JP7185412B2 - Vehicle air conditioner - Google Patents

Description

TECHNICAL FIELD The present invention relates to a heat pump type air conditioner for air-conditioning the interior of a vehicle, and more particularly to a vehicle air conditioner suitable for an electric vehicle or a hybrid vehicle equipped with a battery.

BACKGROUND ART Vehicles such as hybrid vehicles and electric vehicles, in which a motor for driving is driven by electric power supplied from a battery, have come into wide use due to the emergence of environmental problems in recent years. An air conditioner (refrigerating cycle device) that can be applied to such a vehicle includes a refrigerant circuit including a compressor, a condenser, an expansion valve for cooling, an indoor evaporator, and the like. It has been developed to drive the compressor with power supplied from the

In addition, since it is difficult to charge and discharge the battery in high temperature or extremely low temperature conditions, and deterioration also occurs, an evaporator for battery cooling is provided, and a double pipe branched from the branch set in the pipe to the indoor evaporator is used to cool the battery. The refrigerant pressure-reduced by the expansion valve is supplied to the battery-cooling evaporator to cool the battery (secondary battery) (see, for example, Patent Document 1). Furthermore, in this patent document 1, when the solenoid valve on the battery expansion valve side is closed, the amount of refrigerant present in the double pipe that is on the high pressure side is reduced, and in order to reduce the required amount of refrigerant, the battery The expansion valve was placed on the side near the bifurcation to the double pipe.

Japanese Patent No. 5884725

However, the refrigerant also accumulates between the branch portion on the high pressure side and the solenoid valve on the cooling expansion valve side. In addition, since the refrigerant contains lubricating oil dissolved in it, the circulation rate of the oil in the refrigerant circuit decreases. A problem arises that it becomes impossible to maintain. This will be described with reference to FIG. FIG. 16 shows compatibility curves of oil 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 (gas state refrigerant with a degree of superheat), the refrigerant dissolution amount (dissolution amount of oil in the refrigerant) is 50mas%. 100 mass% in the state of liquid refrigerant lower than that.

This is because the gas refrigerant has a low density and the amount of refrigerant that can be retained in the same volume is small, so the amount of oil that can be compatible with each other is also small. That is, since the piping on the low-pressure side is heated by the outside air and becomes gaseous, the amount of oil that can be compatible with the oil is also reduced. On the other hand, the refrigerant on the high-pressure side is cooled by the outside air and liquefied, so that it becomes compatible with a large amount of oil. Therefore, as described above, when the volume on the high pressure side between the branching portion and the solenoid valve on the cooling expansion valve side increases, a large amount of oil is retained and the oil circulation rate (OCR) decreases. .

SUMMARY OF THE INVENTION The present invention has been made to solve such conventional technical problems. An object of the present invention is to provide an air conditioner for a vehicle that can be avoided in advance.

A vehicle air conditioner of the present invention includes a compressor that compresses a refrigerant, an outdoor heat exchanger provided outside the vehicle, a heat absorber that absorbs heat from the refrigerant and cools the air that is supplied to the vehicle, It is configured to have an indoor expansion valve for decompressing the refrigerant flowing into the heat absorber, is equipped with a refrigerant circuit in which a predetermined amount of refrigerant and oil are sealed, and a controller, and air-conditions the interior of the vehicle. , a branch portion set on the high-pressure side of the refrigerant circuit, a heat absorber from this branch portion, a heat absorber inlet side circuit provided with an indoor expansion valve, and a refrigerant outlet side of the outdoor heat exchanger to the branch portion. A refrigerant pipe, a check valve provided in this refrigerant pipe and having a forward direction on the heat absorber inlet circuit side, another branch set on the refrigerant inlet side of the outdoor heat exchanger, and this other A bypass circuit that communicates with the branched portion to bypass the outdoor heat exchanger and the check valve, and a battery temperature adjustment device that circulates the heat medium and adjusts the temperature of the battery mounted on the vehicle. The battery temperature adjustment device includes a refrigerant-heat medium heat exchanger for exchanging heat between a refrigerant and a heat medium, a branch circuit extending from a branch portion to the refrigerant-heat medium heat exchanger, and a branch circuit provided in the branch circuit. , has an auxiliary expansion valve for decompressing the refrigerant flowing into the refrigerant-heat medium heat exchanger, and the control device is capable of executing operation with the indoor expansion valve or the auxiliary expansion valve fully closed, The expansion valve is arranged closer to the branch than the heat absorber in the heat absorber inlet circuit, and the auxiliary expansion valve is arranged closer to the branch than the refrigerant-heat medium heat exchanger in the branch circuit. and another branch member having a refrigerant inlet and first and second refrigerant outlets to form the another branch, and a dehumidification valve provided in the bypass circuit, wherein the bypass circuit The dehumidifying valve is connected to the second refrigerant outlet of one branch member and rises from the other branch member, and is arranged at a position higher than the another branch member.

In the vehicle air conditioner of the invention of claim 2, in the above invention, the control device fully closes the auxiliary expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, and dissipates the radiated refrigerant. It is characterized in that cooling operation is performed by flowing the air from the branch to the heat absorber inlet side circuit, reducing the pressure by the indoor expansion valve, and then absorbing the heat by the heat absorber.

In the vehicle air conditioner of the invention of claim 3, in each of the above inventions, the control device fully closes the indoor expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, and heats the refrigerant discharged from the compressor. is flowed from the branch to the branch circuit, the pressure is reduced by the auxiliary expansion valve, and then the heat is absorbed by the refrigerant-heat medium heat exchanger.

The vehicle air conditioner of the invention of claim 4 is provided with a branching member having a refrigerant inlet and first and second refrigerant outlets in each of the above inventions and constituting a branching part, and the heat absorber inlet side circuit is a branching member The indoor expansion valve is arranged at a position higher than the branch member, and the branch circuit is connected to the second refrigerant outlet of the branch member and rises from the branch member. and the auxiliary expansion valve is arranged at a position higher than the branch member.

In the vehicle air conditioner of the invention of claim 5, in each of the above inventions, the refrigerant circuit comprises a radiator for radiating the refrigerant to heat the air supplied to the vehicle interior, and a radiator for heating the air supplied to the vehicle interior, An outdoor heat exchanger inlet side circuit for flowing to the exchanger, and an outdoor expansion valve provided in the outdoor heat exchanger inlet side circuit for decompressing the refrigerant flowing into the outdoor heat exchanger. , the refrigerant branched from the other branch set on the upstream side of the refrigerant of the outdoor expansion valve and flowed from the radiator to the indoor expansion valve, and the control device causes the flow path to be diverted by the outdoor expansion valve or the dehumidification valve Closed operation can be executed, the outdoor expansion valve is arranged closer to another branch than the outdoor heat exchanger in the outdoor heat exchanger inlet piping, and the dehumidification valve is a bypass circuit It is characterized in that it is arranged closer to the other branch than the indoor expansion valve.

In the vehicle air conditioner of the invention of claim 6, in the above invention, the control device closes the dehumidification valve, causes the refrigerant discharged from the compressor to dissipate heat in the radiator, and transfers the heat-dissipated refrigerant to another branch portion. It is characterized in that the air is flowed from the outside to the outdoor expansion valve, and after the pressure is reduced by the outdoor expansion valve, the heating operation is performed in which the heat is absorbed by the outdoor heat exchanger.

In the vehicle air conditioner of the invention of claim 7, in the invention of claim 5 or 6, the control device fully closes the outdoor expansion valve and opens the dehumidification valve to dissipate heat from the refrigerant discharged from the compressor. After the heat is radiated by the device, the heat-dissipated refrigerant is made to flow from another branch to the bypass circuit, the pressure is reduced by the indoor expansion valve, and then the heat is absorbed by the heat absorber to perform the dehumidifying operation.

In the vehicle air conditioner of the invention of claim 8, in the invention of claims 5 to 7 , the outdoor heat exchanger inlet side circuit is connected to a first refrigerant outlet of another branch member, Rising from the branch member, the outdoor expansion valve is arranged at a position higher than another branch member.

According to the present invention, a compressor for compressing a refrigerant, an outdoor heat exchanger provided outside the vehicle, a heat absorber for absorbing heat from the refrigerant and cooling the air supplied to the vehicle, and the heat absorber A vehicular air conditioner for air conditioning a vehicle interior, comprising a refrigerant circuit having a refrigerant circuit in which a predetermined amount of refrigerant and oil are sealed, and a control device, which is configured to have an indoor expansion valve for decompressing an inflowing refrigerant. , a branch portion set on the high-pressure side of the refrigerant circuit, a heat absorber from this branch portion, a heat absorber inlet side circuit provided with an indoor expansion valve, and a refrigerant outlet side of the outdoor heat exchanger to the branch portion. A refrigerant pipe, a check valve provided in this refrigerant pipe and having a forward direction on the heat absorber inlet circuit side, another branch set on the refrigerant inlet side of the outdoor heat exchanger, and this other A bypass circuit that communicates with the branched portion to bypass the outdoor heat exchanger and the check valve, and a battery temperature adjustment device that circulates the heat medium and adjusts the temperature of the battery mounted on the vehicle. comprising a refrigerant-heat medium heat exchanger for exchanging heat between a refrigerant and a heat medium; a branch circuit extending from a branch portion to the refrigerant-heat medium heat exchanger; and a branch circuit provided in the branch circuit. , which has an auxiliary expansion valve for decompressing the refrigerant flowing into the refrigerant-heat medium heat exchanger, and the control device can execute the operation with the indoor expansion valve or the auxiliary expansion valve fully closed , the indoor expansion valve is arranged on the side of the heat absorber inlet side closer to the branch than the heat absorber, and the auxiliary expansion valve is arranged on the side of the branch circuit closer to the branch than the refrigerant-heat medium heat exchanger. Due to the arrangement, the volume of the heat absorber inlet side circuit between the branch and the indoor expansion valve and the volume of the branch circuit between the branch and the auxiliary expansion valve can be reduced.

As a result, when the refrigerant flows through the bypass circuit, the check valve prevents the refrigerant from flowing back from the branch to the refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger. Therefore, it is possible to prevent the problem that the circulation amount of the oil is reduced. In particular, another branch member having a refrigerant inlet and first and second refrigerant outlets constitutes another branch, the bypass circuit is provided with a dehumidification valve, and the bypass circuit is connected to the second branch member of the other branch member. 2, and the dehumidification valve is arranged at a position higher than the other branch member. Refrigerant and oil are less likely to accumulate in the bypass circuit, and the drop in oil circulation rate can be more effectively resolved. Further, for example, as in the invention of claim 2, the control device fully closes the auxiliary expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, and radiates the heat-dissipated refrigerant from the branch to the heat absorber inlet. When performing cooling operation in which the refrigerant is flowed to the side circuit, decompressed by the indoor expansion valve, and then absorbed by the heat absorber, the refrigerant remaining in the branch circuit between the branch and the auxiliary expansion valve is mixed with the refrigerant. It is possible to significantly reduce the amount of oil used, prevent a decrease in the oil circulation rate, improve the reliability of the compressor, and prevent an increase in the amount of refrigerant and oil required. become.

Furthermore, for example, as in the invention of claim 3, the control device fully closes the indoor expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, and transfers the radiated refrigerant from the branch to the branch circuit. In the heat absorber inlet side circuit between the branch part and the indoor expansion valve It is possible to significantly reduce the amount of refrigerant staying in and the oil dissolved in it, similarly prevent a decrease in the oil circulation rate, improve the reliability of the compressor, and increase the required amount of refrigerant and An increase in the required amount of oil can also be prevented.

In particular, as in the invention of claim 4, the branching portion is configured from branching members having a refrigerant inlet and first and second refrigerant outlets, and the heat absorber inlet side circuit is connected to the first refrigerant outlet of the branching member. The indoor expansion valve is arranged at a position higher than the branch member, the branch circuit is connected to the second refrigerant outlet of the branch member so as to rise from the branch member, and the auxiliary expansion valve If it is arranged at a position higher than the branch member, the refrigerant and oil accumulate in the heat absorber inlet side circuit between the branch member and the indoor expansion valve and the branch circuit between the branch member and the auxiliary expansion valve. It becomes difficult, and it becomes possible to more effectively eliminate the decrease in the oil circulation rate.

Further, as in the invention of claim 5, the refrigerant circuit includes a radiator for radiating the refrigerant and heating the air supplied to the vehicle interior, and an outdoor heat exchanger for flowing the refrigerant discharged from the radiator to the outdoor heat exchanger. An exchanger inlet side circuit and 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 bypass circuit is upstream of the outdoor expansion valve. , the refrigerant discharged from the radiator is allowed to flow to the indoor expansion valve, and the control device can execute the operation with the flow path closed by the outdoor expansion valve or the dehumidification valve. , the outdoor expansion valve is arranged closer to another branch than the outdoor heat exchanger in the outdoor heat exchanger inlet piping, and the dehumidification valve is arranged in the bypass circuit from the indoor expansion valve. Also, by arranging it on the side close to another branch, the volume of the outdoor heat exchanger inlet side circuit between the other branch and the outdoor expansion valve, and the volume of the other branch and the dehumidification valve It becomes possible to reduce the volume of the bypass circuit between.

As a result, for example, as in the invention of claim 6, the control device closes the dehumidification valve, radiates the heat of the refrigerant discharged from the compressor with the radiator, and transfers the heat-dissipated refrigerant from another branch to the outdoor expansion valve. After the pressure is reduced by the outdoor expansion valve, the refrigerant remaining in the bypass circuit between the other branch and the dehumidification valve and the Remarkably reducing the amount of melted oil prevents a drop in the oil circulation rate, improves the reliability of the compressor, and prevents an increase in the amount of refrigerant and oil required. become able to.

Furthermore, for example, as in the invention of claim 7, the control device fully closes the outdoor expansion valve, opens the dehumidification valve, radiates the heat of the refrigerant discharged from the compressor with a radiator, and heats the heat-dissipated refrigerant again. When performing dehumidifying operation in which the air flows from one branch to the bypass circuit, is decompressed by the indoor expansion valve, and then heat is absorbed by the heat absorber, the outdoor heat exchanger inlet between the other branch and the outdoor expansion valve Remarkably reducing the amount of refrigerant remaining in the side circuit and the amount of oil dissolved therein, likewise preventing a drop in the oil circulation rate and improving the reliability of the compressor, the necessary It becomes possible to prevent an increase in the amount of refrigerant and the amount of necessary oil.

In particular, as in the invention of claim 8, the outdoor heat exchanger inlet side circuit is connected to the first refrigerant outlet of another branch member so that it rises from the other branch member, and the outdoor expansion valve is connected to the other branch member. If it is arranged at a position higher than the branch member, it becomes difficult for the refrigerant and oil to accumulate in the outdoor heat exchanger inlet side circuit between the other branch member and the outdoor expansion valve , further reducing the oil circulation rate. can be resolved more effectively.

1 is a configuration diagram of an embodiment of a vehicle air conditioner to which the present invention is applied; FIG. 2 is a control block diagram of a controller (control device) of the vehicle air conditioner of FIG. 1. FIG. 3 is a diagram for explaining heating operation by the controller in FIG. 2; FIG. FIG. 3 is a diagram for explaining dehumidification and heating operation by the controller in FIG. 2; 3 is a diagram for explaining internal cycle operation by the controller of FIG. 2; FIG. FIG. 3 is a diagram for explaining dehumidifying cooling operation/cooling operation by the controller in FIG. 2; FIG. 3 is a diagram illustrating a heating/battery temperature control mode by the controller of FIG. 2; FIG. 3 is a diagram for explaining a dehumidifying cooling/battery temperature control mode (cooling/battery temperature control mode) by the controller of FIG. 2; 3 is a diagram for explaining an internal cycle/battery temperature control mode by the controller of FIG. 2; FIG. FIG. 3 is a diagram for explaining a dehumidification/heating/battery temperature control mode by the controller in FIG. 2; FIG. 3 is a diagram for explaining a battery temperature control single mode by the controller of FIG. 2; FIG. 2 is a plan view of a branch member B2, an indoor expansion valve, and an auxiliary expansion valve shown in FIG. 1; FIG. 13 is a front view of a branch member B2, an indoor expansion valve and an auxiliary expansion valve shown in FIG. 12; It is a top view of branch member B1, an outdoor expansion valve, and an electromagnetic valve (dehumidification) part of FIG. FIG. 15 is a front view of a branch member B1, an outdoor expansion valve, and an electromagnetic valve (dehumidification) portion of FIG. 14; FIG. 2 is a diagram showing compatibility curves of oil with respect to pressure and temperature of refrigerant;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail based on the drawings. FIG. 1 shows a block diagram of a vehicle air conditioner 1 of one embodiment to which the present invention is applied. A vehicle of an embodiment to which the vehicle air conditioner 1 of the present invention is applied is an electric vehicle (EV) that is not equipped with an engine (internal combustion engine), and is equipped with a battery 55 (for example, a lithium battery). An electric motor (not shown) for driving is driven by supplying electric power charged in the battery 55 from an external power supply such as a quick charger or a domestic commercial power supply (normal charging) to an electric motor (not shown) for driving. Further, the vehicle air conditioner 1 of the present invention mounted on the vehicle is also powered by the battery 55 and driven.

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

The vehicle is not limited to an electric vehicle, but the present invention is also effective for a so-called hybrid vehicle that shares an engine and an electric motor for running, and can also be applied to a normal vehicle that runs on an engine. needless to say.

A vehicle air conditioner 1 of 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 a refrigerant, and air in the vehicle interior. is provided in the air flow passage 3 of the HVAC unit 10 through which ventilation is circulated. An outdoor expansion valve 6 consisting of an electric valve (electronic expansion valve) that decompresses and expands the refrigerant during heating, and a refrigerant that functions as a radiator that releases heat from the refrigerant during cooling and as an evaporator that absorbs heat from the refrigerant during heating. An outdoor heat exchanger 7 for exchanging heat with the outside air, an indoor expansion valve 8 consisting of an electric valve (electronic expansion valve) for decompressing and expanding the refrigerant, and an indoor expansion valve 8 provided in the air flow passage 3 for cooling and dehumidification. A refrigerant circuit R is configured by sequentially connecting a heat absorber 9 that causes the refrigerant to absorb heat from the outside and outside of the vehicle, an accumulator 12, and the like through a refrigerant pipe 13. FIG.

A predetermined amount of refrigerant (HFO-1234yf in the embodiment) and oil (lubricating oil) are sealed in the refrigerant circuit R. The outdoor expansion valve 6 and the indoor expansion valve 8 decompress and expand the refrigerant, 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 forcibly blows outside air through the outdoor heat exchanger 7 to exchange heat between the outside air and the refrigerant. The heat exchanger 7 is configured to be ventilated with outside air. Reference numeral 23 in the figure denotes a shutter called a grille shutter. When the shutter 23 is closed, the running wind is prevented from flowing into the outdoor heat exchanger 7 .

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

In addition, the refrigerant pipe 13A coming out of the outdoor heat exchanger 7 is branched, and the branched refrigerant pipe 13D is connected to the refrigerant pipe 13C located on the outlet side of the heat absorber 9 via the electromagnetic valve 21 that is opened during heating. is connected to the This refrigerant pipe 13</b>C is connected to the accumulator 12 , and the accumulator 12 is connected to the refrigerant suction side of the compressor 2 .

Further, a branch member B1 (another branch member in the present invention) constituting another branch portion in the present invention is provided in the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4, which is the high pressure side of the refrigerant circuit R. One end of a refrigerant pipe 13J that constitutes the outdoor heat exchanger inlet side circuit of the present invention is connected to the branch member B1. 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 is connected to the refrigerant pipe 13J.

Furthermore, one end of a refrigerant pipe 13F constituting a bypass circuit in the present invention is connected to the branch member B1. This refrigerant pipe 13F (bypass circuit) is located downstream of the check valve 18 and upstream of the indoor expansion valve 8 via the electromagnetic valve 22 as a dehumidifying valve of the present invention that is opened during dehumidification. It is communicatively connected to a connecting portion (branching member B2 described later) between the refrigerant pipe 13A and the refrigerant pipe 13B. That is, the other end of the refrigerant pipe 13F is connected to a branch member B2, which will be described later. As a result, 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 18 is bypassed.

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

In addition, in the air flow passage 3 on the air upstream side of the radiator 4, the air (inside air or outside air) in the air flow passage 3 after flowing into the air flow passage 3 and passing through the heat absorber 9 is radiated. An air mix damper 28 is provided for adjusting the ratio of ventilation to the vessel 4 . Further, in the air flow passage 3 on the air downstream side of the heat radiator 4, FOOT (foot), VENT (vent), and DEF (def) outlets (representatively indicated by the outlet 29 in FIG. 1) are formed. The air outlet 29 is provided with an air outlet switching damper 31 for switching and controlling air blowing from each of the air outlets.

Furthermore, the vehicle air conditioner 1 includes a battery temperature adjustment device 61 for circulating a heat medium in the battery 55 to adjust the temperature of 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 to the battery 55, a heat medium heater 66 as a heating device, and a refrigerant-heat medium heat exchanger 64. , and the battery 55 are annularly connected by a heat medium pipe 68 .

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

As the heat medium used in the battery temperature adjustment device 61, for example, water, refrigerant such as HFO-1234yf, liquid such as coolant, and gas such as air can be employed. In addition, water is used as a heat medium in the embodiment. The heat medium heater 66 is composed of an electric heater such as a PTC heater. Further, the battery 55 is surrounded by a jacket structure that allows a heat medium to flow in a heat exchange relationship with the battery 55 .

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 is generating heat, the heat medium is heated there, and then It flows into the heat medium flow path 64 A 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 . After the heat medium exchanges heat with the battery 55 there, it is sucked into the circulation pump 62 and circulated in the heat medium pipe 68 .

On the other hand, the refrigerant outlet of the refrigerant pipe 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 pipe 13A and the refrigerant pipe 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. FIG.

One end of a branch pipe 72 constituting a 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 later-described refrigerant passage 64B of the refrigerant-heat medium heat exchanger 64, and can also be fully closed.

The other end of the branch pipe 72 is connected to the refrigerant channel 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 channel 64B. The other end is connected to the refrigerant pipe 13C in front of the accumulator 12 (refrigerant upstream side). These auxiliary expansion valves 73 and the like also constitute a part of the refrigerant circuit R and at the same time constitute a part of the battery temperature adjustment device 61 .

When the auxiliary expansion valve 73 is open, the refrigerant (part or all of the refrigerant) discharged from the refrigerant pipe 13F or the outdoor heat exchanger 7 is decompressed by the auxiliary expansion valve 73, and then transferred to the refrigerant-heat medium heat exchanger. 64 into the coolant flow path 64B where it evaporates. After absorbing heat from the heat medium flowing through the heat medium flow path 64A in the course of flowing through the refrigerant flow path 64B, the refrigerant is sucked into the compressor 2 via the accumulator 12. FIG.

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

Next, in FIG. 2, reference numeral 32 denotes a controller as a control device for controlling the vehicle air conditioner 1, which is composed of a microcomputer as an example of a computer equipped with a processor. The inputs of this controller 32 are an outside air temperature sensor 33 that detects the outside air temperature (Tam) of the vehicle, an outside air humidity sensor 34 that detects the outside air humidity, and the temperature of the air sucked into the air flow passage 3 from the suction port 25. an HVAC intake temperature sensor 36, an inside air temperature sensor 37 that detects the temperature of the air (inside air) in the vehicle interior, an inside air humidity sensor 38 that detects the humidity of the air in the vehicle interior, and a carbon dioxide concentration in the vehicle interior. An indoor CO ₂ concentration sensor 39, an air outlet temperature sensor 41 that detects the temperature of the air that is blown out from the air outlet 29 into the passenger compartment, and a discharge pressure sensor 42 that detects the pressure of the refrigerant discharged from the compressor 2 (discharge pressure Pd). , a discharge temperature sensor 43 for detecting the temperature of the refrigerant discharged from the compressor 2, a suction temperature sensor 44 for detecting the temperature of the suction refrigerant of the compressor 2, and the temperature of the radiator 4 (the temperature of the air passing through the radiator 4, or A radiator temperature sensor 46 that detects the temperature of the radiator 4 itself: radiator temperature TCI), and the refrigerant pressure of the radiator 4 (the pressure of the refrigerant in the radiator 4 or immediately after leaving the radiator 4: the radiator A radiator pressure sensor 47 that detects the pressure PCI), and a heat absorber temperature sensor 48 that detects 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: heat absorber temperature Te). , a heat absorber pressure sensor 49 for detecting the pressure of the refrigerant in the heat absorber 9 (the pressure of the refrigerant in the heat absorber 9 or immediately after leaving the heat absorber 9), and for detecting the amount of solar radiation in the vehicle compartment, for example A photo sensor type solar radiation sensor 51, a vehicle speed sensor 52 for detecting the moving speed of the vehicle (vehicle speed), an air conditioning operation unit 53 for setting a set temperature and switching of air conditioning operation, and an outdoor heat exchanger 7 Temperature (the temperature of the refrigerant immediately after coming out of the outdoor heat exchanger 7, or the temperature of the outdoor heat exchanger 7 itself: outdoor heat exchanger temperature TXO. When the outdoor heat exchanger 7 functions as an evaporator, the outdoor heat exchange The outdoor heat exchanger temperature sensor 54 detects the refrigerant pressure in the outdoor heat exchanger 7, and the refrigerant pressure in the outdoor heat exchanger 7 (inside the outdoor heat exchanger 7 or in the outdoor heat exchange Each output of an outdoor heat exchanger pressure sensor 56 for detecting the pressure of the refrigerant immediately after coming out of the unit 7 is connected.

Further, the temperature of the battery 55 (the temperature of the battery 55 itself, the temperature of the heat medium leaving the battery 55, or the temperature of the heat medium entering the battery 55: battery temperature Tb) is also detected as an input to the controller 32. a battery temperature sensor 76 for detecting the temperature of the heat medium heater 66 (the temperature of the heat medium heater 66 itself, the temperature of the heat medium exiting the heat medium heater 66); 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; 79 are also connected.

On the other hand, the outputs of the controller 32 include the compressor 2, the outdoor fan 15, the indoor fan (blower fan) 27, the suction switching damper 26, the air mix damper 28, the outlet switching damper 31, and the outdoor expansion The valve 6, the indoor expansion valve 8, the solenoid valve 22 (dehumidification), the solenoid valve 21 (heating), the shutter 23, the circulation pump 62, the heat medium heater 66, and the auxiliary expansion valve 73 are connected. . The controller 32 controls these based on the output of each sensor and the setting input by the air conditioning operation section 53 .

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 air conditioning operations such as heating operation, dehumidifying heating operation, internal cycle operation (dehumidifying operation), dehumidifying cooling operation, and cooling operation, and controls 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 the refrigerant flow (solid arrow) in the refrigerant circuit R during heating operation. When heating operation is selected by the controller 32 (auto mode) or by manual operation (manual mode) of the air conditioning operation unit 53, the controller 32 opens the solenoid valve 21 (for heating) and closes the indoor expansion valve 8. Fully closed. Also, 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 fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 . As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air circulation passage 3 is passed through the radiator 4, the air in the air circulation passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 transfers heat to the air. It is robbed, cooled, condensed and liquefied.

After leaving the radiator 4, the refrigerant liquefied in the radiator 4 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 that has flowed into the outdoor expansion valve 6 is decompressed there and then flows into the outdoor heat exchanger 7 . The refrigerant that has flowed into the outdoor heat exchanger 7 evaporates, and draws up heat from the outside air blown by the outdoor blower 15 while the vehicle is running (heat absorption). That is, the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipes 13A and 13D, the electromagnetic valve 21, and enters the accumulator 12 from the refrigerant pipe 13C. Repeat the circulation sucked into. Since the air heated by the radiator 4 is blown out from the outlet 29, the vehicle interior is heated.

The controller 32 calculates a target radiator pressure PCO (a target value of the pressure PCI of the radiator 4) from a target heater temperature TCO (a target value of the air temperature on the leeward side of the radiator 4) calculated from a target outlet temperature TAO, which will be described later. Based on this target radiator pressure PCO and the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47 (radiator pressure PCI, high pressure of the refrigerant circuit R), the rotation speed of the compressor 2 is controlled. At the same time, the valve opening degree of the outdoor expansion valve 6 is controlled based on the temperature of the radiator 4 (radiator temperature TCI) detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47, and heat is released. Controls the degree of subcooling of the refrigerant at the outlet of vessel 4. The target heater temperature TCO is basically set to TCO=TAO, but a predetermined control limit is provided.

(2) Dehumidifying and Heating Operation Next, the dehumidifying and heating operation will be described with reference to FIG. FIG. 4 shows the flow of refrigerant (solid line arrows) in the refrigerant circuit R in the dehumidifying and 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 to decompress and expand the refrigerant. Also, the shutter 23 is opened and the auxiliary expansion valve 73 is fully closed. As a result, part of the condensed refrigerant that exits the radiator 4 and flows through the refrigerant pipe 13E is branched to the refrigerant pipe 13F by the branch member B1. The refrigerant flows into the pipe 13B (heat absorber inlet side circuit) and flows into the indoor expansion valve 8, and the rest of the refrigerant flows into the refrigerant pipe 13J and flows into the outdoor expansion valve 6. That is, a portion of the branched 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 to the high pressure side of the refrigerant circuit R.

The controller 32 controls the valve opening degree of the indoor expansion valve 8 so as to maintain the degree of superheat (SH) of the refrigerant at the outlet of the heat absorber 9 at a predetermined value. Moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9, so that the air is cooled and dehumidified. The remaining refrigerant that has flowed into the refrigerant pipe 13</b>J after being split is decompressed by the outdoor expansion valve 6 and then evaporated in the outdoor heat exchanger 7 .

The refrigerant evaporated in the heat absorber 9 exits the refrigerant pipe 13C, joins the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), passes through the accumulator 12, and is sucked into the compressor 2, repeating circulation. Since the air dehumidified by the heat absorber 9 is reheated in the course of passing through the radiator 4, dehumidification heating is performed in the passenger compartment.

The controller 32 controls the rotation speed of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. , 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 dehumidification operation in the present invention will be described with reference to FIG. FIG. 5 shows the refrigerant flow (solid line 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 (fully closed position) in the state of the dehumidifying and heating operation. However, the electromagnetic 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, this internal cycle operation is a state in which the outdoor expansion valve 6 is fully closed by controlling the outdoor expansion valve 6 in the dehumidifying and heating operation, so this internal cycle operation can also be regarded as part of the dehumidifying and heating operation ( The shutter 23 is open and the auxiliary expansion valve 73 is fully closed).

However, by closing the outdoor expansion valve 6, the inflow of the refrigerant into the outdoor heat exchanger 7 is blocked. It flows into the pipe 13F, passes through the electromagnetic valve 22, and reaches the branch member B2. Therefore, in this case as well, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R. Then, 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 decompressed by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9 due to the heat absorbing action at this time, so that the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C, passes through the accumulator 12, and is sucked into the compressor 2, thereby repeating circulation. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying and heating the vehicle interior is performed. Since the refrigerant is circulated between the radiator 4 (heat dissipation) and the heat absorber 9 (heat absorption) in the path 3, heat is not drawn from the outside air, and the power consumed by the compressor 2 is used for heating. Ability is demonstrated. Since the entire amount of refrigerant flows through the heat absorber 9 that exhibits the dehumidifying action, the dehumidifying capacity is high compared to the dehumidifying and heating operation, but the heating capacity is low.

Although the outdoor expansion valve 6 is closed, the solenoid valve 21 is open, and the refrigerant outlet of the outdoor heat exchanger 7 communicates with the refrigerant suction side of the compressor 2. The refrigerant flows through the refrigerant pipe 13D and the electromagnetic valve 21 into the refrigerant pipe 13C, is recovered by the accumulator 12, and the inside of the outdoor heat exchanger 7 becomes gas refrigerant. As a result, the amount of refrigerant circulating in the refrigerant circuit R increases compared to when the solenoid valve 21 is closed, and the heating capacity of the radiator 4 and the dehumidification capacity of the heat absorber 9 can be improved.

The controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 or the aforementioned radiator pressure PCI (high pressure of the refrigerant circuit R). At this time, the controller 32 controls the compressor 2 by selecting either the temperature of the heat absorber 9 or the radiator pressure PCI, whichever is the lower compressor target rotation speed obtained from the calculation.

(4) Dehumidifying Cooling Operation Next, the dehumidifying cooling operation will be described with reference to FIG. FIG. 6 shows the flow of refrigerant (solid line arrows) in the refrigerant circuit R in the dehumidifying and cooling operation. In the dehumidifying cooling operation, the controller 32 opens the indoor expansion valve 8 to decompress and expand the refrigerant, and closes the solenoid valves 21 and 22 . Then, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 . Also, the shutter 23 is opened and the auxiliary expansion valve 73 is fully closed. As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air circulation passage 3 is passed through the radiator 4, the air in the air circulation passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 transfers heat to the air. It is stolen, cooled, and condensed.

The refrigerant that has exited the radiator 4 flows through the refrigerant pipe 13</b>E from the branch member B<b>1 to the refrigerant pipe 13</b>J (outdoor heat exchanger inlet side circuit), and reaches the outdoor expansion valve 6 . Then, it flows into the outdoor heat exchanger 7 via the outdoor expansion valve 6 which is controlled to be slightly open. The refrigerant that has flowed into the outdoor heat exchanger 7 is air-cooled there by traveling or by outside air blown by the outdoor blower 15 and condensed. The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13 A and the check valve 18 , enters the refrigerant pipe 13 B (heat absorber inlet side circuit) through the branch member B 2 , and reaches the indoor expansion valve 8 . After the refrigerant is decompressed by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9 due to the heat absorbing action at this time, so that the air is cooled and dehumidified.

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

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, the controller 32 adjusts the heat absorber temperature Te to the target heat absorber temperature TEO. In addition to controlling the rotation speed of the compressor 2, a target radiator pressure PCO (radiator pressure PCI (target value of )), the necessary 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 in the refrigerant circuit R is the same as in the dehumidifying cooling operation of FIG. In the cooling operation, the controller 32 fully opens the outdoor expansion valve 6 in the dehumidifying cooling operation. Incidentally, the air mix damper 28 is set in a state of adjusting the ratio of the air to the radiator 4 . Also, the shutter 23 is opened and the auxiliary expansion valve 73 is fully closed.

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Although the air in the air circulation passage 3 is ventilated to the radiator 4, the ratio is small (because it is only reheated during cooling), so most of it only passes through here, and the refrigerant leaving the radiator 4 is It enters the refrigerant pipe 13J 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 open, the refrigerant passes through the outdoor expansion valve 6 and the refrigerant pipe 13J as it is, 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 condensed and liquefied.

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

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and is sucked into the compressor 2 via the refrigerant pipe 13C, repeating circulation. The air cooled and dehumidified by the heat absorber 9 is blown into the passenger compartment through the outlet 29, thereby cooling the passenger compartment. In this cooling operation, the controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 .

(6) Switching of air-conditioning operation The controller 32 calculates the above-described target air temperature TAO from the following equation (I). This target blowout temperature TAO is a target value for 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 vehicle interior set by the air conditioning operation unit 53, Tin is the temperature of the interior air detected by the inside air temperature sensor 37, K is a coefficient, and Tbal is the set temperature Tset and the solar radiation sensor 51 detects. SUN and the outside air temperature Tam detected by the outside air temperature sensor 33 . In general, the lower the outside air temperature Tam is, the higher the target blowing temperature TAO is, and the higher the outside air temperature Tam is, the lower the target blowing temperature TAO is.

At startup, the controller 32 selects one of the air conditioning operations based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target air temperature TAO. Further, after startup, each air conditioning operation is selected and switched according to changes in the environment and setting conditions such as the outside air temperature Tam and the target blowout temperature TAO.

(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. 7 to 12. FIG. 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 ambient temperature is in a high temperature environment or in an extremely low temperature environment, the temperature of the battery 55 becomes extremely high or extremely low, making charging and discharging difficult. For example, when the temperature of the battery 55 is +45° C. or higher, charging becomes difficult, and when the temperature is 60° C. or higher, discharging becomes difficult. In addition, discharging becomes difficult even below -20°C, and charging becomes almost impossible.

Therefore, the controller 32 of the vehicle air conditioner 1 according to the embodiment adjusts the temperature of the battery 55 by the battery temperature adjustment device 61 while performing the air conditioning operation as described above or in a state where the air conditioning operation is stopped. Adjust the temperature within the specified specified temperature range (within the operating temperature range). Since the specified temperature range of the battery 55 is generally +20° C. or more and +40° C. or less, in the embodiment, the temperature of the battery 55 (battery temperature Tb) detected by the battery temperature sensor 76 falls within this specified temperature range. Assume that a target battery temperature TBO (for example, +20° C.), which is a target value, is set.

(7-1) Heating/Battery Temperature Control Mode When the temperature of the battery 55 needs to be adjusted in the heating operation described above, the controller 32 executes the heating/battery temperature control mode. FIG. 7 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrows) and the flow of the heat medium in the battery temperature control device 61 (broken line arrows) in this heating/battery temperature control mode.

In this heating/battery temperature control mode, the controller 32 further opens the solenoid valve 22 (dehumidification valve) and also opens the auxiliary expansion valve 73 in the heating operation state of the refrigerant circuit R shown in FIG. to be in a controlled state. Then, the circulation pump 62 of the battery temperature adjustment device 61 is operated. As a result, part of the refrigerant coming out of the radiator 4 is branched by the branch member B1 and reaches the branch member B2 on the refrigerant upstream side of the indoor expansion valve 8 via the refrigerant pipe 13F. That is, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R also in this case. The refrigerant enters the branch pipe 72 from the branch member B2, is decompressed by the auxiliary expansion valve 73, flows through the branch pipe 72 into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and evaporates. At this time, it exerts an endothermic action. The refrigerant evaporated in the refrigerant flow path 64B repeats the circulation of being sucked into the compressor 2 through the refrigerant pipe 74, the refrigerant pipe 13C and the accumulator 12 in sequence (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 and is heated there (when the heat medium heater 66 is generating heat). It reaches the heat medium flow path 64A of the exchanger 64, where heat is absorbed by the refrigerant that evaporates 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 heat absorption action of the refrigerant exits the refrigerant-heat medium heat exchanger 64, reaches the battery 55, and after heat exchange with the battery 55, The circulation sucked by the circulation pump 62 is repeated (indicated by the dashed arrow 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 to constantly cool the heat medium, based on the battery temperature Tb detected by the battery temperature sensor 76 and the target battery temperature TBO. By controlling the heat generation of the heat medium heater 66, the battery temperature Tb is brought to the target battery temperature TBO (in that case, in practice, the heating/battery temperature control mode is always executed instead of the heating operation). , or the heating operation and the heating/battery temperature control mode are switched for execution). Alternatively, when the battery temperature Tb>target battery temperature TBO+α 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 reaches TBO-α, 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, so that the battery temperature Tb reaches the target battery temperature TBO. so that As described above, the controller 32 adjusts the temperature Tb of the battery 55 to the target battery temperature TBO within the specified temperature range.

(7-2) Cooling/Battery Temperature Control Mode Next, when the temperature of the battery 55 needs to be adjusted during the cooling operation described above, the controller 32 executes the cooling/battery temperature control mode. FIG. 8 shows the flow of refrigerant in the refrigerant circuit R (solid line arrows) and the flow of the heat medium in the battery temperature control device 61 (broken line arrows) in this cooling/battery temperature control mode.

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

As a result, the high-temperature refrigerant discharged from the compressor 2 passes through the radiator 4 and flows into the outdoor heat exchanger 7 from the branch member B1, where it exchanges heat with outside air blown by the outdoor blower 15 and running wind. It dissipates heat and condenses. Part of the refrigerant condensed in the outdoor heat exchanger 7 reaches the branch member B2. That is, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R also in this case. The refrigerant passes through the branch member B2 and reaches the indoor expansion valve 8, where it is decompressed and then flows into the heat absorber 9 where it evaporates. Since the air in the air flow passage 3 is cooled by the heat absorbing action at this time, the vehicle interior is cooled.

The remainder of the refrigerant condensed in the outdoor heat exchanger 7 is branched to the branch pipe 72 by the branch member B2, depressurized by the auxiliary expansion valve 73, and evaporated in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. . Since the coolant 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 coming out of the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and the refrigerant coming out of the refrigerant-heat medium heat exchanger 64 also flows through the refrigerant pipe 74 into the compressor 2 through the accumulator 12. will be sucked.

In this cooling/battery temperature control mode, as in the heating/battery temperature control mode described above, the controller 32 can replace the cooling operation, switch between the refrigerant operation and the cooling/battery temperature control mode, or switch from the cooling operation. 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) Dehumidification cooling/battery temperature control mode Next, when it becomes necessary to adjust the temperature of the battery 55 during the above-described dehumidification cooling operation, the controller 32 executes the dehumidification cooling/battery temperature control mode. . In this dehumidifying cooling/battery temperature control mode, the refrigerant flow (solid line arrow) in the refrigerant circuit R and the heat medium flow (broken line arrow) in the battery temperature control device 61 are the same as in FIG. is controlled to open rather than fully open. As in the cooling/battery temperature control mode, the controller 32 controls the auxiliary expansion valve 73 and the heat medium heater 66 to bring the temperature Tb of the battery 55 to the target battery temperature TBO within the specified temperature range. adjust.

(7-4) Internal Cycle/Battery Temperature Control Mode Next, when the temperature of the battery 55 needs to be adjusted during the internal cycle operation described above, the controller 32 executes the internal cycle/battery temperature control mode. In this internal cycle/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 internal cycle operation shown in FIG. The circulation pump 62 is also operated to bring about a state in which heat is exchanged between the refrigerant and the heat medium in the refrigerant-heat medium heat exchanger 64 . FIG. 9 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrow) and the flow of the heat medium in the battery temperature control device 61 (broken line arrow) in this internal cycle/battery temperature control mode.

As a result, the high-temperature refrigerant discharged from the compressor 2 radiates heat in the radiator 4, and then all flows from the branch member B1 through the solenoid valve 22 to the refrigerant pipe 13F. Then, the refrigerant exiting the refrigerant pipe 13F reaches the branch member B2. That is, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R also in this case. A portion of the refrigerant flows from the branch member B2 through the refrigerant pipe 13B to the indoor expansion valve 8, where it is decompressed and then flows into the heat absorber 9 to evaporate. Moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9 due to the heat absorbing action at this time, so that the air is cooled and dehumidified.

The rest of the refrigerant exiting the refrigerant pipe 13F is branched to the branch pipe 72 by the branch member B2, decompressed by the auxiliary expansion valve 73, and evaporated in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. Since the coolant 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 coming out of the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and the refrigerant coming out of the refrigerant-heat medium heat exchanger 64 also flows through the refrigerant pipe 74 into the compressor 2 through the accumulator 12. will be sucked.

Even in this internal cycle/battery temperature control mode, the controller 32 can replace the internal cycle operation, switch between the internal cycle operation and the internal cycle/battery temperature control mode, or By shifting from the internal cycle operation to the internal cycle/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. do.

(7-5) Dehumidification Heating/Battery Temperature Control Mode Next, when the temperature of the battery 55 needs to be adjusted in the above-described dehumidification heating operation, the controller 32 executes the dehumidification heating/battery temperature control mode. In this dehumidification/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 dehumidification/heating operation of FIG. The circulation pump 62 is also operated to bring about a state in which heat is exchanged between the refrigerant and the heat medium in the refrigerant-heat medium heat exchanger 64 . FIG. 10 shows the flow of refrigerant in the refrigerant circuit R (solid line arrows) and the flow of the heat medium in the battery temperature adjustment device 61 (broken line arrows) in this dehumidifying heating/battery temperature control mode.

As a result, part of the condensed refrigerant that has exited the radiator 4 is branched by the branch member B1, and the branched refrigerant flows through the solenoid valve 22 into the refrigerant pipe 13F, and exits from the refrigerant pipe 13F. part flows from the branch member B2 through the refrigerant pipe 13B to the indoor expansion valve 8, and the rest of the refrigerant flows to the outdoor expansion valve 6. That is, a part of the branched refrigerant is decompressed by the indoor expansion valve 8 and then flows into the heat absorber 9 to evaporate. At this time, moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9 due to the heat absorbing 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 course of passing through the radiator 4, dehumidification heating is performed in the passenger compartment. The remainder of the condensed refrigerant discharged from the radiator 4 flows from the branch member B1 into the refrigerant pipe 13J, is decompressed by the outdoor expansion valve 6, and then evaporates in the outdoor heat exchanger 7 to absorb heat from the outside air.

On the other hand, the rest 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 then evaporates in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64. . Since the coolant 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. Refrigerant coming out of the heat absorber 9 is sucked into the compressor 2 through the refrigerant pipe 13C and the accumulator 12, and refrigerant coming out of the outdoor heat exchanger 7 flows through the refrigerant pipe 13D, the solenoid valve 21, the refrigerant pipe 13C and the accumulator 12. Refrigerant exiting the refrigerant-heat medium heat exchanger 64 is also sucked into the compressor 2 through the refrigerant pipe 74 through the accumulator 12 .

Even in this dehumidification heating/battery temperature control mode, the controller 32 switches between the dehumidification heating operation and the dehumidification heating/battery temperature control mode in the same way as in the heating/battery temperature control mode described above, or switches between the dehumidification heating operation and the dehumidification heating/battery temperature control mode. , the temperature Tb of the battery 55 is adjusted to the target battery temperature TBO within the specified temperature range by shifting from the dehumidification heating operation to the dehumidification heating/battery temperature control mode and controlling the auxiliary expansion valve 73 and the heat medium heater 66. do.

(7-6) Battery Temperature Control Single Mode Next, the battery temperature control single mode for controlling the temperature of the battery 55 without air-conditioning the vehicle interior will be described. FIG. 11 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrow) and the flow of the heat medium in the battery temperature control device 61 (broken line arrow) in the independent battery temperature control mode. The controller 32 operates the compressor 2 and also operates the outdoor fan 15 . Also, the indoor expansion valve 8 is fully closed, and the auxiliary expansion valve 37 is opened to decompress the refrigerant. The outdoor expansion valve 6 is fully opened. Further, the controller 32 closes the solenoid valves 17 and 21 and stops the indoor blower 27 . Then, the circulation pump 62 is operated to bring about a state in which heat is exchanged between the refrigerant and the heat medium in the refrigerant-heat medium heat exchanger 64 .

As a result, the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 passes through the radiator 4 , enters the refrigerant pipe 13</b>J through the branch member B<b>1 , 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 air-cooled by the outdoor air blown by the outdoor fan 15, and is condensed and liquefied. If frost builds up on the outdoor heat exchanger 7, the outdoor heat exchanger 7 is defrosted by the heat radiation 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, the position of the branch member B2 is set on the high pressure side of the refrigerant circuit R also in this case. Since the indoor expansion valve 8 is fully closed at this time, all the refrigerant that has left the outdoor heat exchanger 7 reaches the auxiliary expansion valve 73 via the branch pipe 72 from the branch member B2. After being decompressed by the auxiliary expansion valve 73, the refrigerant flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 and evaporates. At this time, it exerts an endothermic action. The refrigerant evaporated in this refrigerant flow path 64B passes through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 in sequence and is sucked into the compressor 2, repeating circulation.

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 is generating heat), and passes through the heat medium pipe 68 to the refrigerant-heat medium heat exchanger 64. It reaches the heat medium flow path 64A, where heat is absorbed by the refrigerant that evaporates 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 heat absorption action of the refrigerant exits the refrigerant-heat medium heat exchanger 64, reaches the battery 55, and after heat exchange with the battery 55, The circulation sucked by the circulation pump 62 is repeated (indicated by the dashed arrow in FIG. 11).

The controller 32 controls the auxiliary expansion valve 73 and the heat medium heater 66 in this battery temperature control independent mode as well as in the heating/battery temperature control mode described above to keep the temperature Tb of the battery 55 within the specified temperature range. is adjusted to the target battery temperature TBO within.

(8) Specific structure of the branching member B2, layout and connection structure of the indoor expansion valve 8, the auxiliary expansion valve 73, etc. Next, with reference to FIGS. , and the arrangement and 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 branch member B2, the indoor expansion valve 8, and the auxiliary expansion valve 73, and FIG. 13 is a front view. The branch member B2 is composed of a metal block, and the branch member B2 has a first refrigerant inlet IN1 and a second refrigerant inlet IN2, and a first refrigerant outlet OUT1 and a second refrigerant outlet OUT1 communicating with them inside. of the refrigerant outlet OUT2. A refrigerant pipe 13F is connected to the first refrigerant inlet IN1, and a refrigerant pipe 13A is connected to the second refrigerant inlet IN2.

A refrigerant pipe 13B is connected to the first refrigerant outlet OUT1, and a branch pipe 72 is connected to the second refrigerant outlet OUT2. is rising from the refrigerant outlet OUT1. The indoor expansion valve 8 is connected to a side of the refrigerant pipe 13B closer to the branch member B2 than the heat absorber 9, so that the indoor expansion valve 8 is arranged at a position higher than the branch member B2.

Further, as shown in FIG. 13, the branch pipe 72 also rises from the second refrigerant outlet OUT2 of the branch member B2, and the auxiliary expansion valve 73 is also a branch member of the branch pipe 72 rather than the refrigerant-heat medium heat exchanger 64. It is connected to the side closer to B2. As a result, 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 dehumidifying heating operation, the internal cycle operation, the dehumidifying cooling operation, and the cooling operation described above, and the refrigerant from the refrigerant pipe 13F or the refrigerant pipe 13B is supplied to the indoor expansion valve 8. , the volume in the branch pipe 72 between the branch member B2 and the auxiliary expansion valve 73 becomes smaller, the amount of the refrigerant and the oil remaining therein becomes smaller, and the branch member B2 and the auxiliary expansion valve 73 become Refrigerant and oil are less likely to accumulate in the branch pipe 72 between .

In addition, when the indoor expansion valve 8 is fully closed in the heating/battery temperature control mode and the battery temperature control single mode described above and the refrigerant from the refrigerant pipe 13F or the refrigerant pipe 13B flows to the auxiliary expansion valve 73, the branch member B2 and The volume in the refrigerant pipe 13B between the indoor expansion valve 8 becomes smaller, the amount of the refrigerant and oil remaining there decreases, and the refrigerant in the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8 increases. It becomes difficult for oil to accumulate.

In this way, 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 branch pipe 72 more than the refrigerant-heat medium heat exchanger 64. If it is arranged on the side 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 can be reduced. will be able to

As a result, when the auxiliary expansion valve 73 is fully closed, the amount of the refrigerant remaining in the branch pipe 72 between the branch member B2 and the auxiliary expansion valve 73 and the oil dissolved therein is remarkably reduced. It is possible to prevent a decrease in the oil circulation rate, improve the reliability of the compressor 2, and prevent an increase in the amount of refrigerant required and the amount of oil required.

Furthermore, even when the indoor expansion valve 8 is fully closed, the amount of the refrigerant remaining in the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8 and the oil dissolved therein is remarkably reduced. Similarly, it is possible to prevent a decrease in the oil circulation rate, improve the reliability of the compressor 2, and prevent an increase in the required refrigerant amount and the required oil amount.

In particular, as in the embodiment, a branching member B2 having a refrigerant inlet IN1 and first and second refrigerant outlets OUT1 and OUT2 constitutes a branching portion, and the refrigerant pipe 13B is connected to the first refrigerant outlet OUT1 of the branching member B2. 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. By arranging the auxiliary expansion valve 73 at a position higher than the branch member B2, the refrigerant pipe 13B between the branch member B2 and the indoor expansion valve 8, and the branch member B2 and the auxiliary expansion valve Refrigerant and oil are less likely to accumulate in the branch pipe 72 between the valve 73, and the decrease 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, Electromagnetic Valve 22, etc. Next, with reference to FIGS. another branch), the refrigerant pipe 13E, the refrigerant pipe 13J (outdoor heat exchanger inlet side circuit), the refrigerant pipe 13F (bypass circuit), the outdoor expansion valve 6 and the electromagnetic valve 22 (dehumidification valve) will be described.

14 is a plan view of the branch 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 made of a metal block, and has a refrigerant inlet IN and a first refrigerant outlet OUT1 and a second refrigerant outlet OUT2 internally communicating with the refrigerant inlet IN. A refrigerant pipe 13E is connected to the refrigerant inlet IN.

A refrigerant pipe 13J is connected to the first refrigerant outlet OUT1 of the branch member B1, and a refrigerant pipe 13F is connected to the second refrigerant outlet OUT2. It rises from the first refrigerant outlet OUT1 of B1. The outdoor expansion valve 6 is connected to a side of the refrigerant pipe 13J closer to the branch member B1 than the outdoor heat exchanger 7, so that the outdoor expansion valve 6 is arranged at a position higher than the branch member B1. there is

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 solenoid valve 22 is also connected to the branch member B1 rather than the branch member B2 and the indoor expansion valve 8 in the refrigerant pipe 13F. connected to the side closest to the As a result, the electromagnetic valve 22 is also arranged at a position higher than the branch member B1.

With such a configuration, when the solenoid 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 solenoid valve 22 The internal volume becomes smaller, the amount of refrigerant and oil staying 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 solenoid valve 22.

Further, 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 becomes smaller and , it becomes difficult for refrigerant and oil to accumulate there.

Thus, the outdoor expansion valve 6 is arranged closer to the branch member B1 than the outdoor heat exchanger 7 in the refrigerant pipe 13J, and the solenoid valve 22 is arranged closer to the branch member B2 and the indoor expansion valve 8 in the refrigerant pipe 13F. If it is arranged on the side 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 solenoid valve 22 can be reduced. will be able to

As a result, when the solenoid valve 22 is closed, the amount of the refrigerant remaining in the refrigerant pipe 13F between the branch member B1 and the solenoid valve 22 and the oil dissolved therein is remarkably reduced, thereby increasing the oil circulation rate. It is possible to prevent a decrease, improve the reliability of the compressor 2, and 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 the refrigerant remaining in the refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 and the oil dissolved therein is remarkably reduced. Similarly, it is possible to prevent a decrease in the oil circulation rate, improve the reliability of the compressor 2, and prevent an increase in the required refrigerant amount and the required oil amount.

In particular, as in the embodiment, the branch member B1 having the refrigerant inlet IN and the first and second refrigerant outlets OUT1 and OUT2 constitutes another branch, and the refrigerant pipe 13J is connected to the first refrigerant outlet of the branch member B1. 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 so as to rise from the branch member B1. By standing up from the branch member B1 and arranging the electromagnetic valve 22 at a position higher than the branch member B1, the refrigerant pipe 13J between the branch member B1 and the outdoor expansion valve 6 and the branch member B1 and Refrigerant and oil are less likely to accumulate in the refrigerant pipe 13F between the solenoid valve 22, and the decrease in the oil circulation rate can be more effectively eliminated.

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

B1 branching member (another branching member, another branching part)
B2 branching member (branching part)
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 pipe (heat absorber inlet side circuit)
13F refrigerant pipe (bypass circuit)
13J refrigerant pipe (outdoor heat exchanger inlet side circuit)
22 solenoid valve (dehumidification valve)
32 controller 55 battery 61 battery temperature regulator 62 circulation pump 64 refrigerant-heat medium heat exchanger 66 heat medium heater (heating device)
72 branch piping (branch circuit)
73 auxiliary expansion valve

Claims (8)

A compressor that compresses a refrigerant, an outdoor heat exchanger provided outside the vehicle, a heat absorber that absorbs heat from the refrigerant and cools the air that is supplied to the vehicle, and the refrigerant that flows into the heat absorber. a refrigerant circuit configured to have an indoor expansion valve for reducing the pressure and containing a predetermined amount of the refrigerant and oil;
In a vehicle air conditioner that includes a control device and air-conditions the interior of the vehicle,
a branching portion set on the high-pressure side of the refrigerant circuit;
a heat absorber inlet side circuit extending from the branch to the heat absorber and provided with the indoor expansion valve;
a refrigerant pipe extending from the refrigerant outlet side of the outdoor heat exchanger to the branch portion;
a check valve provided in the refrigerant pipe and having a forward direction toward the heat absorber inlet circuit side;
another branch set on the refrigerant inlet side of the outdoor heat exchanger;
a bypass circuit that communicates with the other branch portion and the branch portion to bypass the outdoor heat exchanger and the check valve;
Equipped with a battery temperature adjustment device for circulating a heat medium to adjust the temperature of the battery mounted on the vehicle,
The battery temperature regulator comprises:
a refrigerant-heat medium heat exchanger for exchanging heat between the refrigerant and the heat medium;
a branch circuit from the branch portion to the refrigerant-heat medium heat exchanger;
an auxiliary expansion valve provided in the branch circuit for decompressing the refrigerant flowing into the refrigerant-heat medium heat exchanger;
The control device is capable of executing operation with the indoor expansion valve or the auxiliary expansion valve fully closed,
The indoor expansion valve is arranged closer to the branch portion than the heat absorber in the heat absorber inlet circuit, and the auxiliary expansion valve is arranged in the branch circuit closer to the refrigerant-heat medium heat exchanger. While being arranged on the side close to the branching part,
another branching member having a refrigerant inlet and first and second refrigerant outlets and constituting the another branching part;
A dehumidification valve provided in the bypass circuit,
The bypass circuit is connected to a second refrigerant outlet of the another branch member and rises from the another branch member, and the dehumidification valve is arranged at a position higher than the another branch member. and a vehicle air conditioner. The control device fully closes the auxiliary expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, and transfers the radiated refrigerant from the branch to the heat absorber inlet side circuit. 2. The vehicle air conditioning apparatus according to claim 1, wherein after the air is flowed and decompressed by the indoor expansion valve, a cooling operation is performed in which heat is absorbed by the heat absorber. The control device fully closes the indoor expansion valve, causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, flows the radiated refrigerant from the branch portion to the branch circuit, and 3. The vehicle air conditioner according to claim 1, wherein a battery temperature control independent mode is executed in which heat is absorbed by the refrigerant-heat medium heat exchanger after the pressure is reduced by the auxiliary expansion valve. a branching member having a refrigerant inlet and first and second refrigerant outlets to form the branching part;
The heat absorber inlet side circuit is connected to a first refrigerant outlet of the branch member and rises from the branch member, and the indoor expansion valve is arranged 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 arranged at a position higher than the branch member. 4. The vehicle air conditioner according to any one of 3. The refrigerant circuit includes a radiator for radiating heat from the refrigerant to heat the air supplied to the vehicle interior, and an outdoor heat exchanger inlet for flowing the refrigerant discharged from the radiator to the outdoor heat exchanger. a side circuit, and an outdoor expansion valve provided in the outdoor heat exchanger inlet side circuit for decompressing the refrigerant flowing into the outdoor heat exchanger ,
The bypass circuit is branched from the another branch portion set upstream of the refrigerant of the outdoor expansion valve, and flows the refrigerant discharged from the radiator to the indoor expansion valve,
The control device is capable of executing operation with the flow path closed by the outdoor expansion valve or the dehumidification valve,
The outdoor expansion valve is arranged closer to the other branch than the outdoor heat exchanger in the outdoor heat exchanger inlet pipe, and the dehumidification valve is the indoor expansion valve in the bypass circuit. 5. The vehicle air conditioner according to any one of claims 1 to 4, wherein the vehicle air conditioner is arranged on a side closer to the another branch than the second branch. The control device closes the dehumidification valve, causes the refrigerant discharged from the compressor to radiate heat in the radiator, flows the radiated refrigerant from the another branch portion to the outdoor expansion valve, and 6. The vehicle air conditioner according to claim 5, wherein after the pressure is reduced by the expansion valve, a heating operation is performed in which heat is absorbed by the outdoor heat exchanger. The control device fully closes the outdoor expansion valve, opens the dehumidification valve, causes the refrigerant discharged from the compressor to radiate heat in the radiator, and transfers the heat-dissipated refrigerant to the other branch portion. 7. The vehicle air conditioner according to claim 5 or 6, wherein a dehumidifying operation is performed in which the dehumidifying operation is performed in which the air is flowed from the outlet to the bypass circuit, decompressed by the indoor expansion valve, and then the heat is absorbed by the heat absorber. The outdoor heat exchanger inlet side circuit is connected to the first refrigerant outlet of the another branch member and rises from the another branch member, and the outdoor expansion valve is positioned higher than the another branch member. 8. The vehicle air conditioner according to any one of claims 5 to 7, wherein the vehicle air conditioner is arranged.

Images