WO2019181312A1

WO2019181312A1 - Vehicle air conditioner

Info

Publication number: WO2019181312A1
Application number: PCT/JP2019/005637
Authority: WO
Inventors: 徹也石関; 貴司戸山; 和樹関口
Original assignee: サンデンオートモーティブクライメイトシステム株式会社
Priority date: 2018-03-23
Filing date: 2019-02-15
Publication date: 2019-09-26
Also published as: JP2019166962A; CN111770845A; JP7185412B2

Abstract

[Problem] To provide a vehicle air conditioner which prevents reduction in the oil circulation rate in a cooling circuit when adjusting the battery temperature and which can prevent reduction in compressor reliability. [Solution] A battery temperature adjustment device 61 comprises a refrigerant-heat medium heat exchanger 64, branch piping 72 which extends from a branch member B2 to the refrigerant-heat medium heat exchanger, and an auxiliary expansion valve 73 which is provided in the branch piping and which is for reducing pressure of the refrigerant flowing into the refrigerant-heat medium heat exchanger. An in-cabin expansion valve 8 is arranged in refrigerant piping 13B, nearer to the branching member B2 than to the heat absorber 9, and the auxiliary expansion valve 73 is arranged in the branching piping 72, nearer to the branching member B2 than to the refrigerant-heat medium heat exchanger.

Description

Air conditioner for vehicles

The present invention relates to a heat pump type air conditioner that air-conditions a passenger compartment of a vehicle, and more particularly to a vehicle air conditioner suitable for an electric vehicle or a hybrid vehicle equipped with a battery.

In recent years, with the emergence of environmental problems, vehicles such as hybrid cars and electric cars that drive a driving motor with electric power supplied from a battery have become widespread. An air conditioner (refrigeration cycle apparatus) that can be applied to such a vehicle includes a refrigerant circuit that includes a compressor, a condensing unit, a cooling expansion valve, an indoor evaporator, and the like. The one which drives the compressor with the electric power supplied from has been developed.

In addition, since the battery is difficult to charge and discharge in a high temperature state or extremely low temperature state and deteriorates, a battery cooling evaporator is provided, and the battery is formed by a double tube branched from a branch portion set in the piping to the indoor evaporator. The refrigerant depressurized by the expansion valve is allowed to flow into the battery cooling evaporator to cool the battery (secondary battery) (see, for example, Patent Document 1). Further, in Patent Document 1, in order to reduce the amount of refrigerant present in the double pipe on the high pressure side when the electromagnetic valve on the battery expansion valve side is closed, the battery amount is reduced. The expansion valve for operation was arranged on the side close to the branch to the double pipe.

Japanese Patent No. 5884725

However, the refrigerant also accumulates between the branch portion on the high pressure side and the electromagnetic valve on the cooling expansion valve side. And since the lubricating oil is dissolved in the refrigerant (compatible), the circulation rate of the oil in the refrigerant circuit is lowered, and the reliability of the compressor is increased unless a large amount of oil is sealed. The problem arises that it cannot be maintained. This will be described with reference to FIG. FIG. 16 shows an oil compatibility curve with respect to refrigerant pressure and temperature. For example, when the pressure is 1 MPa and the saturation temperature is 40 ° C., if the refrigerant temperature is 40 ° C. or higher (a gas refrigerant with superheat), the refrigerant dissolution amount (the amount of oil dissolved in the refrigerant) is 50 mass%. While it is below, in the state of a liquid refrigerant lower than that, it is 100 mas%.

This is because gas refrigerant has a low density and the amount of refrigerant that can stay in the same volume is small, so that the amount of oil that can be compatible is also small. That is, the low pressure side pipe is warmed by the outside air and is in a gas state, so that the amount of oil that can be dissolved is reduced. On the other hand, since the refrigerant on the high pressure side is cooled and liquefied by the outside air, many oils can be compatible. Therefore, as described above, when the volume on the high pressure side between the branch portion and the solenoid valve on the cooling expansion valve side increases, a large amount of oil stays and the oil circulation rate (OCR) decreases. .

The present invention has been made in order to solve the conventional technical problem, and prevents the reduction of the oil circulation rate of the refrigerant circuit and the deterioration of the reliability of the compressor when performing battery temperature control. An object of the present invention is to provide a vehicle air conditioner that can be avoided.

A vehicle air conditioner of the present invention includes a compressor that compresses a refrigerant, an outdoor heat exchanger that is provided outside the vehicle interior, a heat absorber that cools the air that is absorbed into the vehicle interior by absorbing the refrigerant, An indoor expansion valve for reducing the pressure of the refrigerant flowing into the heat absorber is provided, and includes a refrigerant circuit in which a predetermined amount of refrigerant and oil are sealed, a control device, and air-conditions the vehicle interior. A branch portion set on the high pressure side of the refrigerant circuit, a heat absorber inlet side circuit provided with an indoor expansion valve from the branch portion to the heat absorber, and a battery mounted on the vehicle by circulating the heat medium A battery temperature adjusting device for adjusting the temperature is provided. The battery temperature adjusting device includes a refrigerant-heat medium heat exchanger for exchanging heat between the refrigerant and the heat medium, and a refrigerant-heat medium heat exchanger from the branch portion. To the branch circuit, and to this branch circuit, An auxiliary expansion valve for depressurizing the refrigerant flowing into the medium-heat medium heat exchanger, and the controller is capable of performing an operation with the indoor expansion valve or the auxiliary expansion valve fully closed. The valve is disposed on the side closer to the branch portion than the heat absorber in the heat sink inlet side circuit, and the auxiliary expansion valve is disposed on the side closer to the branch portion than the refrigerant-heat medium heat exchanger in the branch circuit. It is characterized by being.

According to a second aspect of the present invention, there is provided the vehicle air conditioner according to the first aspect, wherein the control device fully closes the auxiliary expansion valve, dissipates the refrigerant discharged from the compressor in the outdoor heat exchanger, A cooling operation is performed in which the air flows from the branching portion to the circuit on the inlet side of the heat absorber, is decompressed by the indoor expansion valve, and then absorbs heat by the heat absorber.

According to a third aspect of the present invention, there is provided the vehicle air conditioner according to the first aspect, wherein the control device fully closes the indoor expansion valve, radiates the refrigerant discharged from the compressor in the outdoor heat exchanger, and radiates the refrigerant. Is supplied to the branch circuit from the branch section, and after the pressure is reduced by the auxiliary expansion valve, the battery temperature adjustment single mode is performed in which heat is absorbed by the refrigerant-heat medium heat exchanger.

According to a fourth aspect of the present invention, there is provided a vehicle air conditioner comprising: a branch member that has a refrigerant inlet and first and second refrigerant outlets to form a branch portion in each of the above inventions; The branch expansion member is connected to the first refrigerant outlet, rises from the branch member, the indoor expansion valve is disposed at a position higher than the branch member, and the branch circuit is connected to the second refrigerant outlet of the branch member. And the auxiliary expansion valve is arranged at a position higher than the branch member.

According to a fifth aspect of the present invention, there is provided an air conditioning apparatus for a vehicle, wherein the refrigerant circuit in each of the above inventions is configured such that the refrigerant circuit radiates the refrigerant and heats the air supplied to the vehicle interior; An outdoor heat exchanger inlet side circuit for flowing into the exchanger, an outdoor expansion valve provided in the outdoor heat exchanger inlet side circuit for decompressing the refrigerant flowing into the outdoor heat exchanger, and the outdoor expansion valve The control device has a bypass circuit for branching from another branch set on the upstream side of the refrigerant and flowing the refrigerant from the radiator to the indoor expansion valve, and a dehumidification valve provided in the bypass circuit. The outdoor expansion valve or the dehumidifying valve can be operated to close the flow path, and the outdoor expansion valve is closer to the other branch portion of the outdoor heat exchanger inlet side piping than the outdoor heat exchanger. The dehumidification valve is located on the side of the bypass circuit. Than the indoor expansion valve, characterized in that it is arranged closer to the other of the bifurcation.

According to a sixth aspect of the present invention, there is provided an air conditioning apparatus for a vehicle according to the present invention, wherein the control device closes the dehumidifying valve, dissipates the refrigerant discharged from the compressor with a radiator, and dissipates the dissipated refrigerant into another branching portion. Then, after flowing into the outdoor expansion valve, the pressure is reduced by the outdoor expansion valve, and then the heating operation is performed in which heat is absorbed by the outdoor heat exchanger.

According to a seventh aspect of the present invention, in the vehicle air conditioner of the fifth or sixth aspect, the control device releases the refrigerant discharged from the compressor by fully closing the outdoor expansion valve and opening the dehumidifying valve. The dehumidifying operation is performed in which the heat is radiated by the cooler, the radiated refrigerant is caused to flow from the other branch part to the bypass circuit, the pressure is reduced by the indoor expansion valve, and the heat is absorbed by the heat absorber.

An air conditioner for a vehicle according to an eighth aspect of the present invention is the second branch of the fifth and seventh aspects of the present invention, which has a refrigerant inlet and first and second refrigerant outlets to form another branch. And the outdoor heat exchanger inlet side circuit is connected to the first refrigerant outlet of the other branch member and rises from the other branch member, and the outdoor expansion valve is positioned higher than the other branch member. The bypass circuit is connected to the second refrigerant outlet of the other branch member and rises from the other branch member, and the dehumidification valve is positioned higher than the other branch member. Features.

According to the present invention, a compressor for compressing a refrigerant, an outdoor heat exchanger provided outside the passenger compartment, a heat absorber for absorbing the refrigerant and supplying air to the passenger compartment, and the heat absorber A vehicle air conditioner that includes an indoor expansion valve for decompressing an inflowing refrigerant, includes a refrigerant circuit in which a predetermined amount of refrigerant and oil are sealed, and a control device, and air-conditions the vehicle interior. A branch portion set on the high pressure side of the refrigerant circuit, a heat absorber inlet side circuit provided with an indoor expansion valve from the branch portion to the heat absorber, and a battery mounted on the vehicle by circulating the heat medium A battery temperature adjusting device for adjusting the temperature is provided, and the battery temperature adjusting device includes a refrigerant-heat medium heat exchanger for exchanging heat between the refrigerant and the heat medium, and a branch portion to the refrigerant-heat medium heat exchanger. To the branch circuit, and to this branch circuit, The auxiliary expansion valve for depressurizing the refrigerant flowing into the medium-heat medium heat exchanger, and the control device is capable of performing an operation with the indoor expansion valve or the auxiliary expansion valve fully closed, The indoor expansion valve is arranged closer to the branch part than the heat absorber in the circuit on the inlet side of the heat absorber, and the auxiliary expansion valve is arranged closer to the branch part than the refrigerant-heat medium heat exchanger in the branch circuit. Therefore, the volume of the heat absorber inlet side circuit between the branch portion and the indoor expansion valve and the volume of the branch circuit between the branch portion and the auxiliary expansion valve can be reduced.

Thus, for example, as in the invention of claim 2, the control device fully closes the auxiliary expansion valve, dissipates the refrigerant discharged from the compressor in the outdoor heat exchanger, and dissipates the dissipated refrigerant from the branch section. When a cooling operation is performed in which the refrigerant flows through the inlet side circuit, depressurizes by the indoor expansion valve, and absorbs heat by the heat absorber, the refrigerant staying in the branch circuit between the branch section and the auxiliary expansion valve and the compatibility thereof. The amount of generated oil can be remarkably reduced to prevent a decrease in the oil circulation rate, improve the reliability of the compressor, and also prevent an increase in the required refrigerant amount and the required oil amount. It becomes like this.

Further, for example, as in the third aspect of the invention, the control device fully closes the indoor expansion valve, dissipates the refrigerant discharged from the compressor in the outdoor heat exchanger, and dissipates the dissipated refrigerant from the branch part to the branch circuit. In the case where the battery temperature control single mode in which the refrigerant is cooled by the auxiliary expansion valve and then absorbed by the refrigerant-heat medium heat exchanger is executed, the circuit inside the heat absorber inlet side between the branch portion and the indoor expansion valve is also used. The amount of refrigerant staying in the tank and the amount of oil compatible with the refrigerant can be significantly reduced, and similarly, the reduction of the oil circulation rate can be prevented and the reliability of the compressor can be improved. An increase in the required oil amount can be prevented.

In particular, as in the invention of claim 4, the branch portion is constituted by the branch member having the refrigerant inlet and the first and second refrigerant outlets, and the heat sink inlet side circuit is connected to the first refrigerant outlet of the branch member. The indoor expansion valve is disposed at a position higher than the branch member, and the branch circuit is connected to the second refrigerant outlet of the branch member so as to rise from the branch member. If it is arranged at a position higher than the branch member, refrigerant and oil accumulate in the heat absorber inlet side circuit between the branch member and the indoor expansion valve and in the branch circuit between the branch member and the auxiliary expansion valve. It becomes difficult, and the fall of the oil circulation rate can be solved more effectively.

Further, as in the invention of claim 5, the refrigerant circuit radiates the refrigerant and heats the air supplied to the vehicle interior, and the outdoor heat for flowing the refrigerant from the radiator to the outdoor heat exchanger. An exchanger inlet-side circuit, an outdoor expansion valve provided in the outdoor heat exchanger inlet-side circuit, for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger, and another refrigerant upstream of the outdoor expansion valve A bypass circuit for branching from one branch and flowing the refrigerant from the radiator to the indoor expansion valve, and a dehumidifying valve provided in the bypass circuit, and the control device is configured by an outdoor expansion valve or a dehumidifying valve. When it is possible to perform the operation with the flow path closed, the outdoor expansion valve is placed closer to the other branch of the outdoor heat exchanger inlet side piping than the outdoor heat exchanger, and dehumidified. Connect the valve to the indoor expansion valve in the bypass circuit. By placing it on the side close to the branch portion, the volume of the outdoor heat exchanger inlet side circuit between the other branch portion and the outdoor expansion valve, and the bypass circuit between the other branch portion and the dehumidification valve The volume of the can be reduced.

Thus, for example, as in the invention of claim 6, the control device closes the dehumidifying valve, dissipates the refrigerant discharged from the compressor with the radiator, and dissipates the refrigerant from the other branch portion to the outdoor expansion valve. When the heating operation in which the pressure is reduced by the outdoor expansion valve and then absorbed by the outdoor heat exchanger is executed, the refrigerant staying in the bypass circuit between the other branch portion and the dehumidifying valve and the phase The amount of dissolved oil can be remarkably reduced to prevent a decrease in the oil circulation rate, improve the reliability of the compressor, and prevent an increase in the required refrigerant amount and the required oil amount. become able to.

Further, for example, as in the seventh aspect of the invention, the control device fully closes the outdoor expansion valve, opens the dehumidification valve, dissipates the refrigerant discharged from the compressor with the radiator, and further dissipates the dissipated refrigerant. When a dehumidifying operation is performed in which a dehumidifying operation is performed by flowing from one branch to a bypass circuit, depressurizing by an indoor expansion valve, and absorbing heat by a heat absorber, the outdoor heat exchanger inlet between the other branch and the outdoor expansion valve The amount of refrigerant that stays in the side circuit and the amount of oil that is mixed with it can be significantly reduced, as well as preventing a decrease in the oil circulation rate and improving the reliability of the compressor. An increase in the refrigerant amount and the required oil amount can also be prevented.

In particular, as in the eighth aspect of the present invention, another branch part is constituted by another branch member having a refrigerant inlet and first and second refrigerant outlets, and the outdoor heat exchanger inlet side circuit is connected to another branch. Connecting the first refrigerant outlet of the member to rise from the other branch member, arranging the outdoor expansion valve at a higher position than the other branch member, and connecting the bypass circuit to the second branch member If the dehumidification valve is arranged at a position higher than the other branch member by connecting to the refrigerant outlet of No. 2 and rising from the other branch member, the connection between the other branch member and the outdoor expansion valve It is difficult for refrigerant and oil to accumulate in the outdoor heat exchanger inlet side circuit and the bypass circuit between the other branching member and the dehumidifying valve, and the reduction in the oil circulation rate can be more effectively eliminated. Be able to It made.

It is a block diagram of one Example of the air conditioning apparatus for vehicles to which this invention is applied. It is a control block diagram of the controller (control apparatus) of the vehicle air conditioner of FIG. It is a figure explaining the heating operation by the controller of FIG. It is a figure explaining the dehumidification heating operation by the controller of FIG. It is a figure explaining the internal cycle driving | operation by the controller of FIG. It is a figure explaining the dehumidification cooling operation / cooling operation by the controller of FIG. It is a figure explaining the heating / battery temperature control mode by the controller of FIG. It is a figure explaining the dehumidification cooling / battery temperature control mode (cooling / battery temperature control mode) by the controller of FIG. It is a figure explaining the internal cycle / battery temperature control mode by the controller of FIG. It is a figure explaining the dehumidification heating / battery temperature control mode by the controller of FIG. It is a figure explaining the battery temperature control single mode by the controller of FIG. It is a top view of the branch member B2, the indoor expansion valve, and the auxiliary expansion valve part of FIG. It is a front view of the branch member B2, the indoor expansion valve, and the auxiliary expansion valve part of FIG. It is a top view of the branch member B1, the outdoor expansion valve, and the electromagnetic valve (dehumidification) part of FIG. It is a front view of the branch member B1, the outdoor expansion valve, and the solenoid valve (dehumidification) part of FIG. It is a figure which shows the compatibility curve of the oil with respect to the pressure and temperature of a refrigerant | coolant.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment to which the present invention is applied. The vehicle of the embodiment to which the vehicle air conditioner 1 of the present invention is applied is an electric vehicle (EV) in which an engine (internal combustion engine) is not mounted, and a battery 55 (for example, a lithium battery) is mounted on the vehicle. The battery 55 is driven and driven by supplying electric power charged in the battery 55 from an external power source such as a quick charger or a household commercial power source (normal charging) to an electric motor (not shown) for traveling. In addition, the vehicle air conditioner 1 of the present invention mounted on a vehicle is also driven by being supplied with power from the battery 55.

That is, the vehicle air conditioner 1 performs heating operation by heat pump operation using the refrigerant circuit R in an electric vehicle that cannot be heated by engine waste heat, and further performs dehumidification heating operation, internal cycle operation (dehumidification operation), dehumidification The air conditioning of the passenger compartment is performed by selectively executing the air conditioning operations of the cooling operation and the cooling operation.

The present invention is not limited to an electric vehicle, and the present invention is also effective for a so-called hybrid vehicle that uses an engine and an electric motor for traveling, and can also be applied to a normal vehicle that travels with an engine. Needless to say.

The vehicle air conditioner 1 according to the embodiment performs air conditioning (heating, cooling, dehumidification, and ventilation) in a vehicle interior of an electric vehicle, and includes an electric compressor 2 that compresses refrigerant and vehicle interior air. Is provided in the air flow passage 3 of the HVAC unit 10 through which air is circulated, and the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows in through the refrigerant pipe 13G, and dissipates the refrigerant into the vehicle compartment. And an outdoor expansion valve 6 comprising an electric valve (electronic expansion valve) that decompresses and expands the refrigerant during heating, a refrigerant that functions as a radiator that radiates the refrigerant during cooling, and an evaporator that absorbs the refrigerant during heating. An outdoor heat exchanger 7 that exchanges heat with the outside air, an indoor expansion valve 8 that includes an electric valve (electronic expansion valve) that decompresses and expands the refrigerant, and an air flow passage 3 that is provided during cooling and dehumidification Sometimes refrigerant from inside and outside the vehicle A heat absorber 9 for heat absorption, the accumulator 12 and the like are sequentially connected by a refrigerant pipe 13, the refrigerant circuit R is formed.

In this refrigerant circuit R, a predetermined amount of refrigerant (HFO-1234yf in the embodiment) and oil (lubricating oil) are enclosed. In addition, the outdoor expansion valve 6 and the indoor expansion valve 8 allow the refrigerant to expand under reduced pressure, and can be fully opened or fully closed (closed).

The outdoor heat exchanger 7 is provided with an outdoor blower 15. The outdoor blower 15 exchanges heat between the outside air and the refrigerant by forcibly passing outside air through the outdoor heat exchanger 7, so that the outdoor air blower 15 can also be used outdoors even when the vehicle is stopped (that is, the vehicle speed is 0 km / h). It is comprised so that external air may be ventilated by the heat exchanger 7. FIG. In the figure, reference numeral 23 denotes a shutter called a grill shutter. When the shutter 23 is closed, the traveling wind is prevented from flowing into the outdoor heat exchanger 7.

Further, the refrigerant pipe 13A connected to the refrigerant outlet side of the outdoor heat exchanger 7 is connected via a check valve 18 to the refrigerant pipe 13B constituting the heat absorber inlet side circuit in the present invention. The check valve 18 has a refrigerant pipe 13B (heat absorber inlet side circuit) side in the forward direction, and the refrigerant pipe 13B is connected to the indoor expansion valve 8.

Further, the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched, and this branched refrigerant pipe 13D is a refrigerant pipe 13C located on the outlet side of the heat absorber 9 via an electromagnetic valve 21 opened during heating. It is connected in communication. The refrigerant pipe 13 C is connected to the accumulator 12, and the accumulator 12 is connected to the refrigerant suction side of the compressor 2.

Further, the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4 which is the high pressure side of the refrigerant circuit R is provided with a branch member B1 (another branch member in the present invention) constituting another branch portion in the present invention. The branch member B1 is connected to one end of a refrigerant pipe 13J constituting the outdoor heat exchanger inlet side circuit in the present invention. The other end of the refrigerant pipe 13J (outdoor heat exchanger inlet side circuit) is connected to the refrigerant inlet side of the outdoor heat exchanger 7, and the outdoor expansion valve 6 described above is connected to the refrigerant pipe 13J.

Furthermore, one end of a refrigerant pipe 13F constituting the bypass circuit in the present invention is connected to the branch member B1. This refrigerant pipe 13F (bypass circuit) is located on the refrigerant downstream side of the check valve 18 and on the refrigerant upstream side of the indoor expansion valve 8 via an electromagnetic valve 22 as a dehumidification valve in the present invention that is opened during dehumidification. The refrigerant pipe 13 A and the refrigerant pipe 13 B are connected in communication with each other (a branch member B 2 described later). That is, the other end of the refrigerant pipe 13F is connected to a branch member B2 described later. Thus, the refrigerant pipe 13F is connected in parallel to the series circuit of the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve 18, and the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve are connected. The circuit bypasses the circuit 18.

The air flow passage 3 on the air upstream side of the heat absorber 9 is formed with each of an outside air inlet and an inside air inlet (represented by the inlet 25 in FIG. 1). 25 is provided with a suction switching damper 26 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation) which is air inside the vehicle compartment and the outside air (outside air introduction) which is outside the vehicle compartment. Furthermore, an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.

Further, the air (inside air and 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 that adjusts the rate of ventilation through the vessel 4 is provided. Further, FOOT (foot), VENT (vent), and DEF (def) outlets (represented by the outlet 29 as a representative in FIG. 1) are formed in the air flow passage 3 on the air downstream side of the radiator 4. The air outlet 29 is provided with an air outlet switching damper 31 that performs switching control of air blowing from the air outlets.

Furthermore, the vehicle air conditioner 1 includes a battery temperature adjusting device 61 for adjusting the temperature of the battery 55 by circulating a heat medium through the battery 55. The battery temperature adjustment device 61 of the embodiment includes a circulation pump 62 as a circulation device for circulating a heat medium through the battery 55, a heat medium heater 66 as a heating device, and a refrigerant-heat medium heat exchanger 64. These and the battery 55 are annularly connected by a heat medium pipe 68.

In the case of this embodiment, the heat medium heater 66 is connected to the discharge side of the circulation pump 62, the inlet of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 is connected to the outlet of the heat medium heater 66, The inlet of the battery 55 is connected to the outlet of the heat medium flow path 64 A, and the outlet of the battery 55 is connected to the suction side of the circulation pump 62.

As the heat medium used in the battery temperature adjusting 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 employed. In the embodiment, water is used as the heat medium. The heat medium heater 66 is composed of an electric heater such as a PTC heater. Furthermore, it is assumed that a jacket structure is provided around the battery 55 so that the heat medium can circulate with the battery 55 in a heat exchange relationship.

When the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 reaches the heat medium heater 66. If the heat medium heater 66 generates heat, it is heated there, and then It flows into the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64. The heat medium exiting the heat medium flow path 64 A of the refrigerant-heat medium heat exchanger 64 reaches the battery 55. The heat medium exchanges heat therewith with the battery 55 and is then circulated through the heat medium pipe 68 by being sucked into the circulation pump 62.

On the other hand, the refrigerant outlet 13F (bypass circuit) of the refrigerant circuit R, that is, the refrigerant pipe 13F located on the refrigerant downstream side (forward direction side) of the check valve 18 and on the refrigerant upstream side of the indoor expansion valve 8. A branching member B2 constituting a branching portion in the present invention is provided at the connecting portion of the refrigerant piping 13A and the refrigerant piping 13B. That is, one end of the refrigerant pipe 13B (heat absorber inlet side circuit) is connected to the branch member B2, and the other end is connected to the heat absorber 9.

Further, one end of a branch pipe 72 constituting the branch circuit in the present invention is connected to the branch member B2. The branch pipe 72 is provided with an auxiliary expansion valve 73 composed of an electric valve (electronic expansion valve). The auxiliary expansion valve 73 decompresses and expands the refrigerant flowing into a refrigerant flow path 64B (described later) of the refrigerant-heat medium heat exchanger 64 and can be fully closed.

The other end of the branch pipe 72 is connected to the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and one end of the refrigerant pipe 74 is connected to the outlet of the refrigerant flow path 64B. The other end is connected to the refrigerant pipe 13C in front of the accumulator 12 (the refrigerant upstream side). The auxiliary expansion valve 73 and the like also constitute part of the refrigerant circuit R and at the same time constitute part of the battery temperature adjusting device 61.

When the auxiliary expansion valve 73 is open, the refrigerant (a part or all of the refrigerant) discharged from the refrigerant pipe 13F and the outdoor heat exchanger 7 is decompressed by the auxiliary expansion valve 73, and then the refrigerant-heat medium heat exchanger. 64 flows into the refrigerant flow path 64B and 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 through the accumulator 12.

The specific configuration of the branch member B1 described above, the connection structure of the refrigerant pipe 13J and the refrigerant pipe 13F to the branch member B1, and the arrangement of the outdoor expansion valve 6 and the electromagnetic valve 22 will be described in detail later. The specific configuration of the branch member B2 described above, the connection structure of the refrigerant pipe 13B and the branch pipe 72 to the branch member B2, and the arrangement of the indoor expansion valve 8 and the auxiliary expansion valve 73 will be described in detail later.

Next, in FIG. 2, reference numeral 32 denotes a controller as a control device that controls the vehicle air conditioner 1, and includes a microcomputer as an example of a computer including a processor. The input of the controller 32 is an outside air temperature sensor 33 that detects the outside air temperature (Tam) of the vehicle, an outside air humidity sensor 34 that detects outside air humidity, and the temperature of the air that is sucked into the air flow passage 3 from the suction port 25. The HVAC suction temperature sensor 36, 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 in the vehicle interior, and the carbon dioxide concentration in the vehicle interior. An indoor CO ₂ concentration sensor 39, a blowout temperature sensor 41 for detecting the temperature of air blown into the vehicle compartment from the blowout port 29, and a discharge pressure sensor 42 for detecting the discharge refrigerant pressure (discharge pressure Pd) of the compressor 2. The discharge temperature sensor 43 for detecting the discharge refrigerant temperature of the compressor 2, the suction temperature sensor 44 for detecting the suction refrigerant temperature of the compressor 2, and the temperature of the radiator 4 (through the radiator 4). The temperature of the air or the temperature of the radiator 4 itself: the radiator temperature sensor 46 for detecting the radiator temperature TCI, and the refrigerant pressure of the radiator 4 (inside the radiator 4 or immediately after leaving the radiator 4) Detects the pressure of the refrigerant: radiator pressure sensor 47 for detecting the radiator pressure PCI) 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). A heat absorber temperature sensor 48 that detects the refrigerant pressure of the heat absorber 9 (the refrigerant pressure in the heat absorber 9 or the pressure of the refrigerant immediately after leaving the heat absorber 9), and the amount of solar radiation into the passenger compartment For example, a photosensor-type solar radiation sensor 51 for detecting the vehicle, a vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, an air conditioning operation unit 53 for setting switching of the set temperature and air conditioning operation, The temperature of the outdoor heat exchanger 7 (from the outdoor heat exchanger 7 The temperature of the refrigerant immediately after, or the temperature of the outdoor heat exchanger 7 itself: the outdoor heat exchanger temperature TXO When the outdoor heat exchanger 7 functions as an evaporator, the outdoor heat exchanger temperature TXO is the outdoor heat exchanger 7 The outdoor heat exchanger temperature sensor 54 that detects the evaporation temperature of the refrigerant in the refrigerant and the refrigerant pressure of the outdoor heat exchanger 7 (in the outdoor heat exchanger 7 or immediately after the refrigerant is discharged from the outdoor heat exchanger 7). Each output of the outdoor heat exchanger pressure sensor 56 for detecting (pressure) is connected.

Further, the input of the controller 32 further detects the temperature of the battery 55 (the temperature of the battery 55 itself, the temperature of the heat medium exiting the battery 55, or the temperature of the heat medium entering the battery 55: battery temperature Tb). A battery temperature sensor 76, a temperature of the heat medium heater 66 (a temperature of the heat medium heater 66 itself, a temperature of the heat medium that has exited the heat medium heater 66), and a refrigerant. A first outlet temperature sensor 78 for detecting the temperature of the heat medium exiting the heat medium flow path 64A of the heat medium heat exchanger 64, and a second outlet temperature sensor for detecting the temperature of the refrigerant exiting the refrigerant flow path 64B. Each output of 79 is also connected.

On the other hand, the output of the 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 expansion. The solenoid valve 22, the indoor expansion valve 8, the solenoid valve 22 (dehumidification) and the solenoid valve 21 (heating) are connected to the shutter 23, the circulation pump 62, the heat medium heater 66, and the auxiliary expansion valve 73. . And the controller 32 controls these based on the output of each sensor and the setting input in the air-conditioning operation part 53. FIG.

Next, the operation of the vehicle air conditioner 1 of the embodiment having the above configuration will be described. In the embodiment, the controller 32 switches between the heating operation, the dehumidifying heating operation, the internal cycle operation (dehumidifying operation), the dehumidifying and cooling operation, and the cooling operation, and sets the temperature of the battery 55 to a predetermined appropriate temperature. Adjust within range. First, each air conditioning operation of the refrigerant circuit R will be described.

(1) Heating Operation First, the heating operation will be described with reference to FIG. FIG. 3 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the heating operation. When the heating operation is selected by the controller 32 (auto mode) or by the manual operation (manual mode) to the air conditioning operation unit 53, the controller 32 opens the electromagnetic valve 21 (for heating) and opens the indoor expansion valve 8. Fully closed. Further, the electromagnetic valve 22 (for dehumidification) is closed. The shutter 23 is opened and the auxiliary expansion valve 73 is fully closed.

Then, the compressor 2 and the

blowers

15 and 27 are operated, and the air mix damper 28 is in a state of adjusting the ratio of the air blown from the indoor blower 27 to the radiator 4. Thereby, 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 passed 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. Deprived, cooled, and condensed into liquid.

The refrigerant liquefied in the radiator 4 exits the radiator 4 and then flows into the refrigerant pipe 13J (outdoor heat exchanger inlet side circuit) through the refrigerant pipe 13E and the branch member B1 and reaches the outdoor expansion valve 6. The refrigerant flowing into the outdoor expansion valve 6 is decompressed there and then flows into the outdoor heat exchanger 7. The refrigerant flowing into the outdoor heat exchanger 7 evaporates, and pumps up heat from the outside air that is ventilated by traveling or by the outdoor blower 15 (heat absorption). That is, the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the accumulator 12 through the refrigerant pipe 13C through the refrigerant pipe 13A, the refrigerant pipe 13D, and the electromagnetic valve 21, and is separated into gas and liquid there. Repeated circulation inhaled. Since the air heated by the radiator 4 is blown out from the air outlet 29, the vehicle interior is thereby heated.

The controller 32 calculates a target radiator pressure PCO (target value of the pressure PCI of the radiator 4) from a target heater temperature TCO (target value of the air temperature on the leeward side of the radiator 4) calculated from a target outlet temperature TAO described later. The number of revolutions of the compressor 2 is controlled based on this 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 degree of the outdoor expansion valve 6 is controlled based on the temperature of the radiator 4 (the 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 supercooling of the refrigerant at the outlet of the vessel 4 is controlled. The target heater temperature TCO is basically set to TCO = TAO, but a predetermined restriction on control is provided.

(2) Dehumidifying and Heating Operation Next, the dehumidifying and heating operation will be described with reference to FIG. FIG. 4 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying heating operation. In the dehumidifying heating operation, the controller 32 opens the electromagnetic valve 22 (dehumidifying valve) in the heating operation state, and opens the indoor expansion valve 8 so that the refrigerant is decompressed and expanded. The shutter 23 is opened and the auxiliary expansion valve 73 is fully closed. Thereby, a part of the condensed refrigerant flowing out of the radiator 4 and flowing through the refrigerant pipe 13E is diverted to the refrigerant pipe 13F by the branch member B1, and the diverted refrigerant reaches the branch member B2 via the electromagnetic valve 22, The refrigerant flows into the pipe 13B (heat absorber inlet side circuit) and flows into the indoor expansion valve 8, and the remaining refrigerant flows into the refrigerant pipe 13J and flows into the outdoor expansion valve 6. That is, a part of the divided refrigerant is decompressed by the indoor expansion valve 8 and then flows into the heat absorber 9 to evaporate. At this time, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R.

The controller 32 controls the opening degree of the indoor expansion valve 8 so that the degree of superheat (SH) of the refrigerant at the outlet of the heat absorber 9 is maintained at a predetermined value. Since moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, the air is cooled and dehumidified. The remaining refrigerant that is divided and flows into the refrigerant pipe 13J is depressurized by the outdoor expansion valve 6 and then evaporated by the outdoor heat exchanger 7.

The refrigerant evaporated in the heat absorber 9 flows out to the refrigerant pipe 13C and merges with the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), and then repeats circulation sucked into the compressor 2 through the accumulator 12. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed.

The controller 32 controls the rotational 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. 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.

(3) Internal cycle operation (dehumidification operation)
Next, the internal cycle operation as the dehumidifying operation in the present invention will be described with reference to FIG. FIG. 5 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the internal cycle operation. In the internal cycle operation, the controller 32 fully closes the outdoor expansion valve 6 in the dehumidifying and heating operation state (fully closed position). However, the solenoid valve 21 is kept open, and the refrigerant outlet of the outdoor heat exchanger 7 is communicated with the refrigerant suction side of the compressor 2. That is, since this internal cycle operation is a state in which the outdoor expansion valve 6 is fully closed by the control of the outdoor expansion valve 6 in the dehumidifying and heating operation, this internal cycle operation can also be regarded as a part of the dehumidifying and heating operation ( The shutter 23 is open and the auxiliary expansion valve 73 is fully closed).

However, since the inflow of the refrigerant to the outdoor heat exchanger 7 is blocked by closing the outdoor expansion valve 6, all the condensed refrigerant flowing through the refrigerant pipe 13E via the radiator 4 is supplied from the branch member B1. It flows into the pipe 13F and reaches the branch member B2 via the electromagnetic valve 22. Therefore, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. The refrigerant enters the refrigerant pipe 13B (heat absorber inlet side circuit) from the branch member B2 and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13 C and repeats circulation that is sucked into the compressor 2 through the accumulator 12. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed. Since the refrigerant is circulated between the radiator 4 (radiation) and the heat absorber 9 (heat absorption) in the passage 3, heat from the outside air is not pumped up, and heating for the consumed power of the compressor 2 is performed. Ability is demonstrated. Since the entire amount of the refrigerant flows through the heat absorber 9 that exhibits the dehumidifying action, the dehumidifying capacity is higher than the dehumidifying and heating operation, but the heating capacity is lowered.

Although the outdoor expansion valve 6 is closed, the electromagnetic valve 21 is open, and the refrigerant outlet of the outdoor heat exchanger 7 communicates with the refrigerant suction side of the compressor 2, so that the liquid in the outdoor heat exchanger 7 is The refrigerant flows out through the refrigerant pipe 13D and the electromagnetic valve 21 to the refrigerant pipe 13C, is collected by the accumulator 12, and the outdoor heat exchanger 7 is in a gas refrigerant state. Thereby, compared with when the solenoid valve 21 is closed, the amount of refrigerant circulating in the refrigerant circuit R increases, and the heating capacity in the radiator 4 and the dehumidifying capacity in the heat absorber 9 can be improved.

The controller 32 controls the rotational speed of the compressor 2 based on the temperature of the heat absorber 9 or the above-described radiator pressure PCI (high pressure of the refrigerant circuit R). At this time, the controller 32 controls the compressor 2 by selecting the lower one of the compressor target rotational speeds obtained from either calculation, depending on the temperature of the heat absorber 9 or the radiator pressure PCI.

(4) Dehumidifying and Cooling Operation Next, the dehumidifying and cooling operation will be described with reference to FIG. FIG. 6 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying and cooling operation. In the dehumidifying and cooling operation, the controller 32 opens the indoor expansion valve 8 to make the refrigerant decompress and expand, and closes the electromagnetic valve 21 and the electromagnetic valve 22. And the compressor 2 and each

air blower

15 and 27 are drive | operated, and the air mix damper 28 sets it as the state which adjusts the ratio by which the air blown out from the indoor air blower 27 is ventilated by the heat radiator 4. FIG. The shutter 23 is opened and the auxiliary expansion valve 73 is fully closed. Thereby, 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 passed 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 and cooled, and condensates.

The refrigerant exiting the radiator 4 flows from the branching member B1 to the refrigerant pipe 13J (outdoor heat exchanger inlet side circuit) through the refrigerant pipe 13E and reaches the outdoor expansion valve 6. And it flows in into the outdoor heat exchanger 7 through the outdoor expansion valve 6 controlled by an open feeling. The refrigerant flowing into the outdoor heat exchanger 7 is cooled and condensed by running there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B (heat absorber inlet side circuit) from the branch member B2 via the refrigerant pipe 13A and the check valve 18, and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and repeats circulation sucked into the compressor 2 through the refrigerant pipe 13C. Air that has been cooled and dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4 (reheating: lower heat dissipation capacity than during heating), so that dehumidification and cooling of the passenger compartment is performed. become.

The 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 that is the target value. While controlling the rotation speed of the compressor 2, the target radiator pressure PCO (radiator pressure PCI) calculated from the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 and the target heater temperature TCO. 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.

(5) Cooling operation Next, the cooling operation will be described. The flow of the refrigerant circuit R is the same as in the dehumidifying and cooling operation of FIG. In the cooling operation, the controller 32 fully opens the valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling operation state. Note that the air mix damper 28 is in a state of adjusting the ratio of air passing through the radiator 4. The shutter 23 is opened and the auxiliary expansion valve 73 is fully closed.

Thereby, 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 to the radiator 4, the ratio is small (because of only reheating during cooling), so this almost passes through, and the refrigerant exiting the radiator 4 is The refrigerant pipe 13E is entered from the branch member B1 through the refrigerant pipe 13E, and reaches the outdoor expansion valve 6. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through the refrigerant expansion pipe 13J through the outdoor expansion valve 6 and flows into the outdoor heat exchanger 7, where it is ventilated by running or by the outdoor blower 15. It is air-cooled by the outside air and is condensed and liquefied.

The refrigerant that has exited the outdoor heat exchanger 7 reaches the branching member B2 through the refrigerant pipe 13A and the check valve 18. That is, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. The refrigerant enters the refrigerant pipe 13 B (heat absorber inlet side circuit) from the branch member B 2 and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, and the air is cooled.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and repeats circulation sucked into the compressor 2 through the refrigerant pipe 13C. The air cooled and dehumidified by the heat absorber 9 is blown out from the outlet 29 into the vehicle interior, thereby cooling the vehicle interior. In this cooling operation, the controller 32 controls the rotational 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.

(6) Switching of air conditioning operation The controller 32 calculates the target blowing temperature TAO described above from the following formula (I). This target blowing temperature TAO is a target value of the temperature of the air blown out from the blowout port 29 into the vehicle interior.
TAO = (Tset−Tin) × K + Tbal (f (Tset, SUN, Tam))
.. (I)
Here, Tset is the set temperature in the passenger compartment set by the air conditioning operation unit 53, Tin is the temperature of the passenger compartment 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 This is a balance value calculated from the amount of solar radiation SUN to be performed and the outside air temperature Tam detected by the outside air temperature sensor 33. And generally this target blowing temperature TAO is so high that the outside temperature Tam is low, and it falls as the outside temperature Tam rises.

The controller 32 selects one of the above air conditioning operations based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target outlet temperature TAO at the time of activation. In addition, after the activation, the air conditioning operations are selected and switched in accordance with changes in the environment and setting conditions such as the outside air temperature Tam and the target blowing temperature TAO.

(7) Temperature Adjustment of Battery 55 Next, temperature adjustment control of the battery 55 by the controller 32 will be described with reference to FIGS. Here, the temperature of the battery 55 changes depending on the outside air temperature, and the temperature also changes due to self-heating. When the outside air temperature is a high temperature environment or a very low temperature environment, the temperature of the battery 55 becomes extremely high or extremely low, and charging and discharging become difficult. For example, charging is difficult when the temperature of the battery 55 is + 45 ° C. or higher, and discharging is difficult when the temperature is 60 ° C. or higher. In addition, even below −20 ° C., it becomes difficult to discharge, and charging becomes almost impossible.

Therefore, the controller 32 of the vehicle air conditioner 1 according to the embodiment controls the temperature of the battery 55 by the battery temperature adjusting device 61 while performing the air conditioning operation as described above or while the air conditioning operation is stopped. Adjust within the specified temperature range (operating temperature range). Since the specified temperature range of the battery 55 is generally + 20 ° C. or higher and + 40 ° C. or lower, in the embodiment, the temperature of the battery 55 (battery temperature Tb) detected by the battery temperature sensor 76 is within the specified temperature range. A target battery temperature TBO (for example, + 20 ° C.) that is a target value is set.

(7-1) Heating / Battery Temperature Control Mode When it is necessary to adjust the temperature of the battery 55 in the heating operation described above, the controller 32 executes the heating / battery temperature control mode. FIG. 7 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in the heating / battery temperature control mode.

In this heating / battery temperature control mode, the controller 32 further opens the electromagnetic valve 22 (dehumidification valve) and the auxiliary expansion valve 73 in the heating operation state of the refrigerant circuit R shown in FIG. The state to be controlled. Then, the circulation pump 62 of the battery temperature adjusting device 61 is operated. Thereby, a part of refrigerant | coolant which came out from the heat radiator 4 is branched by branch member B1, and reaches branch member B2 of the refrigerant | coolant upstream side of the indoor expansion valve 8 through refrigerant | coolant piping 13F. That is, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. The refrigerant enters the branch pipe 72 from the branch member B2, is decompressed by the auxiliary expansion valve 73, flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 via the branch pipe 72, and evaporates. At this time, an endothermic effect is exhibited. The refrigerant evaporated in the refrigerant flow path 64B is repeatedly circulated through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 and then sucked into the compressor 2 (indicated by solid arrows in FIG. 7).

On the other hand, the heat medium discharged from the circulation pump 62 reaches the heat medium heater 66, where it is heated (when the heat medium heater 66 generates heat), and then in the heat medium pipe 68, the refrigerant-heat medium heat The heat medium flow path 64A of the exchanger 64 is reached, where heat is absorbed by the refrigerant evaporated in the refrigerant flow path 64B, and the heat medium is cooled. The heat medium heated by the heat medium heater 66 and / or cooled by the endothermic action of the refrigerant leaves the refrigerant-heat medium heat exchanger 64 and reaches the battery 55, and after exchanging heat with the battery 55, The circulation sucked into the circulation pump 62 is repeated (indicated by broken line arrows in FIG. 7).

The controller 32, for example, constantly flows the refrigerant through the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and constantly cools the heat medium, based on the battery temperature Tb and the target battery temperature TBO detected by the battery temperature sensor 76. By controlling the heat generation of the heat medium heater 66, the battery temperature Tb is made equal to the target battery temperature TBO (in this case, whether the heating / battery temperature adjustment mode is always executed instead of the heating operation) Or, the heating operation and the heating / battery temperature control mode are switched and executed). Alternatively, when the battery temperature Tb> the target battery temperature TBO + α is satisfied during the heating operation, the mode shifts to the heating / battery temperature control mode, the auxiliary expansion valve 73 is controlled to lower the battery temperature Tb, and the battery temperature Tb <target Even when the battery temperature TBO-α is reached, the heating operation is shifted to the heating / battery temperature control mode, and the heat medium heater 66 is heated to raise the battery temperature Tb, whereby the battery temperature Tb becomes the target battery temperature TBO. To be. As described above, the controller 32 adjusts the temperature Tb of the battery 55 to the target battery temperature TBO that is within the specified temperature range.

(7-2) Cooling / Battery Temperature Control Mode Next, when it is necessary to adjust the temperature of the battery 55 in the above-described cooling operation, the controller 32 executes the cooling / battery temperature control mode. FIG. 8 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in the cooling / battery temperature control mode.

In this cooling / battery temperature control mode, the controller 32 opens the auxiliary expansion valve 73 to control the valve opening degree in the state of the refrigerant circuit R in the cooling operation of FIG. 62 is also operated so that the refrigerant and heat medium heat exchanger 64 exchange heat between the refrigerant and the heat medium.

Thereby, the high-temperature refrigerant discharged from the compressor 2 flows into the outdoor heat exchanger 7 from the branching member B1 through the radiator 4, and exchanges heat with the outside air and traveling air that is ventilated by the outdoor blower 15. Dissipates heat and condenses. A part of the refrigerant condensed in the outdoor heat exchanger 7 reaches the branch member B2. That is, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. The refrigerant reaches the indoor expansion valve 8 through the branch member B2, is decompressed there, and then flows into the heat absorber 9 to evaporate. Since the air in the air flow passage 3 is cooled by the heat absorption action at this time, the passenger compartment is cooled.

The remaining refrigerant condensed in the outdoor heat exchanger 7 is diverted to the branch pipe 72 by the branch member B2, decompressed by the auxiliary expansion valve 73, and then evaporated in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. . Since the refrigerant absorbs heat from the heat medium circulating in the battery temperature adjusting device 61, the battery 55 is cooled in the same manner as described above. The refrigerant from the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and the refrigerant from the refrigerant-heat medium heat exchanger 64 is also passed from the refrigerant pipe 74 through the accumulator 12 to the compressor 2. Will be inhaled.

In this cooling / battery temperature adjustment mode, the controller 32 replaces the cooling operation, switches between the refrigerant operation and the cooling / battery temperature adjustment mode, or starts from the cooling operation similarly to the heating / battery temperature adjustment mode described above. By shifting to the cooling / battery temperature control mode and controlling the auxiliary expansion valve 73 and the heat medium heater 66, the temperature Tb of the battery 55 is adjusted to the target battery temperature TBO within the specified temperature range.

(7-3) Dehumidifying Cooling / Battery Temperature Control Mode Next, when it is necessary to adjust the temperature of the battery 55 during the above-described dehumidifying cooling operation, the controller 32 executes the dehumidifying cooling / battery temperature control mode. . The refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in this dehumidifying cooling / battery temperature control mode are the same as those in FIG. Is controlled by opening rather than fully opening. Then, the controller 32 controls the auxiliary expansion valve 73 and the heat medium heater 66 to control the temperature Tb of the battery 55 to the target battery temperature TBO within the specified temperature range, as in the cooling / battery temperature adjustment mode. adjust.

(7-4) Internal Cycle / Battery Temperature Control Mode Next, when it is necessary to adjust the temperature of the battery 55 in the above-described internal cycle operation, the controller 32 executes the internal cycle / battery temperature control mode. In this internal cycle / battery temperature adjustment mode, the controller 32 opens the auxiliary expansion valve 73 to control the valve opening degree in the state of the refrigerant circuit R in the internal cycle operation of FIG. The circulation pump 62 is also operated so that the refrigerant and heat medium heat exchanger 64 exchange heat between the refrigerant and the heat medium. FIG. 9 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in the internal cycle / battery temperature control mode.

Thereby, the high-temperature refrigerant discharged from the compressor 2 is radiated by the radiator 4, and then flows entirely from the branch member B1 to the refrigerant pipe 13F via the electromagnetic valve 22. And the refrigerant | coolant which came out of the refrigerant | coolant piping 13F reaches branch member B2. That is, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. A part of the refrigerant reaches from the branch member B2 through the refrigerant pipe 13B to the indoor expansion valve 8, where the pressure is reduced, and then the refrigerant flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.

The remainder of the refrigerant that has exited the refrigerant pipe 13F is diverted to the branch pipe 72 by the branch member B2, is depressurized by the auxiliary expansion valve 73, and then evaporates in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. Since the refrigerant absorbs heat from the heat medium circulating in the battery temperature adjusting device 61, the battery 55 is cooled in the same manner as described above. The refrigerant from the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and the refrigerant from the refrigerant-heat medium heat exchanger 64 is also passed from the refrigerant pipe 74 through the accumulator 12 to the compressor 2. Will be inhaled.

In this internal cycle / battery temperature adjustment mode, the controller 32 replaces the internal cycle operation or switches between the internal cycle operation and the internal cycle / battery temperature adjustment mode, as in the heating / battery temperature adjustment mode described above, or Then, the internal cycle operation is shifted to the internal cycle / battery temperature control mode, and the auxiliary expansion valve 73 and the heat medium heater 66 are controlled to adjust the temperature Tb of the battery 55 to the target battery temperature TBO within the specified temperature range. To do.

(7-5) Dehumidifying Heating / Battery Temperature Control Mode Next, when it is necessary to adjust the temperature of the battery 55 in the above-described dehumidifying heating operation, the controller 32 executes the dehumidifying heating / battery temperature control mode. In the dehumidifying heating / battery temperature control mode, the controller 32 opens the auxiliary expansion valve 73 to control the valve opening degree in the state of the refrigerant circuit R in the dehumidifying heating operation of FIG. The circulation pump 62 is also operated so that the refrigerant and heat medium heat exchanger 64 exchange heat between the refrigerant and the heat medium. FIG. 10 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in the dehumidifying heating / battery temperature control mode.

As a result, a part of the condensed refrigerant that has exited the radiator 4 is diverted by the branch member B1, and the diverted refrigerant flows into the refrigerant pipe 13F through the electromagnetic valve 22 and exits from the refrigerant pipe 13F. The part flows from the branch member B2 to the indoor expansion valve 8 through the refrigerant pipe 13B, and the remaining refrigerant flows to the outdoor expansion valve 6. That is, after a part of the divided refrigerant is decompressed by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. At this time, moisture in the air blown out from the indoor blower 27 is condensed and attached to the heat absorber 9 by the heat absorption action of the refrigerant generated in the heat absorber 9, so that the air is cooled and dehumidified. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed. The remaining condensed refrigerant from the radiator 4 flows from the branch member B1 to the refrigerant pipe 13J, is decompressed by the outdoor expansion valve 6, is evaporated by the outdoor heat exchanger 7, and absorbs heat from the outside air.

On the other hand, the remainder of the refrigerant exiting the refrigerant pipe 13F flows into the branch pipe 72 through the branch member B2, is decompressed by the auxiliary expansion valve 73, and evaporates in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. . Since the refrigerant absorbs heat from the heat medium circulating in the battery temperature adjusting device 61, the battery 55 is cooled in the same manner as described above. Note that the refrigerant discharged from the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and the refrigerant discharged from the outdoor heat exchanger 7 passes through the refrigerant pipe 13D, the electromagnetic valve 21, the refrigerant pipe 13C, and the accumulator 12. Then, the refrigerant that has been sucked into the compressor 2 and has exited the refrigerant-heat medium heat exchanger 64 is also sucked into the compressor 2 from the refrigerant pipe 74 through the accumulator 12.

In this dehumidifying heating / battery temperature adjustment mode, the controller 32 replaces the dehumidifying heating operation, or switches between the dehumidifying heating operation and the dehumidifying heating / battery temperature adjustment mode, as in the above-described heating / battery temperature adjustment mode, or Then, the dehumidifying heating operation is shifted to the dehumidifying heating / battery temperature control mode, and the auxiliary expansion valve 73 and the heat medium heater 66 are controlled to adjust the temperature Tb of the battery 55 to the target battery temperature TBO within the specified temperature range. To do.

(7-6) Battery Temperature Control Single Mode Next, a battery temperature control single mode that controls the temperature of the battery 55 without air conditioning the vehicle interior will be described. FIG. 11 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the battery temperature adjusting device 61 in the battery temperature adjustment single mode. The controller 32 compressor 2 is operated and the outdoor fan 15 is also operated. The indoor expansion valve 8 is fully closed and the auxiliary expansion valve 37 is opened to depressurize the refrigerant. The outdoor expansion valve 6 is fully opened. Further, the controller 32 closes the electromagnetic valve 17 and the electromagnetic valve 21 and stops the indoor blower 27. Then, the circulation pump 62 is operated so that the refrigerant and the heat medium heat exchanger 64 exchange heat between the refrigerant and the heat medium.

Thus, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 passes through the radiator 4 and enters the refrigerant pipe 13J from the refrigerant pipe 13E through the branch member B1 and reaches the outdoor expansion valve 6. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through the refrigerant pipe 13J, flows into the outdoor heat exchanger 7 as it is, is cooled by the outside air ventilated by the outdoor blower 15, and is condensed and liquefied. In the case where frost has grown on the outdoor heat exchanger 7, the outdoor heat exchanger 7 is defrosted by the heat dissipation action at this time.

The refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13A and reaches the branch member B2. That is, also in this case, the position of the branch member B2 is set to the high pressure side of the refrigerant circuit R. At this time, since the indoor expansion valve 8 is fully closed, all the refrigerant that has exited the outdoor heat exchanger 7 reaches the auxiliary expansion valve 73 from the branch member B2 through the branch pipe 72. The refrigerant is decompressed by the auxiliary expansion valve 73 and then flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 to evaporate. At this time, an endothermic effect is exhibited. The refrigerant evaporated in the refrigerant flow path 64B is repeatedly circulated through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 in order and sucked into the compressor 2.

On the other hand, the heat medium discharged from the circulation pump 62 is heated through the heat medium heater 66 (when the heat medium heater 66 generates heat), and the heat medium pipe 68 is filled with the refrigerant-heat medium heat exchanger 64. The heat medium channel 64A is reached, where heat is absorbed by the refrigerant evaporated in the refrigerant channel 64B, and the heat medium is cooled. The heat medium heated by the heat medium heater 66 and / or cooled by the endothermic action of the refrigerant leaves the refrigerant-heat medium heat exchanger 64 and reaches the battery 55, and after exchanging heat with the battery 55, The circulation sucked into the circulation pump 62 is repeated (indicated by broken line arrows in FIG. 11).

In the battery temperature control single mode, the controller 32 controls the auxiliary expansion valve 73 and the heat medium heater 66 to control the temperature Tb of the battery 55 in the specified temperature range in the same manner as in the heating / battery temperature control mode described above. It adjusts to the target battery temperature TBO.

(8) Specific structure of branch member B2, arrangement connection structure of indoor expansion valve 8 and auxiliary expansion valve 73, etc. Next, with reference to FIG. 12 and FIG. 13, the specifics of the aforementioned branch member B2 (branch portion) A general structure and an arrangement connection structure of the refrigerant pipe 13B (heat absorber inlet side circuit), the branch pipe 72 (branch circuit), the refrigerant pipe 13A, the indoor expansion valve 8 and the auxiliary expansion valve 73 will be described.

12 is a plan view of the branching member B2, the indoor expansion valve 8, and the auxiliary expansion valve 73, and FIG. 13 is a front view. The branch member B2 includes a metal block. The branch member B2 includes a first refrigerant inlet IN1 and a second refrigerant inlet IN2, and a first refrigerant outlet OUT1 and a second refrigerant communicated with them inside. The refrigerant outlet OUT2 is provided. The refrigerant pipe 13F is connected to the first refrigerant inlet IN1, and the refrigerant pipe 13A is connected to the second refrigerant inlet IN2.

The refrigerant pipe 13B is connected to the first refrigerant outlet OUT1, and the branch pipe 72 is connected to the second refrigerant outlet OUT2. As shown in FIG. 13, the refrigerant pipe 13B is connected to the first branch member B2. From the refrigerant outlet OUT1. The indoor expansion valve 8 is connected to a side closer to the branch member B2 than the heat absorber 9 in the refrigerant pipe 13B, and thus the indoor expansion valve 8 is disposed at a position higher than the branch member B2.

As shown in FIG. 13, the branch pipe 72 also rises from the second refrigerant outlet OUT 2 of the branch member B 2, and the auxiliary expansion valve 73 is also a branch member than the refrigerant-heat medium heat exchanger 64 of the branch pipe 72. It is connected to the side close to B2. Thereby, the auxiliary expansion valve 73 is also arranged at a position higher than the branch member B2.

With such a configuration, the auxiliary expansion valve 73 is fully closed in the above-described dehumidifying and heating operation, internal cycle operation, dehumidifying and cooling operation, and cooling operation, and the refrigerant from the refrigerant pipe 13F and the refrigerant pipe 13B is used as the indoor expansion valve 8. When the flow is made to flow through, the volume in the branch pipe 72 between the branch member B2 and the auxiliary expansion valve 73 becomes smaller, the amount of refrigerant and oil staying there decreases, and the branch member B2 and the auxiliary expansion valve 73 It becomes difficult for refrigerant and oil to accumulate in the branch pipe 72 between the two.

When the indoor expansion valve 8 is fully closed in the heating / battery temperature adjustment mode and the battery temperature adjustment single mode described above and the refrigerant from the refrigerant pipe 13F and the refrigerant pipe 13B flows to the auxiliary expansion valve 73, the branch member B2 and The volume in the refrigerant pipe 13 B between the indoor expansion valve 8 is reduced, the amount of refrigerant and oil remaining therein is reduced, and the refrigerant is placed in the refrigerant pipe 13 B between the branch member B 2 and the indoor expansion valve 8. And oil does not collect easily.

As described above, the indoor expansion valve 8 is arranged closer to the branch member B2 than the heat absorber 9 in the refrigerant pipe 13B, and the auxiliary expansion valve 73 is branched from the refrigerant-heat medium heat exchanger 64 in the branch pipe 72. If arranged closer to the member B2, the volume of the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8 and the volume of the branch pipe 72 between the branch member B2 and the auxiliary expansion valve 73 are reduced. Will be able to.

As a result, when the auxiliary expansion valve 73 is fully closed, the amount of refrigerant that stays in the branch pipe 72 between the branch member B2 and the auxiliary expansion valve 73 and the amount of oil compatible with the refrigerant are significantly reduced. It is possible to prevent a decrease in the oil circulation rate and improve the reliability of the compressor 2, and it is also possible to prevent an increase in the required refrigerant amount and the required oil amount.

Furthermore, even when the indoor expansion valve 8 is fully closed, the amount of refrigerant that stays in the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8 and the amount of oil that is compatible therewith are significantly reduced. Similarly, a decrease in the oil circulation rate can be prevented, the reliability of the compressor 2 can be improved, and an increase in the necessary refrigerant amount and the necessary oil amount can be prevented.

In particular, as in the embodiment, a branch portion is constituted by the branch member B2 having the refrigerant inlet IN1 and the first and second refrigerant outlets OUT1 and OUT2, and the refrigerant pipe 13B is connected to the first refrigerant outlet OUT1 of the branch member B2. Thus, the indoor expansion valve 8 is arranged at a position higher than the branch member B2, and the branch pipe 72 is connected to the second refrigerant outlet OUT2 of the branch member B2 so as to rise from the branch member B2. The auxiliary expansion valve 73 is arranged at a position higher than the branch member B2, so that the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8 and the branch member B2 and the auxiliary expansion are arranged. It becomes difficult for refrigerant and oil to accumulate in the branch pipe 72 between the valve 73 and the reduction in the oil circulation rate can be more effectively eliminated.

(9) Specific structure of branch member B1, arrangement and connection structure of outdoor expansion valve 6 and electromagnetic valve 22, etc. Next, referring to FIGS. 14 and 15, the aforementioned branch member B1 (another branch member). Specific structure of another branch), refrigerant pipe 13E, refrigerant pipe 13J (outdoor heat exchanger inlet side circuit), refrigerant pipe 13F (bypass circuit), outdoor expansion valve 6 and electromagnetic valve 22 (dehumidification valve) The arrangement connection structure will be described.

14 is a plan view of the branching member B1, the outdoor expansion valve 6, and the electromagnetic valve 22, and FIG. 15 is a front view. The branch member B1 is also composed of a metal block, and this branch member B1 has a refrigerant inlet IN, and a first refrigerant outlet OUT1 and a second refrigerant outlet OUT2 communicating with it inside. A refrigerant pipe 13E is connected to the refrigerant inlet IN.

The refrigerant pipe 13J is connected to the first refrigerant outlet OUT1 of the branch member B1, and the refrigerant pipe 13F is connected to the second refrigerant outlet OUT2, but the refrigerant pipe 13J is connected to the branch member as shown in FIG. It rises from the first refrigerant outlet OUT1 of B1. The outdoor expansion valve 6 is connected to the side closer to the branching member B1 than the outdoor heat exchanger 7 in the refrigerant pipe 13J, whereby the outdoor expansion valve 6 is arranged at a position higher than the branching member B1. Yes.

Further, as shown in FIG. 15, the refrigerant pipe 13F also rises from the second refrigerant outlet OUT2 of the branch member B1, and the electromagnetic valve 22 also has a branch member B1 that is more than the branch member B2 and the indoor expansion valve 8 in the refrigerant pipe 13F. Connected to the side close to. Thereby, the solenoid valve 22 is also arranged at a position higher than the branch member B1.

With such a configuration, when the electromagnetic valve 22 is closed in the heating operation described above and the refrigerant from the refrigerant pipe 13E flows to the outdoor expansion valve 6, the refrigerant pipe 13F between the branch member B1 and the electromagnetic valve 22 is used. The internal volume is reduced, the amount of refrigerant and oil remaining therein is reduced, and the refrigerant and oil are less likely to accumulate in the refrigerant pipe 13F between the branch member B1 and the electromagnetic valve 22.

Even when the outdoor expansion valve 6 is fully closed in the internal cycle operation and the internal cycle / battery temperature control mode described above, the volume of the refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 is reduced. , Refrigerant and oil are less likely to accumulate there.

In this way, the outdoor expansion valve 6 is disposed closer to the branch member B1 than the outdoor heat exchanger 7 in the refrigerant pipe 13J, and the electromagnetic valve 22 is located more than the branch member B2 and the indoor expansion valve 8 in the refrigerant pipe 13F. If arranged closer to the branch member B1, the volume of the refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 and the volume of the refrigerant pipe 13F between the branch member B1 and the electromagnetic valve 22 are reduced. Will be able to.

As a result, when the electromagnetic valve 22 is closed, the amount of the refrigerant staying in the refrigerant pipe 13F between the branching member B1 and the electromagnetic valve 22 and the amount of oil compatible with the refrigerant is significantly reduced. It is possible to prevent the reduction and improve the reliability of the compressor 2, and it is also possible to prevent an increase in the required refrigerant amount and the required oil amount.

Furthermore, even when the outdoor expansion valve 6 is fully closed, the amount of refrigerant that stays in the refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 and the amount of oil that is compatible therewith is significantly reduced. Similarly, a decrease in the oil circulation rate can be prevented, the reliability of the compressor 2 can be improved, and an increase in the necessary refrigerant amount and the necessary oil amount can be prevented.

In particular, as in the embodiment, another branch portion is constituted by the branch member B1 having the refrigerant inlet IN and the first and second refrigerant outlets OUT1 and OUT2, and the refrigerant pipe 13J is connected to the first refrigerant outlet of the branch member B1. It is connected to OUT1 so as to rise from the branch member B1, and the outdoor expansion valve 6 is arranged at a position higher than the branch member B1, and the refrigerant pipe 13F is connected to the second refrigerant outlet OUT2 of the branch member B1. The refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 and the branch member B1 are arranged so as to rise from the branch member B1 and arrange the electromagnetic valve 22 at a position higher than the branch member B1. It becomes difficult for the refrigerant and oil to accumulate in the refrigerant pipe 13 F between the electromagnetic valve 22 and the reduction in the oil circulation rate can be more effectively eliminated.

It should be noted that the configurations of the refrigerant circuit R and the battery temperature adjusting device 61 described in the embodiments are not limited thereto, and it goes without saying that they can be changed without departing from the spirit of the present invention.

B1 Branch member (another branch member, another branch part)
B2 Branch member (branch part)
DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 2 Compressor 4 Radiator 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat absorber 13B Refrigerant piping (heat absorber inlet side circuit)
13F Refrigerant piping (bypass circuit)
13J Refrigerant piping (Outdoor heat exchanger inlet side circuit)
22 Solenoid valve (dehumidification valve)
32 Controller 55 Battery 61 Battery temperature adjusting device 62 Circulating pump 64 Refrigerant-heat medium heat exchanger 66 Heat medium heater (heating device)
72 Branch piping (branch circuit)
73 Auxiliary expansion valve

Claims

A compressor that compresses the refrigerant, an outdoor heat exchanger provided outside the vehicle compartment, a heat absorber that absorbs the refrigerant and cools the air that is supplied to the vehicle interior, and the refrigerant that flows into the heat absorber. A refrigerant circuit configured to have an indoor expansion valve for depressurization, in which a predetermined amount of the refrigerant and oil are enclosed;
In a vehicle air conditioner that includes a control device and that air-conditions the vehicle interior,
A branch set on the high pressure side of the refrigerant circuit;
From the branch part to the heat absorber, a heat absorber inlet side circuit provided with the indoor expansion valve;
A battery temperature adjusting device for adjusting the temperature of the battery mounted on the vehicle by circulating the heat medium;
The battery temperature adjusting device includes:
A refrigerant-heat medium heat exchanger for exchanging heat between the refrigerant and the heat medium;
A branch circuit from the branch part to the refrigerant-heat medium heat exchanger;
An auxiliary expansion valve provided in the branch circuit for depressurizing the refrigerant flowing into the refrigerant-heat medium heat exchanger;
The control device is capable of performing an operation with the indoor expansion valve or the auxiliary expansion valve fully closed,
The indoor expansion valve is disposed closer to the branch part than the heat absorber in the heat absorber inlet side circuit, and the auxiliary expansion valve is located in the branch circuit than the refrigerant-heat medium heat exchanger. The vehicle air conditioner is disposed on a side close to the branch portion.
The control device fully closes the auxiliary expansion valve, radiates the refrigerant discharged from the compressor in the outdoor heat exchanger, and radiates the radiated refrigerant from the branch portion to the heat absorber inlet side circuit. 2. The vehicle air conditioner according to claim 1, wherein a cooling operation in which heat is absorbed by the heat absorber is performed after flowing and depressurizing by the indoor expansion valve.
The control device fully closes the indoor expansion valve, radiates the refrigerant discharged from the compressor in the outdoor heat exchanger, and flows the radiated refrigerant from the branch section to the branch circuit, 3. The vehicle air conditioner according to claim 1, wherein after the pressure is reduced by an auxiliary expansion valve, a battery temperature adjustment single mode in which heat is absorbed by the refrigerant-heat medium heat exchanger is executed.
A branching member having a refrigerant inlet and first and second refrigerant outlets to constitute the branching portion;
The heat absorber inlet side circuit is connected to the first refrigerant outlet of the branch member and rises from the branch member, the indoor expansion valve is disposed at a position higher than the branch member,
The branch circuit is connected to a second refrigerant outlet of the branch member and rises from the branch member, and the auxiliary expansion valve is disposed at a position higher than the branch member. The vehicle air conditioner according to claim 3.
The refrigerant circuit includes a radiator for heating the air supplied to the vehicle interior by dissipating the refrigerant, and an outdoor heat exchanger inlet for flowing the refrigerant from the radiator to the outdoor heat exchanger A side circuit, an outdoor expansion valve provided in the outdoor heat exchanger inlet side circuit for decompressing the refrigerant flowing into the outdoor heat exchanger, and another set upstream of the refrigerant of the outdoor expansion valve A bypass circuit for branching from one branch part and flowing the refrigerant from the radiator to the indoor expansion valve, and a dehumidification valve provided in the bypass circuit,
The control device is capable of performing an operation in which a flow path is closed by the outdoor expansion valve or the dehumidifying valve,
The outdoor expansion valve is disposed closer to the other branch portion than the outdoor heat exchanger in the outdoor heat exchanger inlet-side piping, and the dehumidification valve is the indoor expansion valve in the bypass circuit. The vehicle air conditioner according to any one of claims 1 to 4, wherein the vehicle air conditioner is disposed closer to the other branch portion than the other branch portion.
The control device closes the dehumidification valve, causes the refrigerant discharged from the compressor to radiate heat with the radiator, and causes the radiated refrigerant to flow from the another branch portion to the outdoor expansion valve. 6. The vehicle air conditioner according to claim 5, wherein a heating operation is performed in which heat is absorbed by the outdoor heat exchanger after the pressure is reduced by the expansion valve.
The control device fully closes the outdoor expansion valve, opens the dehumidification valve, radiates the refrigerant discharged from the compressor with the radiator, and radiates the radiated refrigerant to the another branch portion. The vehicle air conditioner according to claim 5 or 6, wherein a dehumidifying operation is performed in which the dehumidifying operation is performed after flowing into the bypass circuit and depressurizing with the indoor expansion valve and then absorbing heat with the heat absorber.
Another branch member having a refrigerant inlet and first and second refrigerant outlets to constitute the other branch portion;
The circuit on the inlet side of the outdoor heat exchanger is connected to the first refrigerant outlet of the other branch member and rises from the other branch member, and the outdoor expansion valve is positioned higher than the other branch member. And placed
The bypass circuit is connected to a second refrigerant outlet of the other branch member and rises from the other branch member, and the dehumidification valve is disposed at a position higher than the other branch member. A vehicle air conditioner according to any one of claims 5 to 7.