode of the temperature control target cooling mode and the temperature control target cooling mode, the vehicle interior is air-conditioned, and the temperature control target 55, which will be described later, is also cooled. ..

Needless to say, the present invention is effective not only for the electric vehicle as a vehicle but also for a so-called hybrid vehicle or a normal engine-driven vehicle that uses an engine and an electric motor for traveling.

The vehicle air conditioner 1 of the embodiment air-conditions (heats, cools, dehumidifies, and ventilates) the interior of the electric vehicle, and is an electric compressor (electric compressor) 2 that compresses the refrigerant. A radiator 4 is provided in the air flow passage 3 of the HVAC unit 10 through which the air in the vehicle interior is circulated to heat the air supplied to the vehicle interior by radiating the refrigerant, and the refrigerant is depressurized and expanded during heating. An outdoor expansion valve 6 composed of an electric valve for allowing air conditioning, and an outdoor for exchanging heat between the refrigerant and the outside air so as to function as a radiator that dissipates heat of the refrigerant during cooling and as an evaporator that absorbs the refrigerant during heating. An indoor expansion valve 8 including a heat exchanger 7 and an electric valve that decompresses and expands the refrigerant, and air provided in the air flow passage 3 that absorbs heat from the outside of the vehicle interior to the refrigerant and supplies it to the vehicle interior during cooling and dehumidification. A heat absorber 9 for cooling the above, an accumulator 12, and the above-mentioned composite valve 81 and the like are sequentially connected by a refrigerant pipe 13, and a refrigerant circuit R is configured.

The outdoor expansion valve 6 and the indoor expansion valve 8 can be fully opened or fully closed while decompressing and expanding the refrigerant. Further, the refrigerant inlet of the radiator 4 is connected to the refrigerant pipe 13G on the discharge side of the compressor 2. Further, the outdoor heat exchanger 7 is provided with an outdoor blower 15. The outdoor blower 15 forcibly ventilates the outside air to the outdoor heat exchanger 7 to exchange heat between the outside air and the refrigerant, whereby the outdoor air is outdoors even when the vehicle is stopped (that is, the vehicle speed is 0 km / h). The heat exchanger 7 is configured to ventilate outside air.

Further, the refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to the first refrigerant inlet 88 of the composite valve 81, and the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve 8 is connected to the second refrigerant outlet 93 of the composite valve 81. 13B is connected. A refrigerant pipe 13D constituting a part of the refrigerant pipe on the suction side of the compressor 2 is connected to the first refrigerant outlet 89 of the composite valve 81, and the refrigerant pipe 13D is connected to the refrigerant outlet side of the heat absorber 9. It is continuously connected to the pipe 13C. The refrigerant pipe 13C constitutes the main body of the refrigerant pipe on the suction side of the compressor 2. A check valve 20 is connected to the refrigerant pipe 13C downstream from the connection point of the refrigerant pipe 13D, and the refrigerant pipe 13C downstream from the check valve 20 is on the suction side of the compressor 2 via the accumulator 12. It is connected to the. The check valve 20 has the accumulator 12 side in the forward direction. Further, the entire refrigerant pipe from the refrigerant outlet side of the heat absorber 9 to the suction side of the compressor 2 is indicated by reference numeral 13C.

Further, the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4 is branched into the refrigerant pipe 13J and the bypass circuit (refrigerant pipe) 13F in front of the outdoor expansion valve 6 (on the upstream side of the refrigerant), and one of the branched refrigerant pipes 13J. Is connected to the refrigerant inlet side of the outdoor heat exchanger 7 via the outdoor expansion valve 6. That is, the refrigerant pipe 13J constitutes a part of the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4. Further, the branched bypass circuit 13F is connected to the second refrigerant inlet 92 of the composite valve 81.

Further, in the air flow passage 3 on the air upstream side of the heat absorber 9, each suction port of the outside air suction port and the inside air suction port is formed (represented by the suction port 25 in FIG. 3), and this suction port is formed. The suction switching damper 26 for switching the air introduced into the air flow passage 3 into the inside air (inside air circulation), which is the air inside the vehicle interior, and the outside air (outside air introduction), which is the air outside the vehicle interior, is provided. Further, an indoor blower fan 27 for supplying the introduced inside air and outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.

Further, in FIG. 3, 23 is an auxiliary heater as an auxiliary heating device. In the embodiment, the auxiliary heater 23 is composed of a PTC heater (electric heater), and is provided in the air flow passage 3 on the air downstream side of the radiator 4 with respect to the air flow in the air flow passage 3. There is. Then, when the auxiliary heater 23 is energized and generates heat, this becomes a so-called heater core, which complements the heating of the vehicle interior.

Further, the air (inside air or outside air) in the air flow passage 3 after flowing into the air flow passage 3 and passing through the heat absorber 9 is radiated into the air flow passage 3 on the air upstream side of the radiator 4. An air mix damper 28 for adjusting the ratio of ventilation to the vessel 4 and the auxiliary heater 23 is provided. Further, FOOT (foot), VENT (vent), and DEF (def) outlets (represented by the outlet 29 in FIG. 3) are formed in the air flow passage 3 on the air downstream side of the radiator 4. The outlet 29 is provided with an outlet switching damper 31 for switching and controlling the blowing of air from each of the outlets.

(3) Cooling device for temperature control 61
Further, the vehicle air conditioner 1 includes a temperature control target cooling device 61 for circulating a heat medium to cool the temperature control target 55 such as a battery or a traveling motor mounted on the vehicle. That is, in the embodiment, the battery and the traveling motor are the temperature-controlled objects 55 mounted on the vehicle, but the following description assumes that the temperature-controlled object 55 is a battery. The object to be temperature-controlled in the present invention is not limited to the battery and the traveling motor, but also includes electric devices such as an inverter circuit for driving the traveling motor.

The cooling device 61 for temperature control of the embodiment includes a circulation pump 62 as a circulation device for circulating a heat medium in the temperature control target 55, and a heat exchanger 64 for temperature control, and the heat exchanger 64 is provided with them. The adjustment target 55 is connected by a heat medium pipe 68. In the case of the embodiment, the inlet of the heat medium flow path 64A of the heat exchanger 64 for temperature control is connected to the discharge side of the circulation pump 62, and the temperature control target 55 is connected to the outlet of the heat medium flow path 64A. ing. The outlet of the temperature control target 55 is connected to the suction side of the circulation pump 62.

As the heat medium used in the temperature-controlled cooling device 61, for example, water, a refrigerant such as HFO-1234yf, a liquid such as a coolant, or a gas such as air can be adopted. In the embodiment, water is used as a heat medium. Further, it is assumed that a jacket structure is provided around the temperature control target 55 (battery) so that, for example, a heat medium can be distributed in a heat exchange relationship with the temperature control target 55.

Then, when the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 flows into the heat medium flow path 64A of the heat exchanger 64 for temperature control. The heat medium exiting the heat medium flow path 64A of the heat exchanger 64 for temperature control reaches the temperature control target 55, and the heat medium exchanges heat with the temperature control target 55 there. The heat medium that has exchanged heat with the temperature-controlled object 55 is sucked into the circulation pump 62 and circulated in the heat medium pipe 68.

On the other hand, one end of the branch pipe 72 is connected to the refrigerant pipe 13B on the refrigerant inlet side of the indoor expansion valve 8. The branch pipe 72 is provided with an auxiliary expansion valve 73 composed of an electric valve. The auxiliary expansion valve 73 is capable of decompressing and expanding the refrigerant flowing into the refrigerant flow path 64B, which will be described later, of the heat exchanger 64 for temperature control, and also allowing it to be fully closed.

The other end of the branch pipe 72 is connected to the refrigerant inlet of the refrigerant flow path 64B of the heat exchanger 64 for temperature control, and the refrigerant outlet of the refrigerant flow path 64B is a check valve via the refrigerant pipe 74. It is continuously connected to the refrigerant pipe 13C on the downstream side of the refrigerant of 20 and in front of the accumulator 12 (upstream side of the refrigerant). Therefore, the refrigerant pipe 74 also constitutes a part of the refrigerant pipe on the suction side of the compressor 2. Then, these auxiliary expansion valves 73 and the like also form a part of the refrigerant circuit R, and at the same time, form a part of the temperature-controlled cooling device 61.

When the auxiliary expansion valve 73 is open, the refrigerant flowing into the refrigerant pipe 13B flows into the branch pipe 72, is depressurized by the auxiliary expansion valve 73, and then flows into the refrigerant flow path 64B of the heat exchanger 64 for temperature control. Then it evaporates there. The refrigerant absorbs heat from the heat medium flowing through the heat medium flow path 64A in the process of flowing through the refrigerant flow path 64B, and then is sucked into the compressor 2 via the accumulator 12.

(4) Air conditioning controller 32 (control device) of the vehicle air conditioner 1
Next, in FIG. 4, reference numeral 32 denotes an air conditioning controller 32 as a control device that controls the air conditioning device 1 for vehicles. The air conditioning controller 32 is connected to the vehicle controller 35 (ECU) that controls the entire vehicle including the control of the temperature control target 55 (battery and traveling motor) via the vehicle communication bus 45, and transmits / receives information. It is said to be composed. Both the air conditioning controller 32 and the vehicle controller 35 (ECU) are composed of a microcomputer as an example of a computer equipped with a processor.

The input of the air conditioner controller 32 (control device) is sucked into the air flow passage 3 from the outside air temperature sensor 33 that detects the outside air temperature (Tam) of the vehicle, the outside air humidity sensor 34 that detects the outside air humidity, and the suction port 25. The HVAC suction temperature sensor 36 that detects the temperature of the air, the inside air temperature sensor 37 that detects the temperature of the air (inside air) in the vehicle interior, the inside air humidity sensor 38 that detects the humidity of the air inside the vehicle interior, and the dioxide in the vehicle interior. The indoor CO ₂ concentration sensor 39 that detects the carbon concentration, the blowout temperature sensor 41 that detects the temperature of the air blown into the vehicle interior from the blowout port 29, and the discharge refrigerant pressure (discharge pressure Pd) of the compressor 2 are detected. The discharge pressure sensor 42, the discharge temperature sensor 43 that detects the discharge refrigerant temperature of the compressor 2, the suction temperature sensor 44 that detects the suction refrigerant temperature of the compressor 2, and the temperature of the radiator 4 (air that has passed through the radiator 4). The temperature of the radiator 4 or the temperature of the radiator 4 itself: the radiator temperature sensor 46 and the refrigerant pressure of the radiator 4 (inside the radiator 4 or immediately after leaving the radiator 4). Pressure: radiator pressure PCI) detects the radiator pressure sensor 47 and the temperature of the heat absorber 9 (the temperature of the air passing through the heat absorber 9 or the temperature of the heat absorber 9 itself: the heat absorber temperature Te). The heat absorber temperature sensor 48, the heat absorber pressure sensor 49 that detects the refrigerant pressure of the heat absorber 9 (the pressure of the refrigerant in the heat absorber 9 or immediately after leaving the heat absorber 9), and the amount of solar radiation into the vehicle interior. For example, a photosensor type solar radiation sensor 51 for detection, a vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, and air conditioning for setting ON / OFF of air conditioning, setting temperature, and switching of operation mode. The temperature of the operation unit 53 and the outdoor heat exchanger 7 (the temperature of the refrigerant immediately after exiting from the outdoor heat exchanger 7 or the temperature of the outdoor heat exchanger 7 itself: outdoor heat exchanger temperature TXO. Outdoor heat exchanger 7 The outdoor heat exchanger temperature TXO is the evaporation temperature of the refrigerant in the outdoor heat exchanger 7 when functions as an evaporator), and the outdoor heat exchanger temperature sensor 54 and the refrigerant pressure of the outdoor heat exchanger 7 (outdoor). Each output of the outdoor heat exchanger pressure sensor 56 for detecting the pressure of the refrigerant in the heat exchanger 7 or immediately after exiting from the outdoor heat exchanger 7 is connected.

Further, at the input of the air conditioning controller 32, the temperature of the temperature control target 55 (for example, the battery) mounted on the vehicle (the temperature of the temperature control target 55 itself or the heat medium exiting the temperature control target 55). The output of the temperature control target temperature sensor 76 for detecting the temperature of the above temperature or the temperature of the heat medium entering the temperature control target 55: temperature control target temperature Tw) is also connected.

On the other hand, the output of the air conditioning controller 32 includes the compressor 2, the outdoor blower 15, the indoor blower (blower fan) 27, the suction switching damper 26, the air mix damper 28, the outlet switching damper 31, and the outdoor. The expansion valve 6, the indoor expansion valve 8, the drive device 83 of the composite valve 81, the auxiliary heater 23, the circulation pump 62 of the cooling device 61 to be temperature-controlled, and the auxiliary expansion valve 73 are connected. The air conditioning controller 32 controls these based on the output of each sensor, the settings input by the air conditioning operation unit 53, and the information from the vehicle controller 35.

(5) Operation of the vehicle air conditioner 1 including the compound valve 81 With the above configuration, the operation of the vehicle air conditioner 1 of the embodiment will be described next. In the embodiment, the air conditioning controller 32 (control device) can be executed by switching between a heating mode, a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, a cooling / temperature control target cooling mode, and a temperature control target cooling mode. Has been done. Hereinafter, each operation mode will be described.

(5-1) Heating mode First, the heating mode will be described with reference to FIG. FIG. 5 shows the flow of the refrigerant (solid line arrow) in the refrigerant circuit R in the heating mode. When the heating mode is selected by the air conditioning controller 32 (auto mode) or by manual operation to the air conditioning operation unit 53 (manual mode), the air conditioning controller 32 energizes the drive device 83 of the compound valve 81 and the actuator 84. The first on-off valve portion 21 and the second on-off valve portion 22 open the first refrigerant passage 91 and the second refrigerant passage 94 (state of FIG. 1). Further, the indoor expansion valve 8 and the auxiliary expansion valve 73 are fully closed (preventing the inflow of the refrigerant into the heat absorber 9 and the heat exchanger 64 for temperature control).

Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23. As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by the high temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived, cooled, and liquefied.

The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 via the refrigerant pipes 13E and 13J. The refrigerant that has flowed into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7. The refrigerant that has flowed into the outdoor heat exchanger 7 evaporates and draws heat by running or from the outside air that is ventilated by the outdoor blower 15 (endothermic). That is, the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant leaving the outdoor heat exchanger 7 enters the first refrigerant passage 91 of the composite valve 81 from the refrigerant pipe 13A, and exits to the refrigerant pipe 13D via the first on-off valve portion 21.

The refrigerant discharged from the refrigerant pipe 13D enters the refrigerant pipe 13C, enters the accumulator 12 via the check valve 20, is gas-liquid separated there, and then repeats the circulation in which the gas refrigerant is sucked into the compressor 2. Since the air heated by the radiator 4 is blown out from the outlet 29, the interior of the vehicle is heated by this. Although the second on-off valve portion 22 of the composite valve 81 is also open, the refrigerant does not flow into the second refrigerant passage 94 because the indoor expansion valve 8 and the auxiliary expansion valve 73 are fully closed.

The air conditioner controller 32 has a target radiator pressure PCO (target value of the pressure PCI of the radiator 4) from the target heater temperature TCO (target value of the air temperature on the leeward side of the radiator 4) calculated from the target outlet temperature TAO described later. Is calculated, and the rotation speed of the compressor 2 is controlled based on the target radiator pressure PCO and the refrigerant pressure of the radiator 4 (radiator pressure PCI; high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. At the same time, the valve opening of the outdoor expansion valve 6 is controlled based on the temperature of the radiator 4 (radiator temperature TCI) detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47. The degree of overcooling of the refrigerant at the outlet of the radiator 4 is controlled. The target heater temperature TCO is basically TCO = TAO, but a predetermined control limit is provided. Further, when the heating capacity of the radiator 4 is insufficient, the auxiliary heater 23 is energized to generate heat to supplement the heating capacity.

(5-2) Dehumidifying / heating mode Next, the dehumidifying / heating mode will be described with reference to FIG. FIG. 6 shows the flow of the refrigerant (solid arrow) in the refrigerant circuit R in the dehumidifying / heating mode. In the dehumidifying and heating mode, the air conditioning controller 32 opens the indoor expansion valve 8 to decompress and expand the refrigerant in the heating mode. As a result, a part of the condensed refrigerant flowing through the radiator 4 and the refrigerant pipe 13E is diverted to the bypass circuit 13F, and the diverted refrigerant enters the second refrigerant passage 94 from the second refrigerant inlet 92 of the composite valve 81. It flows into the refrigerant pipe 13B from the second refrigerant outlet 93 via the second on-off valve portion 22, flows from the refrigerant pipe 13B to the indoor expansion valve 8, and the remaining refrigerant flows to the outdoor expansion valve 6. That is, a part of the shunted refrigerant is depressurized by the indoor expansion valve 8 and then flows into the heat absorber 9 to evaporate.

The air conditioning controller 32 controls the valve opening degree of the indoor expansion valve 8 so as to maintain the degree of superheat (SH) of the refrigerant at the outlet of the heat absorber 9 at a predetermined value, and the endothermic action of the refrigerant generated in the heat absorber 9 at this time. Since the moisture in the air blown out from the indoor blower 27 condenses and adheres to the endothermic device 9, the air is cooled and dehumidified. The remaining refrigerant that has been shunted and has flowed into the refrigerant pipe 13J is decompressed by the outdoor expansion valve 6 and then evaporated by the outdoor heat exchanger 7.

The refrigerant evaporated in the heat absorber 9 goes out to the refrigerant pipe 13C, merges with the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), and then is sucked into the compressor 2 via the check valve 20 and the accumulator 12. Repeat the cycle. The air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, so that the dehumidifying and heating of the vehicle interior is performed.

The air conditioning controller 32 controls the rotation speed of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. At the same time, the valve opening degree of the outdoor expansion valve 6 is controlled based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.

The outdoor expansion valve 6 can be fully closed. Therefore, when the outdoor expansion valve 6 is fully closed in the dehumidifying / heating mode of FIG. 6, the inflow of the refrigerant into the outdoor heat exchanger 7 is blocked, so that the refrigerant pipe 13E passes through the radiator 4. All the condensed refrigerant flowing through the circuit will flow to the bypass circuit 13F. Then, the refrigerant flowing through the refrigerant pipe 13F reaches the indoor expansion valve 8 from the refrigerant pipe 13B via the second refrigerant passage 94 and the second on-off valve portion 22 of the composite valve 81. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the endothermic device 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the endothermic device 9, so that the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C, passes through the check valve 20 and the accumulator 12, and is sucked into the compressor 2 repeatedly. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidification and heating of the vehicle interior is performed by this, but in this operation, the air flow passage 3 on the indoor side is performed. Since the refrigerant is circulated between the radiator 4 (heat dissipation) and the heat absorber 9 (heat absorption) inside, the heat from the outside air is not pumped up, and the heating capacity equivalent to the power consumed by the compressor 2 is exhibited. It will be. Therefore, since the entire amount of the refrigerant flows through the endothermic device 9 that exerts a dehumidifying action, the dehumidifying capacity is high, but the heating capacity is low.

(5-3) Dehumidifying and cooling mode Next, the dehumidifying and cooling mode will be described with reference to FIG. 7. FIG. 7 shows the flow of the refrigerant (solid arrow) in the refrigerant circuit R in the dehumidifying / cooling mode. In the dehumidifying / cooling mode, the air conditioning controller 32 opens the indoor expansion valve 8 to depressurize and expand the refrigerant, de-energizes the drive device 83 of the composite valve 81, lowers the actuator 84, and lowers the first on-off valve portion 21 and the first on-off valve portion 21. The first on-off valve portion 22 closes the first refrigerant passage 91 and the second refrigerant passage 94 (state in FIG. 2). Further, the outdoor expansion valve 6 is controlled to open slightly, and the auxiliary expansion valve 73 is fully closed (preventing the inflow of the refrigerant into the heat exchanger 64 for temperature control).

Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23. As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by the high temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived, cooled, and condensed.

The refrigerant leaving the radiator 4 reaches the outdoor expansion valve 6 via the refrigerant pipes 13E and 13J, and flows into the outdoor heat exchanger 7 via the outdoor expansion valve 6 which is controlled to be slightly open. The refrigerant flowing into the outdoor heat exchanger 7 is air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 flows out to the refrigerant pipe 13A, and enters the first refrigerant passage 91 from the first refrigerant inlet 88 of the composite valve 81.

At this time, since the first on-off valve portion 21 and the second on-off valve portion 22 are closed, the refrigerant flowing into the first refrigerant passage 91 enters the second refrigerant passage 94 via the communication passage 96 and the check valve 18. , The second refrigerant outlet 93 enters the refrigerant pipe 13B. The refrigerant flowing into the refrigerant pipe 13B reaches the indoor expansion valve 8, is depressurized by the indoor expansion valve 8, and then flows into the heat absorber 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the endothermic device 9, so that the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C and the check valve 20, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. The dehumidified air cooled by the heat absorber 9 is reheated (reheated: heating, the heat dissipation capacity is lower than that during dehumidifying and heating) in the process of passing through the radiator 4, so that the dehumidifying and cooling of the vehicle interior can be performed. It will be done.

The air conditioner controller 32 sets the heat absorber temperature Te to the target heat absorber temperature TEO based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO which is the target value thereof. The target radiator pressure PCO (radiator pressure) calculated from the radiator pressure PCI (high pressure of the refrigerant circuit R) and the target heater temperature TCO detected by the radiator pressure sensor 47 while controlling the rotation speed of the compressor 2 The required reheat amount by the radiator 4 is obtained by controlling the valve opening degree of the outdoor expansion valve 6 so that the radiator pressure PCI becomes the target radiator pressure PCO based on the target value of PCI).

(5-4) Cooling mode Next, the cooling mode will be described. The flow of the refrigerant circuit R is the same as the dehumidifying / cooling mode of FIG. 7. In the cooling mode, the air conditioning controller 32 fully opens the valve opening degree of the outdoor expansion valve 6 in the dehumidifying cooling mode. The air mix damper 28 is in a state of adjusting the ratio of air to the radiator 4 and the auxiliary heater 23.

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Although the air in the air flow passage 3 is ventilated through the radiator 4, the ratio is small (because of only reheating during cooling), so that most of the air passes through here, and the refrigerant leaving the radiator 4 is discharged. It reaches the outdoor expansion valve 6 via the refrigerant pipe 13E. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through the outdoor expansion valve 6 as it is, passes through the refrigerant pipe 13J, flows into the outdoor heat exchanger 7, and is ventilated there by traveling or by the outdoor blower 15. It is air-cooled by the outside air to be condensed and liquefied. The refrigerant leaving the outdoor heat exchanger 7 enters the refrigerant pipe 13B via the refrigerant pipe 13A, the first refrigerant passage 91 of the composite valve 81, the communication passage 96 (check valve 18), and the second refrigerant passage 94, and enters the indoor expansion valve. Up to 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the endothermic device 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the endothermic device 9, and the air is cooled.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C and the check valve 20, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. The air cooled by the heat absorber 9 and dehumidified is blown out into the vehicle interior from the air outlet 29, whereby the vehicle interior is cooled. In this cooling mode, the air conditioning controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.

(5-5) Switching between heating mode, dehumidifying heating mode, dehumidifying cooling mode, and cooling mode The air conditioning controller 32 calculates the above-mentioned target blowing temperature TAO from the following formula (I). This target outlet temperature TAO is a target value of the temperature of the air blown into the vehicle interior from the outlet 29.
TAO = (Tset-Tin) x K + Tbal (f (Tset, SUN, Tam))
・ ・ (I)
Here, Tset is the set temperature in the vehicle interior set by the air conditioning operation unit 53, Tin is the temperature of the vehicle interior air detected by the inside air temperature sensor 37, K is a coefficient, Tbal is the set temperature Tset, and the solar radiation sensor 51 detects it. It is a balance value calculated from the amount of solar radiation SUN and the outside air temperature Tam detected by the outside air temperature sensor 33. In general, the target blowout temperature TAO is higher as the outside air temperature Tam is lower, and decreases as the outside air temperature Tam rises.

Then, the air conditioning controller 32 is operated in any one of the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode based on the outside air temperature Tam detected by the outside air temperature sensor 33 at the time of activation and the target blowing temperature TAO. Select. Further, after the start-up, each operation mode is selected and switched according to changes in the environment and setting conditions such as the outside air temperature Tam and the target blowout temperature TAO.

(5-6) Cooling / Temperature Control Target Cooling Mode Next, a cooling / temperature control target cooling mode by the air conditioning controller 32 during the cooling mode will be described with reference to FIG. Here, the temperature of the battery (target to be temperature-controlled) rises due to the outside air temperature, and also rises due to self-heating during charging / discharging. That is, when the outside air temperature is in a high temperature environment, the temperature of the battery becomes extremely high and charging / discharging becomes difficult (note that the temperature of the traveling motor also becomes extremely high depending on the operation and environmental conditions, resulting in malfunction. It may break down).

Therefore, the air-conditioning controller 32 of the vehicle air conditioner 1 of the embodiment has a predetermined target temperature subject temperature TWO (for example, the target temperature of the battery) for the temperature subject temperature Tw, and a predetermined hysteresis above and below the target temperature TWO. When the upper limit value TWH and the lower limit value TWL are set and the cooling mode as described above is executed, the temperature control target temperature Tw detected by the temperature control target temperature sensor 76 rises above the predetermined upper limit TWH. In this case, the mode shifts from the cooling mode to the cooling / temperature control target cooling mode. FIG. 8 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrow) and the flow of the heat medium of the temperature control target cooling device 61 (dashed line arrow) in this cooling / temperature control target cooling mode.

In this cooling mode for cooling / temperature control, the air conditioning controller 32 opens the auxiliary expansion valve 73 in the cooling mode of the refrigerant circuit R shown in FIG. 7, and the degree of overheating of the refrigerant in the heat exchanger 64 for temperature control is high. The valve opening is controlled based on the above. Then, the circulation pump 62 of the cooling device 61 to be temperature-controlled is operated. As a result, the refrigerant discharged from the radiator 4 flows into the outdoor heat exchanger 7 as described above, and is air-cooled by traveling there or by the outside air ventilated by the outdoor blower 15 to be condensed and liquefied. The refrigerant leaving the outdoor heat exchanger 7 enters the refrigerant pipe 13B via the refrigerant pipe 13A, the first refrigerant passage 91 of the composite valve 81, the communication passage 96 (check valve 18), and the second refrigerant passage 94, and enters the indoor expansion valve. Up to 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the endothermic device 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the endothermic device 9, and the air is cooled.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C and the check valve 20, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. On the other hand, a part of the refrigerant that has entered the refrigerant pipe 13B enters the branch pipe 72, is depressurized by the auxiliary expansion valve 73, and then flows into the refrigerant flow path 64B of the heat exchanger 64 for temperature control via the branch pipe 72. And evaporate. At this time, it exerts an endothermic effect. The refrigerant evaporated in the refrigerant flow path 64B repeats circulation that is sequentially sucked into the compressor 2 through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 (indicated by a solid line arrow in FIG. 8).

On the other hand, the heat medium discharged from the circulation pump 62 reaches the heat medium flow path 64A of the heat exchanger 64 for temperature control in the heat medium pipe 68, where heat is absorbed by the refrigerant evaporating in the refrigerant flow path 64B. The heat medium is cooled. The heat medium exiting the heat medium flow path 64A of the heat exchanger 64 for temperature control reaches the temperature control target 55 and exchanges heat with the temperature control target 55 for cooling. Then, the heat medium that has exchanged heat with the temperature-controlled object 55 repeats circulation sucked into the circulation pump 62 (indicated by a broken line arrow in FIG. 8).

When the temperature control target 55 is cooled in this way and its temperature Tw drops below the lower limit TWL, the air conditioning controller 32 fully closes the auxiliary expansion valve 73, stops the circulation pump 62, and cools / heats. The control target cooling mode returns to the cooling mode. In this way, the temperature Tw of the temperature-controlled object 55 (for example, the battery) is maintained at a predetermined target temperature-controlled temperature TWO.

In the cooling mode for cooling / temperature control, the air conditioning operation unit 53 turns on the air conditioning (air conditioning) not only during the operation of the cooling mode but also when the vehicle is stopped and the battery (heat control target 55) is charged. It is also executed when requested). The flow of the refrigerant in the refrigerant circuit R and the flow of the heat medium in the temperature-controlled cooling device 61 do not change. However, in that case, the air conditioning controller 32 controls the rotation speed of the compressor 2 based on the temperature control target temperature Tw detected by the temperature control target temperature sensor 76, and the indoor expansion valve 8 is based on the heat absorber temperature Te. The valve opening degree is controlled, and the degree of superheat of the refrigerant in the heat absorber 9 is controlled. That is, in the cooling / temperature control target cooling mode during charging, the cooling of the temperature control target is prioritized, and in the running cooling / temperature control target cooling mode, the cooling of the vehicle interior is prioritized.

(5-7) Cooling mode for temperature control Next, referring to FIG. 9, the air conditioning controller 32 receives the air conditioning when there is no air conditioning request in the vehicle interior (air conditioning OFF) while the battery (temperature control target 55) is being charged. The cooling mode for temperature control will be described. Since the battery generates heat during charging, the air conditioning controller 32 of the embodiment also has a predetermined target temperature control target temperature TWO (target temperature of the battery) for the temperature control target temperature Tw and a predetermined hysteresis above and below the target temperature control target temperature TWO. When the upper limit value TWH and the lower limit value TWL are set and the temperature control target temperature Tw detected by the temperature control target temperature sensor 76 rises above the predetermined upper limit TWH, the mode shifts to the temperature control target cooling mode. .. FIG. 9 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrow) and the flow of the heat medium of the temperature control target cooling device 61 (broken line arrow) in this temperature control target cooling mode.

In this temperature-controlled cooling mode, the air-conditioning controller 32 de-energizes the drive device 83 of the composite valve 81, lowers the actuator 84, and uses the first on-off valve section 21 and the second on-off valve section 22 to make the first refrigerant passage. 91 and the second refrigerant passage 94 are closed (state in FIG. 2). Further, the outdoor expansion valve 6 is fully opened, the indoor expansion valve 8 is fully closed (preventing the inflow of the refrigerant into the heat absorber 9), and the auxiliary expansion valve 73 is opened to adjust the valve opening degree. In addition, the circulation pump 62 is operated.

Then, the compressor 2 and the outdoor blower 15 are operated, and the indoor blower 27 is stopped. As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the outdoor heat exchanger 7 via the radiator 4. The refrigerant that has flowed into the outdoor heat exchanger 7 is air-cooled and condensed by the outside air that is ventilated by the outdoor blower 15 there. The refrigerant exiting the outdoor heat exchanger 7 flows out to the refrigerant pipe 13A, and enters the first refrigerant passage 91 from the first refrigerant inlet 88 of the composite valve 81.

At this time, since the first on-off valve portion 21 and the second on-off valve portion 22 are closed, the refrigerant flowing into the first refrigerant passage 91 enters the second refrigerant passage 94 via the communication passage 96 and the check valve 18. , The second refrigerant outlet 93 enters the refrigerant pipe 13B. The refrigerant flowing into the refrigerant pipe 13B flows into the branch pipe 72 to reach the auxiliary expansion valve 73, is depressurized by the auxiliary expansion valve 73, and then enters the refrigerant flow path 64B of the heat exchanger 64 for temperature control. It flows in and evaporates.

The refrigerant evaporated in the refrigerant flow path 64B flows out to the refrigerant pipe 74, reaches the accumulator 12 via the refrigerant pipe 13C and the check valve 20, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. On the other hand, the heat medium discharged from the circulation pump 62 reaches the heat medium flow path 64A of the heat exchanger 64 for temperature control in the heat medium pipe 68, where heat is absorbed by the refrigerant evaporating in the refrigerant flow path 64B. The heat medium is cooled. The heat medium exiting the heat medium flow path 64A of the heat exchanger 64 for temperature control reaches the temperature control target 55 and exchanges heat with the temperature control target 55 for cooling. Then, the heat medium that has exchanged heat with the temperature-controlled object 55 repeats circulation sucked into the circulation pump 62 (indicated by a broken line arrow in FIG. 9).

The air conditioning controller 32 is based on the temperature of the temperature control target 55 (temperature control target temperature Tw) detected by the temperature control target temperature sensor 76 and the target temperature control target temperature TWO, which is the target value thereof, and the temperature control target temperature. The rotation speed of the compressor 2 is controlled so that Tw (the temperature of the battery in the embodiment) is set to the target temperature subject temperature TWO.

As described in detail above, the composite valve 81 of the present invention is formed in a housing 82 having a first refrigerant inlet 88, a first refrigerant outlet 89, a second refrigerant inlet 92, and a second refrigerant outlet 93, and in the housing 82. A first refrigerant passage 91 that extends between the first refrigerant inlet 88 and the first refrigerant outlet 89, and a second refrigerant passage 94 that is formed in the housing 82 and extends between the second refrigerant inlet 92 and the second refrigerant outlet 93. , A first on-off valve portion 21 provided in the first refrigerant passage 91 to open and close the first refrigerant passage 91, and a second on-off valve portion provided in the second refrigerant passage 94 to open and close the second refrigerant passage 94. A drive device 83 for driving the first on-off valve portion 21 and the second on-off valve portion 22 via the actuator 84, and a first refrigerant inlet 88 formed in the housing 82 from the first on-off valve portion 21. A communication passage 96 that communicates the first refrigerant passage 91 on the side and the second refrigerant passage 94 on the second refrigerant outlet 93 side from the second on-off valve portion 22, and the second refrigerant passage 94 provided in the communication passage 96. Since the check valve 18 having the forward direction is provided, the compressor 2 that compresses the refrigerant and the refrigerant inlet are connected to the refrigerant pipe 13G on the discharge side of the compressor 2 as in the embodiment, and the refrigerant is dissipated. The radiator 4 for heating the air supplied to the vehicle interior and the refrigerant outlet are connected to the refrigerant pipe 13C on the suction side of the compressor 2 to absorb the refrigerant and cool the air supplied to the vehicle interior. In order to reduce the pressure of the refrigerant flowing into the outdoor heat exchanger 7 connected to the heat absorber 9 and the refrigerant pipes 13E and 13J on the refrigerant outlet side of the radiator 4 and provided outside the vehicle interior, and the outdoor heat exchanger 7. The outdoor expansion valve 6 is provided, the indoor expansion valve 8 for reducing the pressure of the refrigerant flowing into the heat absorber 9, the bypass circuit 13F branched from the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4, and the air conditioning controller 32. Applied to the vehicle air conditioner 1, the refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to the first refrigerant inlet 88 of the composite valve 81, and becomes the refrigerant pipe on the suction side of the compressor 2. The 13D is connected to the first refrigerant outlet 89 of the composite valve 81, the bypass circuit 13F is connected to the second refrigerant inlet 92 of the composite valve 81, and the refrigerant pipe 13B on the refrigerant inlet side of the indoor expansion valve 8 is connected to the first refrigerant inlet 89 of the composite valve 81. 2 When connected to the refrigerant outlet 93, the air conditioning controller 32 controls the drive device 83 of the composite valve 81 to switch between the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode as in the embodiment. It becomes possible.

Further, as in the embodiment, a temperature control target cooling device 61 for cooling the temperature control target 55 (battery or traveling motor) mounted on the vehicle by using a refrigerant is provided, and the temperature control target cooling device 61 is provided with the temperature control target cooling device 61. A heat exchanger 64 for temperature control target for absorbing heat of the refrigerant to cool the temperature control target 55 and an auxiliary expansion valve 73 for reducing the pressure of the refrigerant flowing into the heat control target heat exchanger 64 are provided. The refrigerant inlet of the heat exchanger 64 for temperature control is connected to the branch pipe 72 branched from the refrigerant pipe 13B on the refrigerant inlet side of the indoor expansion valve 8, and the refrigerant outlet of the heat exchanger 64 for temperature control is connected to the refrigerant. If it is connected to the refrigerant pipe 13C on the suction side of the compressor 2 via the pipe 74, the air conditioning controller 32 controls the drive device 83 of the compound valve to cool the cooling / temperature-controlled cooling mode and the temperature-controlled cooling. It is possible to switch modes and execute.

That is, the function of switching the operation mode of the vehicle air conditioner 1, which was conventionally carried out by a plurality of solenoid valves (solenoid valves for heating and solenoid valves for dehumidification), can be integrated into the composite valve 81. By reducing the number of parts, the parts cost and production cost can be reduced, and the installation space can be reduced.

In this case, in the embodiment, the housing 82 is provided with the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first on-off valve portion 21 and the second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the second on-off valve portion 22. Since the first refrigerant passage 91 and the second refrigerant passage 94 are formed adjacent to each other in the inside, the first refrigerant passage 91 and the second refrigerant passage 94 can be communicated with each other by the communication passage 96 having a short dimension, and the loss such as pressure loss in the communication passage 96 can be minimized. It is possible to suppress it to the limit.

Further, in the embodiment, the housing 82 is provided with the first refrigerant inlet 88, the first refrigerant outlet 89, the first refrigerant passage 91, the first housing member 86 provided with the first on-off valve portion 21, and the second refrigerant inlet. 92, a second refrigerant outlet 93, a second refrigerant passage 94, and a second housing member 87 provided with a second on-off valve portion 22 are coupled and configured, and an actuator 84 is spread over the housing members 86 and 87. Since it is provided so as to drive the on-off valve portions 21 and 22, the manufacturing / assembling work of the composite valve 81 becomes easy.

In particular, in the embodiment, the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first on-off valve portion 21 is formed in the first housing member 86 close to one surface of the first housing member 86, and the second opening / closing is performed. A second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the valve portion 22 is formed in the second housing member 87 close to one surface of the second housing member 87, and the first housing member 86 has a first opening / closing. A first communication portion 96A is formed from the valve portion 21 to one surface of the first housing member 86 from the first refrigerant passage 91 on the side of the first refrigerant inlet 88, and the second on-off valve portion 22 is connected to the second housing member 87. 2 When a second communication portion 96B extending from the second refrigerant passage 94 on the refrigerant outlet 93 side to one surface of the second housing member 87 is formed and one surface of each housing member 86, 87 is connected to each other, each communication portion 96A, Since the 96Bs are matched to form the communication passage 96, the communication passage 96 having a short size can be easily constructed, and the check valve 18 can be easily attached.

The configuration of the composite valve 81 and the configuration of the vehicle air conditioner 1 described in the examples are not limited thereto, and can be changed without departing from the spirit of the present invention. Further, in the embodiment, the indoor expansion valve 8 and the auxiliary expansion valve 73 are configured by an electric valve and fully closed to prevent the inflow of the refrigerant into the heat absorber 9 and the heat exchanger 64 for temperature control. However, the indoor expansion valve 8 and the auxiliary expansion valve 73 may be configured by a mechanical expansion valve, and a solenoid valve may be connected in series to prevent the inflow of the refrigerant. The outdoor expansion valve 6 is also composed of a mechanical expansion valve instead of an electric valve, and a solenoid valve is connected in parallel and always closed. In the adjustment target cooling mode, this solenoid valve may be opened.

Further, in the embodiment, the temperature control target cooling device 61 that cools the temperature control target 55 with the refrigerant via the heat medium is adopted, but the present invention is not limited to this, and the heat exchanger 64 for the temperature control is covered with the refrigerant. The temperature control target 55 may be directly cooled. Furthermore, in the embodiment, the composite valve of the present invention is applied to the air conditioner for a vehicle, but it is needless to say that the compound valve can be applied to various devices having a refrigerant circuit.

1 Air conditioner for vehicles 2 Compressor 4 Heat sink 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat absorber 18 Check valve 21 1st on-off valve 22 2nd on-off valve 32 Air-conditioning controller (control device) )
55 Temperature control target 61 Temperature control target Cooling device 62 Circulation pump 64 Heat exchanger for temperature control target 72 Branch piping 73 Auxiliary expansion valve 81 Composite valve 82 Housing 83 Drive device 84 Actuator 86 1st housing member 87 2nd housing Member 88 1st refrigerant inlet 89 1st refrigerant outlet 91 1st refrigerant passage 92 2nd refrigerant inlet 93 2nd refrigerant outlet 94 2nd refrigerant passage 96 communication passage 96A 1st communication part 96B 2nd communication part

Claims (7)

A compound valve applied to a refrigerant circuit
A housing having a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, and a second refrigerant outlet.
A first refrigerant passage formed in the housing and passing between the first refrigerant inlet and the first refrigerant outlet.
A second refrigerant passage formed in the housing and passing between the second refrigerant inlet and the second refrigerant outlet.
A first on-off valve portion provided in the first refrigerant passage to open and close the first refrigerant passage,
A second on-off valve portion provided in the second refrigerant passage to open and close the second refrigerant passage, and a second on-off valve portion.
A drive device for driving the first on-off valve portion and the second on-off valve portion via an actuator.
Formed in the housing, the first on-off valve portion communicates with the first refrigerant passage on the first refrigerant inlet side and the second on-off valve portion communicates with the second refrigerant passage on the second refrigerant outlet side. Communicating passages and
A composite valve provided in the continuous passage and provided with a check valve having the direction of the second refrigerant passage in the forward direction. The first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side from the second on-off valve portion are formed adjacent to each other in the housing. The compound valve according to claim 1, wherein the compound valve is characterized in that. The housing is
The first refrigerant inlet, the first refrigerant outlet, the first refrigerant passage, and the first housing member provided with the first on-off valve portion.
The second refrigerant inlet, the second refrigerant outlet, the second refrigerant passage, and the second housing member provided with the second on-off valve portion are coupled to each other.
The composite valve according to claim 1 or 2, wherein the actuator is provided over each of the housing members and drives each on-off valve portion. The first refrigerant passage on the first refrigerant inlet side from the first on-off valve portion is formed in the first housing member in the vicinity of one surface of the first housing member.
The second refrigerant passage on the outlet side of the second refrigerant from the second on-off valve portion is formed in the second housing member in close proximity to one surface of the second housing member.
The first housing member has a first communication portion from the first on-off valve portion to one surface of the first housing member from the first refrigerant passage on the first refrigerant inlet side.
The second housing member has a second communication portion extending from the second refrigerant passage on the second refrigerant outlet side to one surface of the second housing member from the second on-off valve portion.
The composite valve according to claim 3, wherein one surface of each housing member is connected to each other, and the communication portions match each other in that state to form the communication passage. A compressor that compresses the refrigerant and
A radiator in which the refrigerant inlet is connected to the refrigerant pipe on the discharge side of the compressor to dissipate the refrigerant and heat the air supplied to the vehicle interior.
A heat absorber for cooling the air supplied to the passenger compartment by absorbing the refrigerant and cooling the air supplied to the passenger compartment by connecting the refrigerant outlet to the refrigerant pipe on the suction side of the compressor.
An outdoor heat exchanger connected to the refrigerant pipe on the refrigerant outlet side of the radiator and provided outside the vehicle interior,
An outdoor expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger,
An indoor expansion valve for reducing the pressure of the refrigerant flowing into the endothermic device,
A bypass circuit branched from the refrigerant pipe on the refrigerant outlet side of the radiator,
Equipped with a control device
The refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger is connected to the first refrigerant inlet of the composite valve.
The refrigerant pipe on the suction side of the compressor is connected to the first refrigerant outlet of the composite valve.
The bypass circuit is connected to the second refrigerant inlet of the composite valve.
Claims 1 to 2, wherein the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve is connected to the second refrigerant outlet of the composite valve, and the drive device of the composite valve is controlled by the control device. An air conditioner for vehicles using any of the composite valves described in 4. The control device controls the drive device of the composite valve by controlling the drive device.
The compression is performed in a state where the first on-off valve portion and the second on-off valve portion of the composite valve open the first refrigerant passage and the second refrigerant passage to prevent the inflow of the refrigerant into the heat exchanger. A heating mode in which the refrigerant discharged from the machine is radiated by the radiator, the radiated refrigerant is decompressed by the outdoor expansion valve, and then heat is absorbed by the outdoor heat exchanger.
The first on-off valve portion and the second on-off valve portion of the composite valve open the first refrigerant passage and the second refrigerant passage, and the refrigerant discharged from the compressor is dissipated by the radiator. After decompressing the radiated refrigerant with the outdoor expansion valve, heat is absorbed by the outdoor heat exchanger, the refrigerant from the bypass circuit is decompressed by the indoor expansion valve, and then heat is absorbed by the heat exchanger. Mode and
The first on-off valve portion and the second on-off valve portion of the composite valve close the first refrigerant passage and the second refrigerant passage, and the refrigerant discharged from the compressor is used as the radiator and the outdoor heat. A dehumidifying / cooling mode in which the radiated refrigerant is radiated by the exchanger, the radiated refrigerant is flowed through the check valve of the composite valve to the indoor expansion valve, the pressure is reduced by the indoor expansion valve, and then the heat is absorbed by the heat absorber.
The first on-off valve portion and the second on-off valve portion of the composite valve close the first refrigerant passage and the second refrigerant passage, and the refrigerant discharged from the compressor is dissipated by the outdoor heat exchanger. A cooling mode in which the radiated refrigerant is allowed to flow through the check valve of the composite valve to the indoor expansion valve, the pressure is reduced by the indoor expansion valve, and then heat is absorbed by the heat exchanger.
The vehicle air conditioner according to claim 5, wherein the air conditioner is switched and executed. Equipped with a temperature control target cooling device that cools the temperature control target mounted on the vehicle using a refrigerant.
The temperature control target cooling device absorbs heat from the refrigerant to cool the temperature control target, and reduces the pressure of the refrigerant flowing into the temperature control target heat exchanger and the temperature control target heat exchanger. The heat exchanger for temperature control has an auxiliary expansion valve, and the refrigerant inlet of the heat exchanger for temperature control is connected to a branch pipe branched from the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve. The refrigerant outlet is connected to the refrigerant pipe on the suction side of the compressor, and at the same time,
The control device controls the drive device of the composite valve by controlling the drive device.
The first on-off valve portion and the second on-off valve portion of the composite valve close the first refrigerant passage and the second refrigerant passage, and the refrigerant discharged from the compressor is dissipated by the outdoor heat exchanger. The radiated refrigerant is allowed to flow through the check valve of the composite valve to the indoor expansion valve and the auxiliary expansion valve, depressurized by the indoor expansion valve, then absorbed by the heat exchanger, and is absorbed by the auxiliary expansion valve. After depressurizing, the cooling / temperature control target cooling mode in which heat is absorbed by the heat exchanger for temperature control,
The compression is performed in a state where the first on-off valve portion and the second on-off valve portion of the composite valve close the first refrigerant passage and the second refrigerant passage to prevent the inflow of the refrigerant into the heat exchanger. The refrigerant discharged from the machine is radiated by the outdoor heat exchanger, the radiated refrigerant flows through the check valve of the composite valve to the auxiliary expansion valve, the pressure is reduced by the auxiliary expansion valve, and then the temperature is adjusted. The temperature-controlled target cooling mode, in which heat is absorbed by the target heat exchanger,
The vehicle air conditioner according to claim 5 or 6, wherein the air conditioner for a vehicle is switched and executed.

Images