JP7153170B2 - COMPOSITE VALVE AND VEHICLE AIR CONDITIONER USING THE SAME - Google Patents

Description

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

An air conditioner that can be applied to vehicles such as hybrid vehicles and electric vehicles includes a refrigerant circuit in which a compressor, a radiator, a heat absorber, and an outdoor heat exchanger are connected. A heating mode heats the vehicle interior by allowing the refrigerant to radiate heat in a radiator, decompressing the refrigerant that has radiated heat in this radiator with an outdoor expansion valve, and then absorbing heat in an outdoor heat exchanger to heat the vehicle interior. A vehicle air conditioner has been developed that switches between cooling modes for cooling the passenger compartment by releasing heat in an outdoor heat exchanger, reducing the pressure in an indoor expansion valve, and then absorbing heat in a heat absorber. In addition, such operation modes in the passenger compartment have been realized by switching using a large number of electromagnetic valves and expansion valves (see, for example, Patent Document 1).

JP 2011-237052 A JP 2015-45453 A

In this way, the operation mode of conventional vehicle air conditioners is switched by using a large number of solenoid valves and expansion valves. In the case of , there is no engine, but there is an inconvenience that it occupies a space outside the vehicle where devices related to running and air conditioning are installed.

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

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 a composite valve that can reduce the cost, and a vehicle air conditioner using the same.

A composite valve of the present invention is applied to a refrigerant circuit, and includes a housing having a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, a second refrigerant outlet, and a third refrigerant outlet; a first refrigerant passage formed in the housing and extending between the first refrigerant inlet and the first refrigerant outlet; a second refrigerant passage formed in the housing and extending between the second refrigerant inlet and the second refrigerant outlet; a first on-off valve portion provided in the refrigerant passage for opening and closing the first refrigerant passage; a second on-off valve portion provided in the second refrigerant passage for opening and closing the second refrigerant passage; A third refrigerant passage extending from the second refrigerant passage on the second refrigerant inlet side of the second on-off valve portion to the third refrigerant outlet, and an expansion valve provided in the third refrigerant passage for adjusting the degree of opening of the third refrigerant passage. a driving device for driving the expansion valve portion, the first on-off valve portion, and the second on-off valve portion via an actuator; 1 refrigerant passage and a second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion; characterized by comprising

In the compound valve of the invention of claim 2, the driving device causes the first on-off valve portion and the second on-off valve portion to open the first refrigerant passage and the second refrigerant passage, and the expansion valve portion to open the first refrigerant passage and the second refrigerant passage. 3 A state in which the opening degree of the refrigerant passage is adjusted, the first on-off valve portion and the second on-off valve portion close the first refrigerant passage and the second refrigerant passage, and the expansion valve portion opens the third refrigerant passage. It is characterized in that it is in a state in which the degree is adjusted.

In the compound valve of the invention of claim 3, in each of the above inventions, the first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion are: It is characterized by being formed adjacently within the housing.

In the compound valve of the invention of claim 4, in each of the above inventions, the housing includes a first housing member provided with a first refrigerant inlet, a first refrigerant outlet, a first refrigerant passage, and a first on-off valve portion; A second housing member provided with two refrigerant inlets, a second refrigerant outlet, a second refrigerant passage, and a second on-off valve portion, and a third refrigerant outlet, a third refrigerant passage, and an expansion valve portion are provided. A third housing member is coupled to the third housing member, and an actuator is provided over each housing member to drive the expansion valve portion and each opening/closing valve portion.

In the compound valve of the invention of claim 5, in the above invention, the first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion is formed in the first housing member in proximity to one surface of the first housing member, A second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion is formed in the second housing member in close proximity to one surface of the second housing member, and the first housing member includes the first on-off valve. The second housing member has a first communication portion extending from the first refrigerant passage on the first refrigerant inlet side of the portion to one surface of the first housing member, and the second housing member has a second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion. It has a second communicating portion extending from the passage to one surface of the second housing member, and the first and second housing members are joined at their one surfaces, and in this state, the communicating portions are matched to form a communicating passage. , the third housing member is coupled to the other surface of the second housing member.

A vehicle air conditioner according to a sixth aspect of the present invention includes the compound valve of each of the above inventions, a compressor for compressing refrigerant, and a refrigerant inlet connected to a refrigerant pipe on the discharge side of the compressor to dissipate heat from the refrigerant and heat the vehicle. A radiator for heating the air supplied to the interior, a heat absorber having a refrigerant outlet connected to the refrigerant pipe on the suction side of the compressor, absorbing heat from the refrigerant and cooling the air supplied to the vehicle interior, and a heat sink Equipped with an outdoor heat exchanger connected to the refrigerant pipe on the refrigerant outlet side of the unit and provided outside the vehicle, an indoor expansion valve for reducing the pressure of the refrigerant flowing into the heat absorber, and a control device, the outdoor heat exchanger The refrigerant pipe on the refrigerant outlet side is connected to the first refrigerant inlet of the composite valve, the refrigerant pipe on the suction side of the compressor is connected to the first refrigerant outlet of the composite valve, and the refrigerant pipe on the refrigerant outlet side of the radiator is connected to the composite valve. The refrigerant pipe on the refrigerant inlet side of the indoor expansion valve is connected to the second refrigerant outlet of the composite valve, and the refrigerant pipe on the refrigerant inlet side of the outdoor heat exchanger is connected to the third refrigerant outlet of the composite valve , and the control device controls the driving device of the composite valve.

According to the vehicle air conditioner of the invention of claim 7, in the above invention, the control device controls the driving device of the composite valve, thereby causing the first opening and closing valve portion and the second opening and closing valve portion of the composite valve to perform the first opening and closing. The refrigerant passage and the second refrigerant passage are opened, and the degree of opening of the third refrigerant passage is adjusted by the expansion valve portion to prevent the refrigerant from flowing into the heat absorber and heat the refrigerant discharged from the compressor. A heating mode in which the heat is released in the vessel, the refrigerant that has released heat is decompressed in the expansion valve, and the heat is absorbed in the outdoor heat exchanger, and the first opening and closing valve section of the composite valve and the second opening and closing valve section The refrigerant passage and the second refrigerant passage are opened, the opening degree of the third refrigerant passage is adjusted by the expansion valve portion, the refrigerant discharged from the compressor is dissipated by the radiator, and part of the dissipated refrigerant is The part is passed through the second on-off valve part to the indoor expansion valve, and after being decompressed by the indoor expansion valve, the heat is absorbed by the heat absorber, and the rest of the heat-dissipated refrigerant is decompressed by the expansion valve part, and then to the outdoor heat exchanger. A dehumidifying heating mode in which heat is absorbed by the first and second opening and closing valve portions of the composite valve, the first refrigerant passage and the second refrigerant passage are closed by the expansion valve portion, and the degree of opening of the third refrigerant passage is adjusted, the refrigerant discharged from the compressor is radiated by the radiator and the outdoor heat exchanger, and the radiated refrigerant is passed through the check valve of the composite valve to the indoor expansion valve, and the pressure is reduced by this indoor expansion valve. After that, the first refrigerant passage and the second refrigerant passage are closed by the dehumidifying cooling mode in which heat is absorbed by the heat absorber, and the first opening and closing valve portion and the second opening and closing valve portion of the composite valve. A cooling mode in which the refrigerant discharged from is radiated by the outdoor heat exchanger, the radiated refrigerant is flowed through the check valve of the composite valve to the indoor expansion valve, the pressure is reduced by the indoor expansion valve, and the heat is absorbed by the heat absorber. , are switched and executed.

According to the eighth aspect of the invention, there is provided a vehicle air conditioner comprising a temperature-adjusted object cooling device for cooling a temperature-adjusted object mounted on a vehicle using a refrigerant in the sixth or seventh aspect of the invention, The temperature control target cooling device includes a temperature control target heat exchanger for absorbing heat from a refrigerant to cool a temperature control target, and an auxiliary expansion valve for decompressing the refrigerant flowing into the temperature control target heat exchanger. The refrigerant inlet of the heat exchanger for temperature control is connected to a branch pipe branched from the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve, and the refrigerant outlet of the heat exchanger for temperature control is connected to the compressor The control device is connected to the refrigerant pipe on the suction side, and controls the driving device of the composite valve to open the first refrigerant passage and With the second refrigerant passage closed, the refrigerant discharged from the compressor is dissipated by the outdoor heat exchanger, and the dissipated refrigerant is passed through the check valve of the composite valve to the indoor expansion valve and the auxiliary expansion valve. A cooling/temperature-controlled cooling mode in which the pressure is reduced by the expansion valve, the heat is absorbed by the heat absorber, the pressure is reduced by the auxiliary expansion valve, and the heat is absorbed by the temperature-controlled heat exchanger, and the first opening/closing valve of the composite valve. In a state in which the first refrigerant passage and the second refrigerant passage are closed by the unit and the second on-off valve unit, the refrigerant is prevented from flowing into the heat absorber, and the refrigerant discharged from the compressor is transferred to the outdoor heat exchanger. A temperature controlled target cooling mode in which the heat is dissipated in and the heat-dissipated refrigerant is flowed through the check valve of the composite valve to the auxiliary expansion valve, decompressed by the auxiliary expansion valve, and then absorbed by the temperature controlled target heat exchanger. , are switched and executed.

According to the present invention, in a composite valve applied to a refrigerant circuit, a housing having a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, a second refrigerant outlet, and a third refrigerant outlet; a first refrigerant passage formed in the housing and extending between the first refrigerant inlet and the first refrigerant outlet; a second refrigerant passage formed in the housing and extending between the second refrigerant inlet and the second refrigerant outlet; A first on-off valve portion provided in the first refrigerant passage for opening and closing the first refrigerant passage; a second on-off valve portion provided in the second refrigerant passage for opening and closing the second refrigerant passage; a third refrigerant passage extending from the second refrigerant passage on the second refrigerant inlet side of the on-off valve portion to the third refrigerant outlet; and an expansion valve portion provided in the third refrigerant passage for adjusting the degree of opening of the third refrigerant passage. , a driving device for driving the expansion valve portion, the first on-off valve portion, and the second on-off valve portion via an actuator; A communication passage that communicates the passage with the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion, and a check valve that is provided in the communication passage and has a forward direction in the direction of the second refrigerant passage. Therefore, for example, according to the second aspect of the invention, the drive device causes the first on-off valve portion and the second on-off valve portion to open the first refrigerant passage and the second refrigerant passage, and the expansion valve portion to open the second refrigerant passage. 3 A state in which the opening degree of the refrigerant passage is adjusted, the first on-off valve portion and the second on-off valve portion close the first refrigerant passage and the second refrigerant passage, and the expansion valve portion opens the third refrigerant passage. The compressor for compressing the refrigerant and the refrigerant inlet are connected to the refrigerant pipe on the discharge side of the compressor, and the refrigerant is radiated to the vehicle interior as described in claim 6. A radiator for heating the air supplied to the compressor, a heat absorber whose refrigerant outlet is connected to the refrigerant pipe on the suction side of the compressor, and for absorbing heat from the refrigerant and cooling the air supplied to the vehicle interior, and a radiator A vehicle air conditioner equipped with an outdoor heat exchanger connected to the refrigerant pipe on the refrigerant outlet side of the vehicle and provided outside the vehicle, an indoor expansion valve for reducing the pressure of the refrigerant flowing into the heat absorber, and a control device Apply, the refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger is connected to the first refrigerant inlet of the compound valve, the refrigerant pipe on the suction side of the compressor is connected to the first refrigerant outlet of the compound valve, and the refrigerant of the radiator Connect the refrigerant pipe on the outlet side to the second refrigerant inlet of the compound valve, connect the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve to the second refrigerant outlet of the compound valve, and connect the refrigerant pipe on the refrigerant inlet side of the outdoor heat exchanger. is connected to the third refrigerant outlet of the composite valve, the control device controls the driving device of the composite valve Thus, the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode can be switched and executed.

Further, as in the eighth aspect of the present invention, a temperature-controlled object cooling device for cooling a temperature-controlled object mounted on a vehicle using a refrigerant is provided, and the temperature-controlled object cooling device absorbs heat from the refrigerant to cool the temperature-controlled object. A refrigerant inlet of the heat exchanger for the temperature control target provided with a heat exchanger for the temperature control target for cooling the temperature control target and an auxiliary expansion valve for decompressing the refrigerant flowing into the heat exchanger for the temperature control target. is connected to the branch pipe branched from the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve, and the refrigerant outlet of the heat exchanger for temperature control is connected to the refrigerant pipe on the suction side of the compressor. By controlling the driving device, it is possible to switch between the cooling/temperature-controlled cooling mode and the temperature-controlled cooling mode.

That is, the function of switching the operation mode of a vehicle air conditioner, which was conventionally performed by a plurality of electromagnetic valves, and the function of reducing the pressure of the refrigerant, which was performed by an expansion valve, can be integrated into the composite valve, reducing the number of parts. It is possible to reduce the parts cost and production cost by reducing the number of parts, and to reduce the installation space.

In this case, the first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion are adjacent to each other in the housing. With this configuration, the first refrigerant passage and the second refrigerant passage can be communicated with each other through a communication passage having a short dimension, and loss such as pressure loss in the communication passage can be minimized. .

Further, as in the invention of claim 4, the housing is composed of a first housing member provided with a first refrigerant inlet, a first refrigerant outlet, a first refrigerant passage, and a first on-off valve portion, a second refrigerant inlet, a first a second housing member provided with a second refrigerant outlet, a second refrigerant passage, and a second on-off valve portion; and a third housing member provided with a third refrigerant outlet, a third refrigerant passage, and an expansion valve portion; , and an actuator is provided over each housing member to drive the expansion valve portion and each on-off valve portion, the manufacturing/assembling work of the compound valve is facilitated.

In particular, as in the invention of claim 5, the first refrigerant passage on the side of the first refrigerant inlet from the first on-off valve portion is formed in the first housing member close to one surface of the first housing member, and the second on-off valve A second refrigerant passage on the side of the second refrigerant outlet from the section is formed in the second housing member close to one surface of the second housing member, and the first housing member is provided with the first refrigerant inlet from the first on-off valve section. A first communication portion is formed from the first refrigerant passage on the side of the first housing member to one surface of the first housing member, and the second housing member is provided with the second refrigerant passage from the second refrigerant outlet side of the second on-off valve portion to the second housing member. A second communicating portion extending to one surface is formed, and when the one surfaces of the first and second housing members are joined together, the communicating portions are aligned to form a communicating passage, and the third housing member is the second housing member. If it is connected to the other surface of the member, a short communication passage can be easily constructed, the check valve can be easily attached, and the third housing member can be connected without any trouble.

1 is a cross-sectional view of a composite valve of one embodiment to which the present invention is applied (state in which the expansion valve portion adjusts the degree of opening and the first on-off valve portion and the second on-off valve portion are open); FIG. 2 is a cross-sectional view of the compound valve of FIG. 1 in a state where the expansion valve section fully closes the third refrigerant passage and the first on-off valve section and the second on-off valve section open the first and second refrigerant passages; 2 is a cross-sectional view of the compound valve of FIG. 1 in a state in which the expansion valve portion adjusts the degree of opening of the third refrigerant passage, and the first on-off valve portion and the second on-off valve portion close the first and second refrigerant passages; FIG. FIG. 2 is a cross-sectional view of the composite valve of FIG. 1 in a state in which the expansion valve section fully opens the third refrigerant passage, and the first on-off valve section and the second on-off valve section close the first and second refrigerant passages; It is a figure explaining operation|movement of a compound valve. FIG. 2 is a configuration diagram of an embodiment of a vehicle air conditioner to which the composite valve of FIG. 1 is applied; FIG. 7 is a block diagram of an air conditioning controller as a control device for the vehicle air conditioner of FIG. 6 ; 8 is a diagram for explaining a heating mode by the air conditioning controller of FIG. 7; FIG. It is a figure explaining the dehumidification heating mode by the air-conditioning controller of FIG. 8 is a diagram for explaining a dehumidifying cooling mode/cooling mode by the air conditioning controller of FIG. 7; FIG. FIG. 8 is a diagram for explaining a cooling/temperature-controlled target cooling mode by the air conditioning controller of FIG. 7; FIG. 8 is a diagram for explaining a temperature-controlled cooling mode by the air conditioning controller of FIG. 7;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
(1) Compound valve 81
1 to 4 show cross-sectional views of a compound valve 81 of one embodiment to which the present invention is applied, and FIG. 5 is a diagram for explaining the operation of the compound valve 81. FIG. A composite valve 81 of the present invention is applied to a refrigerant circuit R of a vehicle air conditioner 1 or the like, which will be described later. The valve portion 6, the check valve 18, the first on-off valve portion 21, the second on-off valve portion 22, and the driving device 83 for driving the expansion valve portion 6, the first and second on-off valve portions 21 and 22 are provided. I have it.

The driving device 83 adjusts and drives the expansion valve portion 6 via the actuator 84 and further drives the first and second opening/closing valve portions 21 and 22 to open and close. The driving device 83 of this embodiment is composed of a stepping motor.

Further, the housing 82 of the embodiment is constructed by combining three parts, a first housing member 86, a second housing member 87, and a third housing member 85, all of which are made of a metal block such as aluminum. A first coolant inlet 88 and a first coolant outlet 89 are formed on one side and the other side of the first housing member 86, respectively. A first coolant passage 91 extending between the 89 is formed.

A second coolant inlet 92 and a second coolant outlet 93 are formed on the other side and one side of the second housing member 87, respectively. A second refrigerant passage 94 is formed between the two refrigerant outlets 93 . Further, a third coolant outlet 97 is formed on the other side surface of the third housing member 85, and an opening 85A is formed on one side. A third coolant passage 98 is formed between 97 .

The first on-off valve portion 21 is formed from a first valve seat 21A provided in the first refrigerant passage 91 and a first valve body 21B for opening and closing the first refrigerant passage 91 by coming into contact with the first valve seat 21A. The second opening/closing valve portion 22 includes a second valve seat 22A provided in the second refrigerant passage 94 and a second opening for opening and closing the second refrigerant passage 94 by contacting the second valve seat 22A. It is composed of two valve bodies 22B.

The expansion valve portion 6 includes a third valve seat 6A provided in the third refrigerant passage 98, and a third valve body for adjusting the opening degree of the third refrigerant passage 98 by contacting the third valve seat 6A. The third valve seat 6A is located inside the third refrigerant passage 98 on the third refrigerant outlet 97 side of the opening 85A. located in An internal passage 6D is formed in the third valve body 6B from the surface on the side of the third valve seat 6A to one side surface, and the needle valve body 6C extends from the surface of the internal passage 6D on the side of the third valve seat 6A. Adjust the opening of the opening.

One surface of the first housing member 86 and the second housing member 87 are coupled to each other, and one surface of the third housing member 85 is coupled to the other surface (the surface opposite to the one surface) of the second housing member 87 to form an integral unit. The second housing member 87 has an opening 87A on the other surface thereof, which communicates with the second refrigerant passage 94 closer to the second refrigerant inlet 92 than the second on-off valve portion 22. When the other surface of the second housing member 87 and one surface of the third housing member 85 are joined, the opening 87A matches the opening 85A of the third housing member 85 and communicates with each other.

The driving device 83 is attached to the other surface of the third housing member 85 (the surface opposite to one surface). The actuator 84 of the drive device 83 is composed of a first actuator member 84A, a second actuator member 84B and a third actuator member 84C. It is attached to the tip of the member 84A. The second actuator member 84B is located at a communicating portion between the openings 85A and 87A, and is attached between the surface of the third valve body 6B opposite to the third valve seat 6A and the second valve body 22B, and is extendable. there is The third actuator member 84C penetrates the second housing member 87 and is attached between the second valve body 22B and the first valve body 21B. As a result, the actuator 84 is provided across the housing members 85 , 87 , 86 to drive the expansion valve section 6 and the on-off valve sections 21 , 22 .

The driving device 83 (stepping motor) is rotationally controlled by the number of pulses. When the driving device 83 rotates, the actuator 84 (first to third actuator members 84A to 84C) moves the needle valve body 6C up and down. 21B and the second valve body 22B are driven simultaneously. That is, in this embodiment, when the driving device 83 is at the 0 pulse position, the first actuator member 84A and the needle valve body 6C are positioned closest to the driving device 83 side. In this state, the third valve body 6B contacts the third valve seat 6A to close the third valve seat 6A, but the needle valve body 6C is close to the opening of the internal passage 6D of the third valve body 6B. , the internal passage 6D is opened, and the opening degree of the third refrigerant passage 98 is narrowed (a state in which the opening degree is adjusted). Further, the first valve body 21B is separated from the first valve seat 21A, the first on-off valve portion 21 opens the first refrigerant passage 91, and the second valve body 22B is separated from the second valve seat 22A, and The second on-off valve portion 22 opens the second refrigerant passage 84 (FIG. 1).

When the driving device 83 is rotated forward by several pulses from the state shown in FIG. 1, the first actuator member 84A moves the needle valve body 6C toward the third valve body 6B, and soon the needle valve body 6C moves toward the third valve body 6B. It abuts against the opening of the internal passage 6D and closes, and in this state, the expansion valve portion 6 is in a state in which the third refrigerant passage 98 is fully closed. In this application, adjusting the degree of opening is a concept that includes fully closed and fully opened. This state is the state of FIG. 2. At this point, the first valve body 21B is still separated from the first valve seat 21A, the first on-off valve section 21 opens the first refrigerant passage 91, and the second valve body 22B is opened. The second on-off valve portion 22 opens the second refrigerant passage 84 apart from the second valve seat 22A (Fig. 2).

When the driving device 83 is further rotated forward by several pulses from the state shown in FIG. 2, the needle valve body 6C pushes the third valve body 6B toward the second valve body 22B, so that the third valve body 6B moves toward the third valve. It is separated from the seat 6A, and the state in which the degree of opening of the third refrigerant passage 98 is narrowed again (the state in which the degree of opening is adjusted) is reached. This state is the state shown in FIG. 3. At this point, the first valve body 21B contacts the first valve seat 21A, the first opening/closing valve portion 21 closes the first refrigerant passage 91, and the second valve body 22B is closed. The second on-off valve portion 22 closes the second refrigerant passage 84 by coming into contact with the second valve seat 22A (FIG. 3).

When the driving device 83 is further rotated forward by several pulses from the state shown in FIG. 3, the needle valve body 6C pushes the third valve body 6B toward the second valve body 22B, so that the third valve body 6B eventually moves to the third valve seat. It is greatly separated from 6A and is in a state of being fully opened with the third refrigerant passage 98 . This state is the state of FIG. 4. In this state, the second actuator member 84B is contracted, so that the first valve body 21B abuts against the first valve seat 21A and the first on-off valve portion 21 is closed by the first refrigerant passage 91. is closed, the second valve body 22B contacts the second valve seat 22A, and the second on-off valve portion 22 maintains the state in which the second refrigerant passage 84 is closed (FIG. 4).

Further, if the driving device 83 is rotated in the reverse direction, the operation is reversed to the above. FIG. 5 summarizes the above operations. In FIG. 5, the horizontal axis indicates the number of pulses of the driving device 83, and the vertical axis indicates the opening areas of the coolant passages 91, 94, and 98. As shown in FIG. In the drawing, the thick solid line indicates the degree of opening of the third refrigerant passage 98 by the expansion valve portion 6, the thick broken line indicates the open/closed state of the first refrigerant passage 91 by the first on-off valve portion 21, and the thin broken line indicates the second refrigerant by the second on-off valve 22. The open/closed state of the passage 94 is shown. 5, P1 indicates the state of FIG. 1, P2 indicates the state of FIG. 2, P3 indicates the state of FIG. 3, and P4 indicates the state of FIG. The control range in the heating mode of the vehicle air conditioner 1 described later, "dehumidifying heating" indicates the control range in the dehumidifying heating mode described later, and "dehumidifying cooling" indicates the control in the dehumidifying cooling mode described later. The range "cooling" indicates the control range in the cooling mode, which will be described later. As is clear from this figure, in the dehumidifying and heating mode, the expansion valve portion 6 is used from a state in which the degree of opening of the third refrigerant passage 98 is adjusted to a state in which the third refrigerant passage 98 is fully closed. In this way, the compound valve 81 is constructed so that the single driving device 83 can simultaneously adjust the opening degree of the expansion valve portion 6 and open/close the two opening/closing valve portions 21 and 22 .

A first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first valve seat 21A is formed close to one surface of the first housing member 86, and a first communicating portion extending from the close portion to the one surface. 96A is formed. A second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the second valve seat 22A is formed close to one surface of the second housing member 87, and a second communicating portion extending from this close portion to the one surface. 96B is formed. Communicating portions 96A and 96B are aligned with each other in a state where one surfaces of housing members 86 and 87 are joined to form a communicating passage 96. As shown in FIG. At this time, the check valve 18 is attached to one of the communicating portions (96A or 96B), and when the housing members 86 and 87 are joined, the check valve 18 is installed in the other communicating portion (96B or 96A). If it is made to advance, the non-return valve 18 will also come to be attached easily.

Also, with such a configuration, the first refrigerant passage 91 on the first refrigerant inlet 88 side of the first valve seat 21A and the second refrigerant passage 94 on the second refrigerant outlet 93 side of the second valve seat 22A are adjacent in the housing 82. It becomes a form to do. The communication path 96 communicates the first refrigerant passage 91 on the first refrigerant inlet 88 side of the first valve seat 21A and the second refrigerant passage 94 on the second refrigerant outlet 93 side of the second valve seat 22A. A check valve 18 is provided in the communication passage 96, and the direction of the second refrigerant passage 94 is the forward direction.

In the compound valve 81, as shown in FIG. 1, the needle valve body 6C of the expansion valve section 6 opens the internal passage 6D in the third valve body 6B to adjust the degree of opening of the third refrigerant passage 98, thereby opening the first on-off valve section. 21 and the second on-off valve portion 22 open the first refrigerant passage 91 and the second refrigerant passage 94, the refrigerant flowing in from the second refrigerant inlet 92 is divided, one of which is throttled by the expansion valve portion 6 to the third refrigerant passage. The refrigerant flows out from the refrigerant outlet 97 , and the other flows out from the second refrigerant outlet 93 after passing through the second on-off valve portion 22 . Also, the refrigerant that has flowed in from the first refrigerant inlet 88 passes through the first on-off valve portion 21 and flows out from the first refrigerant outlet 89 (indicated by white arrows and thin line arrows in FIG. 1).

2 by the driving device 83, the expansion valve portion 6 closes the third refrigerant passage 98, so that the refrigerant flowing from the second refrigerant inlet port 92 passes through the second opening/closing valve portion 22 and enters the second opening/closing valve portion 22. The refrigerant that flows out from the second refrigerant outlet 93 and flows in from the first refrigerant inlet 88 passes through the first on-off valve portion 21 and flows out from the first refrigerant outlet 89 (indicated by the white arrow in FIG. 1).

3 by the driving device 83, the refrigerant flowing in from the second refrigerant inlet 92 is throttled by the expansion valve portion 6, flows out from the third refrigerant outlet 97, and flows from the first refrigerant inlet 88 to the third refrigerant outlet. The refrigerant flowing into the first refrigerant passage 91 passes through the check valve 18, reaches the second refrigerant passage 94, and flows out from the second refrigerant outlet 93 (indicated by white arrows and thin line arrows in FIG. 3).

4 by the driving device 83, the refrigerant flowing in from the second refrigerant inlet 92 passes through the expansion valve portion 6 as it is, flows out from the third refrigerant outlet 97, and flows from the first refrigerant inlet 88 to the third refrigerant outlet. The refrigerant that has flowed into the first refrigerant passage 91 passes through the check valve 18, reaches the second refrigerant passage 94, and flows out from the second refrigerant outlet 93 (indicated by white arrows and thin line arrows in FIG. 4).

(2) Circuit Configuration of Vehicle Air Conditioner 1 Next, the vehicle air conditioner 1 to which the composite valve 81 of the present invention is applied will be described with reference to FIG. FIG. 6 shows a configuration diagram of a vehicle air conditioner 1 of one embodiment. Here, the vehicle to which the vehicle air conditioner 1 of the embodiment is applied is an electric vehicle (EV) that is not equipped with an engine (internal combustion engine), and the vehicle is equipped with a battery (for example, a lithium battery), The electric power charged in the battery from the external power supply is supplied to the driving motor (electric motor) to drive and run.

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

It goes without saying that the present invention is effective not only for electric vehicles, but also for so-called hybrid vehicles that share an engine and an electric motor for running, and ordinary engine-driven vehicles.

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 (electric compressor) 2 for compressing a refrigerant. a radiator 4 provided in the air flow passage 3 of the HVAC unit 10 through which the vehicle interior air is ventilated and circulated to heat the air supplied to the vehicle interior by releasing the heat of the refrigerant; The indoor expansion consists of an outdoor heat exchanger 7 for exchanging heat between the refrigerant and the outside air to function as a radiator and an evaporator that absorbs heat from the refrigerant during heating, and an electric valve that decompresses and expands the refrigerant. A valve 8, a heat absorber 9 provided in the air flow passage 3 for absorbing heat from the refrigerant from outside and outside the vehicle interior during cooling and dehumidification to cool the air supplied to the vehicle interior, an accumulator 12, and the above-described composite A refrigerant circuit R is configured by sequentially connecting the valves 81 and the like by the refrigerant pipes 13 .

The indoor expansion valve 8 decompresses and expands the refrigerant, and can be fully opened or fully closed. Also, the refrigerant inlet of the radiator 4 is connected to the refrigerant pipe 13G on the discharge side of the compressor 2 . In addition, the outdoor heat exchanger 7 is provided with an outdoor fan 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.

The refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to the first refrigerant inlet 88 of the composite valve 81, and the second refrigerant outlet 93 of the composite valve 81 is connected to the refrigerant pipe on the refrigerant inlet side of the indoor expansion valve 8. 13B is connected. A first refrigerant outlet 89 of the composite valve 81 is connected to a refrigerant pipe 13D that constitutes a part of the refrigerant pipe on the suction side of the compressor 2, and this refrigerant pipe 13D is connected to the refrigerant outlet side of the heat absorber 9. It is communicatively connected to the pipe 13C. This refrigerant pipe 13</b>C constitutes the main part of the refrigerant pipe on the suction side of the compressor 2 . A check valve 20 is connected to the refrigerant pipe 13C on the downstream side of the connection point of the refrigerant pipe 13D, and the refrigerant pipe 13C on the downstream side of the check valve 20 is connected to the suction side of the compressor 2 via the accumulator 12. It is connected to the. The check valve 20 is oriented forward toward the accumulator 12 side. Further, the entire refrigerant pipe from the refrigerant outlet side of the heat absorber 9 to the suction side of the compressor 2 is denoted by reference numeral 13C.

Furthermore, the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4 is connected to the second refrigerant inlet 92 of the composite valve 81, and the refrigerant pipe 13J on the refrigerant inlet side of the outdoor heat exchanger 7 is connected to the third refrigerant of the composite valve 81. It is connected to outlet 97 .

In addition, the air flow passage 3 on the air upstream side of the heat absorber 9 is formed with an external air suction port and an internal air suction port (represented by a suction port 25 in FIG. 6). 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 FIG. 6, reference numeral 23 denotes an auxiliary heater as an auxiliary heating device. The auxiliary heater 23 is composed of a PTC heater (electric heater) in the embodiment, and is provided in the air flow passage 3 downstream of the radiator 4 with respect to the air flow in the air flow passage 3. there is When the auxiliary heater 23 is energized and heats up, it functions as a so-called heater core to supplement the heating of the passenger compartment.

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 and the auxiliary heater 23 . Furthermore, 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 outlet 29 in FIG. 6) 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.

(3) Temperature controlled cooling device 61
Furthermore, the vehicle air conditioner 1 includes a temperature controlled object cooling device 61 for circulating a heat medium to cool a temperature controlled object 55 such as a battery or a running motor mounted on the vehicle. That is, in the embodiment, the temperature controlled object 55 mounted on the vehicle is a battery or a running motor, but the following description assumes that the temperature controlled object 55 is a battery. In the present invention, the object to be temperature-controlled is not limited to the battery and the motor for running, but includes an electric device such as an inverter circuit for driving the motor for running.

A temperature-controlled target cooling device 61 of the embodiment includes a circulation pump 62 as a circulation device for circulating a heat medium to a temperature-controlled target 55, and a temperature-controlled target heat exchanger 64. An object to be adjusted 55 is connected by a heat medium pipe 68 . In the embodiment, the inlet of the heat medium flow path 64A of the heat exchanger 64 for temperature control target is connected to the discharge side of the circulation pump 62, and the temperature control target 55 is connected to the outlet of the heat medium flow path 64A. ing. The outlet of the temperature controlled object 55 is connected to the suction side of the circulation pump 62 .

As the heat medium used in the temperature controlled cooling device 61, for example, water, 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. Further, it is assumed that a jacket structure is provided around the temperature controlled object 55 (battery) so that, for example, a heat medium can flow with the temperature controlled object 55 in a heat exchange relationship.

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

On the other hand, one end of a branch pipe 72 is connected to the refrigerant pipe 13B on the refrigerant inlet side of the indoor expansion valve 8 . The branch pipe 72 is provided with an auxiliary expansion valve 73 which is an electric valve. The auxiliary expansion valve 73 decompresses and expands the refrigerant flowing into the later-described refrigerant flow path 64B of the heat exchanger 64 for temperature control and can be fully closed.

The other end of the branch pipe 72 is connected to the refrigerant inlet of the refrigerant flow path 64B of the heat exchanger 64 for temperature control, and the refrigerant outlet of the refrigerant flow path 64B is a check valve via the refrigerant pipe 74. 20 downstream of the refrigerant and before the accumulator 12 (refrigerant upstream). Therefore, the refrigerant pipe 74 also constitutes part of the refrigerant pipe on the suction side of the compressor 2 . 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 cooling device 61 subject to temperature control.

When the auxiliary expansion valve 73 is open, the refrigerant flowing into the refrigerant pipe 13B flows into the branch pipe 72, and after being decompressed by the auxiliary expansion valve 73, flows into the refrigerant flow path 64B of the heat exchanger 64 for temperature control. and evaporate there. 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.

(4) Air-conditioning controller 32 (control device) of vehicle air conditioner 1
Next, in FIG. 7, reference numeral 32 denotes an air conditioning controller 32 as a control device for controlling the vehicle air conditioner 1. As shown in FIG. The air-conditioning controller 32 is connected via a vehicle communication bus 45 to a vehicle controller 35 (ECU) that controls the entire vehicle including control of the temperature controlled object 55 (battery and running motor), and transmits and receives information. It is configured. Each of these air conditioning controller 32 and vehicle controller 35 (ECU) is composed of a microcomputer as an example of a computer having a processor.

The inputs of the air conditioning controller 32 (control device) include 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 air drawn into the flow path 3 from the intake port 25. An HVAC intake temperature sensor 36 that detects the air temperature, 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 carbon dioxide in the vehicle interior. An indoor CO ₂ concentration sensor 39 that detects the carbon concentration, an air outlet temperature sensor 41 that detects the temperature of the air blown into the passenger compartment from the air outlet 29, and a pressure of the refrigerant discharged from the compressor 2 (discharge pressure Pd) is detected. A discharge pressure sensor 42, a discharge temperature sensor 43 that detects the temperature of the refrigerant discharged from the compressor 2, a suction temperature sensor 44 that detects the temperature of the refrigerant drawn into the compressor 2, and the temperature of the radiator 4 (air passing through the radiator 4 or the temperature of the radiator 4 itself: radiator temperature TCI), and the refrigerant pressure of the radiator 4 (the refrigerant in the radiator 4 or immediately after leaving the radiator 4 pressure: radiator pressure PCI) and the temperature of the heat absorber 9 (the temperature of the air passing through the heat absorber 9 or the temperature of the heat absorber 9 itself: heat absorber temperature Te) A heat absorber temperature sensor 48, a heat absorber pressure sensor 49 that detects 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 the amount of solar radiation into the vehicle compartment. For example, a photo sensor type solar radiation sensor 51 for detection, a vehicle speed sensor 52 for detecting the moving speed of the vehicle (vehicle speed), and an air conditioner for setting ON/OFF of air conditioning, setting temperature and switching of operation mode The operation unit 53 and the temperature of the outdoor heat exchanger 7 (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: the outdoor heat exchanger temperature TXO. The outdoor heat exchanger 7 functions as an evaporator, the outdoor heat exchanger temperature TXO becomes the evaporation temperature of the refrigerant in the outdoor heat exchanger 7), and the refrigerant pressure in the outdoor heat exchanger 7 (outdoor Each output of an outdoor heat exchanger pressure sensor 56 for detecting the pressure of the refrigerant in the heat exchanger 7 or immediately after coming out of the outdoor heat exchanger 7 is connected.

Further, the input of the air conditioning controller 32 includes the temperature of the temperature controlled object 55 (for example, battery) mounted on the vehicle (the temperature of the temperature controlled object 55 itself, or the heat medium exiting the temperature controlled object 55 or the temperature of the heat medium entering the temperature controlled object 55 (temperature controlled object temperature Tw).

On the other hand, the outputs of the air conditioning 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 indoor The expansion valve 8, the driving device 83 of the composite valve 81, the auxiliary heater 23, the circulation pump 62 of the temperature controlled cooling device 61, and the auxiliary expansion valve 73 are connected. The air conditioning controller 32 controls these based on the output of each sensor, the settings input by the air conditioning operation section 53 and the information from the vehicle controller 35 .

(5) Operation of Vehicle Air Conditioner 1 Including Compound Valve 81 With the above configuration, the operation of the vehicle air conditioner 1 of the embodiment will be described next. In the embodiment, the air conditioning controller 32 (control device) can switch between a heating mode, a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, a cooling/temperature controlled cooling mode, and a temperature controlled cooling mode. It is Each operation mode will be described below.

(5-1) Heating Mode First, the heating mode will be described with reference to FIG. FIG. 8 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the heating mode. When the heating mode is selected by the air conditioning controller 32 (auto mode) or by manual operation (manual mode) of the air conditioning operation unit 53, the air conditioning controller 32 controls the driving device 83 of the composite valve 81 to operate the actuator 84. The expansion valve portion 6 adjusts the degree of opening of the third refrigerant passage 98, and the first on-off valve portion 21 and the second on-off valve portion 22 open the first refrigerant passage 91 and the second refrigerant passage 94. Open (state shown in FIG. 1). In addition, the indoor expansion valve 8 and the auxiliary expansion valve 73 are fully closed (inflow of the refrigerant to the heat absorber 9 and the temperature-controlled heat exchanger 64 is blocked).

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 and the auxiliary heater 23 . As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air 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 the refrigerant liquefied in the radiator 4 leaves the radiator 4, it reaches the expansion valve portion 6 of the composite valve 81 through the refrigerant pipe 13E. After the refrigerant that has flowed into the expansion valve portion 6 is decompressed there, it flows into the outdoor heat exchanger 7 through the refrigerant pipe 13J. 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. The low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the first refrigerant passage 91 of the composite valve 81 from the refrigerant pipe 13A, passes through the first on-off valve portion 21, and exits to the refrigerant pipe 13D.

Refrigerant exiting the refrigerant pipe 13D enters the refrigerant pipe 13C, passes through the check valve 20, and enters the accumulator 12. After the gas-liquid separation there, the gas refrigerant is sucked into the compressor 2, repeating the circulation. Since the air heated by the radiator 4 is blown out from the outlet 29, the vehicle interior is heated. Although the second on-off valve portion 22 of the compound valve 81 is also open, the indoor expansion valve 8 and the auxiliary expansion valve 73 are fully closed, so the refrigerant does not flow into the second refrigerant passage 94 .

The air conditioning controller 32 converts a target heater temperature TCO (a target value of the air temperature on the leeward side of the radiator 4) calculated from a target blowout temperature TAO, which will be described later, into a target radiator pressure PCO (a target value of the pressure PCI of the radiator 4). is calculated, and the rotation speed of the compressor 2 is controlled 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) At the same time, based on the temperature of the radiator 4 (radiator temperature TCI) detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47, the driving device 83 of the composite valve 81 is controlled to expand. The degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled by adjusting the degree of opening of the third refrigerant passage 98 by the valve portion 6 . The target heater temperature TCO is basically set to TCO=TAO, but a predetermined control limit is provided. Further, when the heating capacity of the radiator 4 is insufficient, the auxiliary heater 23 is energized to generate heat to complement the heating capacity.

(5-2) Dehumidifying Heating Mode Next, the dehumidifying heating mode will be described with reference to FIG. FIG. 9 shows the flow of refrigerant (solid line arrows) in the refrigerant circuit R in the dehumidifying and heating mode. In the dehumidifying heating mode, the air conditioning controller 32 opens the indoor expansion valve 8 to decompress and expand the refrigerant in the heating mode. As a result, part of the refrigerant that has passed through the radiator 4 and has reached the second refrigerant inlet 92 of the composite valve 81 from the refrigerant pipe 13E passes through the second on-off valve portion 22 of the composite valve 81 and is branched to the second refrigerant passage 94, The branched refrigerant flows from the second refrigerant outlet 93 into the refrigerant pipe 13B, flows from the refrigerant pipe 13B to the indoor expansion valve 8, and the rest of the refrigerant flows to the expansion valve portion 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.

The air conditioning controller 32 controls the degree of opening 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. At , the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, so the air is cooled and dehumidified. After being decompressed by the expansion valve portion 6, the remaining divided refrigerant enters the outdoor heat exchanger 7 via the refrigerant pipe 13J and evaporates.

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), and is sucked into the compressor 2 via the check valve 20 and the accumulator 12. repeat the 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 air conditioning controller 32 controls the rotation speed of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. At the same time, based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48, the driving device 83 of the composite valve 81 is controlled to adjust the opening degree of the third refrigerant passage 98 by the expansion valve portion 6. do.

As described above, in this dehumidifying heating mode, the expansion valve portion 6 of the compound valve 81 is also fully closed. Therefore, when the expansion valve portion 6 is fully closed as shown in FIG. 2 in the dehumidifying heating mode of FIG. All of the condensed refrigerant flowing through the refrigerant pipe 13</b>E flows through the second on-off valve portion 22 of the composite valve 81 . Then, the refrigerant passes through the second refrigerant passage 94 of the compound valve 81 and reaches the indoor expansion valve 8 from the refrigerant pipe 13B. 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 check valve 20 and 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 process of passing through the radiator 4, dehumidifying and heating the vehicle interior is performed. Since the refrigerant circulates between the radiator 4 (heat dissipation) and the heat absorber 9 (heat absorption) inside, heat is not drawn up from the outside air, and the heating capacity corresponding to the power consumption of the compressor 2 is exhibited. It will be. Therefore, since the entire amount of refrigerant flows through the heat absorber 9 that exerts the dehumidifying action, the dehumidifying capacity is high, but the heating capacity is low.

(5-3) Dehumidifying Cooling Mode Next, the dehumidifying cooling mode will be described with reference to FIG. FIG. 10 shows the refrigerant flow (solid line arrow) in the refrigerant circuit R in the dehumidifying cooling mode. In the dehumidification cooling mode, the air conditioning controller 32 opens the indoor expansion valve 8 to decompress and expand the refrigerant, and the drive device 83 of the composite valve 81 causes the actuator 84 to cause the expansion valve portion 6 to change the opening degree of the third refrigerant passage 98. is adjusted, and the first refrigerant passage 91 and the second refrigerant passage 94 are closed by the first on-off valve portion 21 and the second on-off valve portion 22 (state in FIG. 3). In addition, the auxiliary expansion valve 73 is fully closed (prevents the refrigerant from flowing into the temperature-controlled heat exchanger 64).

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 and the auxiliary heater 23 . As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air 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 exiting the radiator 4 passes through the refrigerant pipe 13E and reaches the expansion valve portion 6 of the composite valve 81, where it is slightly throttled and then flows into the outdoor heat exchanger 7 through the refrigerant pipe 13J. 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 flows into the refrigerant pipe 13A and enters the first refrigerant passage 91 from the first refrigerant inlet 88 of the composite valve 81 .

At this time, since the first on-off valve portion 21 and the second on-off valve portion 22 are closed, the refrigerant that has flowed into the first refrigerant passage 91 enters the second refrigerant passage 94 through the communication passage 96 and the check valve 18. , from the second refrigerant outlet 93 into the refrigerant pipe 13B. The refrigerant that has flowed into the refrigerant pipe 13B reaches the indoor expansion valve 8, and after being decompressed by the indoor expansion valve 8, 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 the check valve 20, and is sucked into the compressor 2 through the accumulator 12, repeating circulation. The dehumidified air cooled by the heat absorber 9 is reheated in the process of passing through the radiator 4 (reheating: the heat dissipation capacity is lower than that during heating and dehumidifying heating), thereby dehumidifying and cooling the passenger compartment. will be done.

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 air conditioning 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, the target radiator pressure PCO (radiator pressure Based on the target value of PCI), the driving device 83 of the composite valve 81 is controlled so that the radiator pressure PCI becomes the target radiator pressure PCO, and the opening degree of the third refrigerant passage 98 is controlled by the expansion valve section 6. to obtain the amount of reheat required by the radiator 4.

(5-4) Cooling Mode Next, the cooling mode will be described. The flow of the refrigerant circuit R is the same as in the dehumidification cooling mode of FIG. In the cooling mode, the air conditioning controller 32 fully opens the expansion valve portion 6 of the composite valve 81 in the dehumidifying cooling mode (state shown in FIG. 4). Incidentally, the air mix damper 28 is in a state of adjusting the ratio of the air to the radiator 4 and the auxiliary heater 23 .

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Although the air in the air 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 reaches the expansion valve portion 6 of the composite valve 81 through the refrigerant pipe 13E. At this time, since the expansion valve portion 6 fully opens the third refrigerant passage 98, the refrigerant passes through the expansion valve portion 6 and the refrigerant pipe 13J as it is, and flows into the outdoor heat exchanger 7, where the vehicle travels or is operated by the outdoor blower. At 15, it is air-cooled by the outside air ventilated and condensed and liquefied. The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13A, the first refrigerant passage 91 of the composite valve 81, the communication passage 96 (the check valve 18), and the second refrigerant passage 94, enters the refrigerant pipe 13B, and enters the indoor expansion valve. up to 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 the check valve 20, and is sucked into the compressor 2 through the accumulator 12, 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 mode, the air conditioning controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 .

(5-5) Switching between Heating Mode, Dehumidifying Heating Mode, Dehumidifying Cooling Mode, and Cooling Mode The air conditioning controller 32 calculates the aforementioned target outlet 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.

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

(5-6) Cooling/Temperature Control Target Cooling Mode Next, the cooling/temperature control target cooling mode by the air conditioning controller 32 during the cooling mode will be described with reference to FIG. Here, the temperature of the battery (to be subject to temperature control) rises due to the temperature of the outside air, and the temperature also rises due to self-heating during charging and discharging. That is, when the outside air temperature is high, the temperature of the battery becomes extremely high, making charging and discharging difficult. may malfunction).

Therefore, the air-conditioning controller 32 of the vehicle air-conditioning apparatus 1 of the embodiment has a predetermined target temperature TWO (for example, the target temperature of the battery) for the temperature Tw to be controlled, and a predetermined hysteresis above and below it. When the upper limit value TWH and the lower limit value TWL are set and the cooling mode as described above is executed, the temperature to be controlled Tw detected by the temperature control target temperature sensor 76 rises above the predetermined upper limit value TWH. , the cooling mode is changed to the cooling/temperature controlled cooling mode. FIG. 11 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrows) and the flow of the heat medium in the temperature controlled cooling device 61 (broken line arrows) in this cooling/temperature controlled cooling mode.

In this cooling/temperature controlled target cooling mode, the air conditioning controller 32 opens the auxiliary expansion valve 73 in the cooling mode state of the refrigerant circuit R shown in FIG. The valve opening is controlled based on. Then, the circulation pump 62 of the temperature controlled cooling device 61 is operated. As a result, the refrigerant coming out of the radiator 4 passes through the expansion valve portion 6 of the composite valve 81 as described above and flows into the outdoor heat exchanger 7, where the outside air is blown by the running or the outdoor blower 15. It is air-cooled and condensed and liquefied. The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13A, the first refrigerant passage 91 of the composite valve 81, the communication passage 96 (the check valve 18), and the second refrigerant passage 94, enters the refrigerant pipe 13B, and enters the indoor expansion valve. up to 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 the check valve 20, and is sucked into the compressor 2 through the accumulator 12, repeating circulation. On the other hand, part of the refrigerant that has entered the refrigerant pipe 13B enters the branch pipe 72, is decompressed by the auxiliary expansion valve 73, and flows through the branch pipe 72 into the refrigerant flow path 64B of the heat exchanger 64 for temperature control. and evaporate. 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 line arrows in FIG. 11).

On the other hand, the heat medium discharged from the circulation pump 62 reaches the heat medium flow path 64A of the heat exchanger 64 for temperature control target through the heat medium pipe 68, where heat is absorbed by the refrigerant evaporated in the refrigerant flow path 64B, The heat carrier is cooled. The heat medium exiting the heat medium flow path 64A of the temperature-controlled target heat exchanger 64 reaches the temperature-controlled target 55 and exchanges heat with the temperature-controlled target 55 to cool it. Then, the heat medium that has exchanged heat with the temperature controlled object 55 is sucked into the circulation pump 62 and repeatedly circulates (indicated by the dashed arrow in FIG. 11).

When the object 55 to be temperature controlled is cooled in this way and its temperature Tw drops below the lower limit value TWL, the air conditioning controller 32 fully closes the auxiliary expansion valve 73 and stops the circulation pump 62 to cool/heat the object. Return from the controlled cooling mode to the cooling mode. In this manner, the temperature Tw of the temperature controlled object 55 (for example, the battery) is maintained at the predetermined target temperature controlled object temperature TWO.

The cooling/temperature-controlled object cooling mode can be set not only during operation in the cooling mode, but also when the vehicle is stopped and the battery (temperature-controlled object 55) is being charged. requested). The flow of the refrigerant in the refrigerant circuit R and the flow of the heat medium in the temperature controlled cooling device 61 remain unchanged. However, in that case, the air conditioning controller 32 controls the rotation speed of the compressor 2 based on the temperature to be adjusted Tw detected by the temperature sensor to be adjusted 76, and the indoor expansion valve 8 based on the heat absorber temperature Te. , the degree of superheat of the refrigerant in the heat absorber 9 is controlled. That is, priority is given to cooling the object to be temperature-controlled in the cooling/temperature-controlled cooling mode during charging, and cooling of the vehicle interior is prioritized in the cooling/temperature-controlled cooling mode during running.

(5-7) Cooling Mode for Temperature Controlled Object Next, referring to FIG. The temperature control target cooling mode will be described. Since the battery generates heat during charging, the air-conditioning controller 32 of the embodiment also sets the target temperature Tw to the target temperature TWO (the target temperature of the battery) with a predetermined hysteresis above and below it. An upper limit value TWH and a lower limit value TWL are set, and when the temperature Tw to be controlled detected by the temperature control target temperature sensor 76 rises to a predetermined upper limit value TWH or higher due to charging, the temperature control target cooling mode is entered. . FIG. 12 shows the flow of the refrigerant in the refrigerant circuit R (solid line arrow) and the flow of the heat medium in the temperature control target cooling device 61 (broken line arrow) in this temperature controlled cooling mode.

In this temperature-controlled cooling mode, the air conditioning controller 32 fully opens the third refrigerant passage 98 by the expansion valve section 6 with the driving device 83 of the composite valve 81, and the first on-off valve section 21 and the second on-off valve section 22 closes the first refrigerant passage 91 and the second refrigerant passage 94 (state shown in FIG. 4). Also, the indoor expansion valve 8 is fully closed (prevents the refrigerant from flowing into the heat absorber 9), and the auxiliary expansion valve 73 is opened to adjust the valve opening degree. Also, the circulation pump 62 is operated.

Then, the compressor 2 and the outdoor fan 15 are operated, and the indoor fan 27 is stopped. As a result, the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 passes through the radiator 4 , the expansion valve portion 6 of the composite valve 81 , and flows into the outdoor heat exchanger 7 . The refrigerant that has flowed into the outdoor heat exchanger 7 is cooled there by the outside air blown by the outdoor fan 15 and condensed. The refrigerant exiting the outdoor heat exchanger 7 flows into the refrigerant pipe 13A and enters the first refrigerant passage 91 from the first refrigerant inlet 88 of the composite valve 81 .

At this time, since the first on-off valve portion 21 and the second on-off valve portion 22 are closed, the refrigerant that has flowed into the first refrigerant passage 91 enters the second refrigerant passage 94 through the communication passage 96 and the check valve 18. , from the second refrigerant outlet 93 into the refrigerant pipe 13B. The refrigerant flowing into the refrigerant pipe 13B flows into the branch pipe 72 and reaches the auxiliary expansion valve 73. After being decompressed by the auxiliary expansion valve 73, the refrigerant flows into the refrigerant flow path 64B of the heat exchanger 64 for temperature control. flows and evaporates.

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

The air conditioning controller 32 adjusts the temperature of the temperature control target 55 (temperature control target temperature Tw) detected by the temperature control target temperature sensor 76 based on the target temperature TWO, which is the target temperature of the temperature control target temperature. The number of revolutions of the compressor 2 is controlled so that Tw (the temperature of the battery in the embodiment) becomes the target temperature to be controlled TWO.

As described in detail above, the composite valve 81 of the present invention includes a housing 82 having a first refrigerant inlet 88, a first refrigerant outlet 89, a second refrigerant inlet 92, a second refrigerant outlet 973, and a third refrigerant outlet 97; A first coolant passage 91 is formed in the housing 82 and extends between a first coolant inlet 88 and a first coolant outlet 89, and a first coolant passage 91 is formed in the housing 82 and extends between a second coolant inlet 92 and a second coolant outlet 93. a second refrigerant passage 94; a second on-off valve portion 22, a third refrigerant passage 98 formed in the housing 82 and extending from a second refrigerant passage 94 on the second refrigerant inlet 92 side of the second on-off valve portion 22 to a third refrigerant outlet 97; The expansion valve portion 6 provided in the third refrigerant passage 98 for adjusting the degree of opening of the third refrigerant passage 98, the expansion valve portion 6 through the actuator 84, the first on-off valve portion 21, and the second on-off valve a first refrigerant passage 91 formed in the housing 82 and closer to the first refrigerant inlet 88 than the first on-off valve portion 21; and a check valve 18 which is provided in the communication path 96 and directed in the direction of the second refrigerant path 94, as in the embodiment. By the driving device 83, the first on-off valve portion 21 and the second on-off valve portion 22 open the first refrigerant passage 91 and the second refrigerant passage 94, and the expansion valve portion 6 changes the opening degree of the third refrigerant passage 98. , the first on-off valve portion 21 and the second on-off valve portion 22 close the first refrigerant passage 91 and the second refrigerant passage 94, and the expansion valve portion 6 opens the third refrigerant passage 98. The refrigerant is connected to the compressor 2 for compressing the refrigerant as in the embodiment, and the refrigerant inlet is connected to the refrigerant pipe 13G on the discharge side of the compressor 2, and the refrigerant is radiated to the vehicle interior. A radiator 4 for heating the air supplied to the vehicle, and a heat absorber 9 whose refrigerant outlet is connected to the refrigerant pipe 13C on the suction side of the compressor 2 and absorbs heat from the refrigerant to cool the air supplied to the vehicle interior. , an outdoor heat exchanger 7 connected to the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4 and provided outside the vehicle, an indoor expansion valve 8 for reducing the pressure of the refrigerant flowing into the heat absorber 9, and an air conditioning controller 32, the refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to the first refrigerant inlet 88 of the composite valve 81, and the refrigerant pipe on the suction side of the compressor 2 13D (cold ) is connected to the first refrigerant outlet 89 of the composite valve 81, the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4 is connected to the second refrigerant inlet 92 of the composite valve 81, and the indoor expansion valve 8 If the refrigerant pipe 13B on the refrigerant inlet side is connected to the second refrigerant outlet 93 of the compound valve 81, and the refrigerant pipe 13J on the refrigerant inlet side of the outdoor heat exchanger 7 is connected to the third refrigerant outlet 97 of the compound valve 81, air conditioning By controlling the driving device 83 of the composite valve 81 by the controller 32, it is possible to switch between the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode as in the embodiment.

Further, as in the embodiment, a temperature-controlled object cooling device 61 is provided for cooling a temperature-controlled object 55 (a battery or a running motor) mounted on a vehicle using a refrigerant. A temperature-controlled target heat exchanger 64 for cooling the temperature-controlled target 55 by causing the refrigerant to absorb heat, and an auxiliary expansion valve 73 for decompressing the refrigerant flowing into the temperature-controlled target heat exchanger 64 are provided. The refrigerant inlet of the temperature-controlled heat exchanger 64 is connected to a branch pipe 72 branched from the refrigerant pipe 13B on the refrigerant inlet side of the indoor expansion valve 8, and the refrigerant outlet of the temperature-controlled heat exchanger 64 is connected to the refrigerant pipe. 74 to the refrigerant pipe 13C on the suction side of the compressor 2, the air conditioning controller 32 controls the driving device 73 of the composite valve 81 to switch between the cooling/temperature-controlled cooling mode and the temperature-controlled cooling mode. It is possible to switch the mode and execute.

In other words, the function of switching the operation mode of the vehicle air conditioner 1, which has conventionally been performed by a plurality of solenoid valves, and the function of depressurizing the refrigerant, which has been performed by the outdoor expansion valve, can be integrated into the composite valve 81. By reducing the number of parts, it is possible to reduce part costs and production costs, and to reduce the installation space.

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

Further, in the embodiment, the housing 82 is composed of a first housing member 86 provided with a first refrigerant inlet 88, a first refrigerant outlet 89, a first refrigerant passage 91, and a first on-off valve portion 21, and a second refrigerant inlet. 92, a second housing member 87 provided with a second refrigerant outlet 93, a second refrigerant passage 94, and a second on-off valve portion 22, a third refrigerant outlet 97, a third refrigerant passage 98, and an expansion valve portion 6 is connected to a third housing member 85, and an actuator 84 is provided over each of the housing members 85, 87, 86 to drive the expansion valve portion 6 and each of the on-off valve portions 21, 22. As a result, the manufacturing/assembling work of the composite valve 81 is also facilitated.

In particular, in the embodiment, the first refrigerant passage 91 on the side of the first refrigerant inlet 88 from the first on-off valve portion 21 is formed in the first housing member 86 so as to be close to one surface of the first housing member 86, and the second opening/closing valve is provided. A second refrigerant passage 94 on the side of the second refrigerant outlet 93 from the valve portion 22 is formed in the second housing member 87 in close proximity to one surface of the second housing member 87 , and the first housing member 86 is provided with a first opening/closing passage. A first communication portion 96</b>A is formed from the first refrigerant passage 91 on the first refrigerant inlet 88 side of the valve portion 21 to one surface of the first housing member 86 . A second communicating portion 96B extending from the second refrigerant passage 94 on the second refrigerant outlet 93 side to one surface of the second housing member 87 is formed, and when the first and second housing members 86 and 87 are joined together, each Communicating portions 96A and 96B are matched to form a communicating passage 96, and the third housing member 85 is connected to the other surface of the second housing member 87, so that a short communicating passage 96 can be easily constructed. In addition, the check valve 18 can be easily attached, and the third housing member 85 can be connected without any trouble.

The configuration of the compound valve 81 and the configuration of the vehicle air conditioner 1 described in the embodiment are not limited to them, and can be changed within the scope of the present invention. In addition, in the embodiment, the indoor expansion valve 8 and the auxiliary expansion valve 73 are configured by electric valves, and are fully closed to prevent the refrigerant from flowing into the heat absorber 9 and the heat exchanger 64 for temperature control object. Alternatively, the indoor expansion valve 8 and the auxiliary expansion valve 73 may be mechanical expansion valves, and solenoid valves may be connected in series to block the inflow of refrigerant.

Furthermore, in the embodiment, the temperature controlled object cooling device 61 that cools the temperature controlled object 55 with the refrigerant through the heat medium is adopted. The temperature control target 55 may be directly cooled. Furthermore, in the embodiments, the composite valve of the present invention is applied to an air conditioner for vehicles, but it is needless to say that it can be applied to various devices having a refrigerant circuit.

1 vehicle air conditioner 2 compressor 4 radiator 6 expansion valve section 7 outdoor heat exchanger 8 indoor expansion valve 9 heat absorber 18 check valve 21 first on-off valve section 22 second on-off valve section 32 air conditioning controller (control device )
55 temperature controlled target 61 temperature controlled target cooling device 62 circulation pump 64 temperature controlled target heat exchanger 72 branch pipe 73 auxiliary expansion valve 81 compound valve 82 housing 83 drive device 84 actuator 85 third housing member 86 first housing Member 87 Second housing member 88 First refrigerant inlet 89 First refrigerant outlet 91 First refrigerant passage 92 Second refrigerant inlet 93 Second refrigerant outlet 94 Second refrigerant passage 96 Communication passage 96A First communication portion 96B Second communication portion 97 Third refrigerant outlet 98 Third refrigerant passage

Claims (8)

A composite valve applied to a refrigerant circuit,
a housing having a first coolant inlet, a first coolant outlet, a second coolant inlet, a second coolant outlet, and a third coolant outlet;
a first coolant passage formed in the housing and extending between the first coolant inlet and the first coolant outlet;
a second coolant passage formed in the housing and extending between the second coolant inlet and the second coolant outlet;
a first on-off valve portion provided in the first refrigerant passage for opening and closing the first refrigerant passage;
a second on-off valve portion provided in the second refrigerant passage for opening and closing the second refrigerant passage;
a third refrigerant passage formed in the housing and extending from the second refrigerant passage on the second refrigerant inlet side of the second on-off valve portion to the third refrigerant outlet;
an expansion valve portion provided in the third refrigerant passage for adjusting the degree of opening of the third refrigerant passage;
a driving device that drives the expansion valve portion, the first opening/closing valve portion, and the second opening/closing valve portion via actuators;
The first refrigerant passage formed in the housing on the first refrigerant inlet side of the first on-off valve portion communicates with the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion. a communicating passage to
A composite valve, comprising: a check valve provided in the communication passage and having a forward direction in the direction of the second refrigerant passage. By the driving device,
a state in which the first on-off valve portion and the second on-off valve portion open the first refrigerant passage and the second refrigerant passage, and the expansion valve portion adjusts the degree of opening of the third refrigerant passage;
The first on-off valve portion and the second on-off valve portion close the first refrigerant passage and the second refrigerant passage, and the expansion valve portion adjusts the degree of opening of the third refrigerant passage. The composite valve according to claim 1, characterized by: The first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion and the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion are formed adjacent to each other in the housing. 3. The composite valve according to claim 1 or 2, wherein the composite valve is The housing is
a first housing member provided with the first refrigerant inlet, the first refrigerant outlet, the first refrigerant passage, and the first on-off valve portion;
a second housing member provided with the second refrigerant inlet, the second refrigerant outlet, the second refrigerant passage, and the second on-off valve portion;
a third housing member provided with the third refrigerant outlet, the third refrigerant passage, and the expansion valve portion;
4. The composite valve according to any one of claims 1 to 3, wherein the actuator is provided over each of the housing members and drives the expansion valve section and the opening and closing valve sections. the first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion is formed in the first housing member in close proximity to one surface of the first housing member;
The second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion is formed in the second housing member in proximity to one surface of the second housing member,
The first housing member has a first communication portion extending from the first refrigerant passage on the first refrigerant inlet side of the first on-off valve portion to one surface of the first housing member,
The second housing member has a second communication portion extending from the second refrigerant passage on the second refrigerant outlet side of the second on-off valve portion to one surface of the second housing member,
The first and second housing members are joined together at their one surfaces, and in this state, the respective communicating portions are matched to form the communicating passages, and the third housing member is the second housing member. 5. The composite valve of claim 4, wherein the composite valve is bonded to a face. a compressor that compresses a refrigerant;
a radiator, the refrigerant inlet of which is connected to a refrigerant pipe on the discharge side of the compressor, for radiating the refrigerant to heat the air supplied to the passenger compartment;
a heat absorber having a refrigerant outlet connected to a refrigerant pipe on the suction side of the compressor and absorbing heat from the refrigerant to cool the air supplied to the passenger compartment;
an outdoor heat exchanger connected to the refrigerant pipe on the refrigerant outlet side of the radiator and provided outside the vehicle;
an indoor expansion valve for decompressing the refrigerant flowing into the heat absorber;
with a control device,
A refrigerant pipe on the refrigerant outlet side of the outdoor heat exchanger is connected to the first refrigerant inlet of the composite valve,
A refrigerant pipe on the suction side of the compressor is connected to the first refrigerant outlet of the composite valve,
A refrigerant pipe on the refrigerant outlet side of the radiator is connected to the second refrigerant inlet of the composite valve,
A refrigerant pipe on the refrigerant inlet side of the indoor expansion valve is connected to the second refrigerant outlet of the composite valve,
A refrigerant pipe on the refrigerant inlet side of the outdoor heat exchanger is connected to the third refrigerant outlet of the composite valve,
6. A vehicle air conditioner using a composite valve according to any one of claims 1 to 5, wherein said control device controls a drive device for said composite valve. By controlling the driving device of the composite valve, the control device
The first on-off valve portion and the second on-off valve portion of the composite valve open the first refrigerant passage and the second refrigerant passage, and the expansion valve portion adjusts the degree of opening of the third refrigerant passage. state, the refrigerant discharged from the compressor is prevented from flowing into the heat absorber, the refrigerant discharged from the compressor is radiated by the radiator, and the heat-dissipated refrigerant is decompressed by the expansion valve portion, and then the outdoor heat is A heating mode that absorbs heat with an exchanger,
The first on-off valve portion and the second on-off valve portion of the composite valve open the first refrigerant passage and the second refrigerant passage, and the expansion valve portion adjusts the degree of opening of the third refrigerant passage. state, the refrigerant discharged from the compressor is radiated by the radiator, part of the radiated refrigerant is flowed to the indoor expansion valve through the second on-off valve portion, and the pressure is reduced by the indoor expansion valve. After that, a dehumidifying heating mode in which heat is absorbed by the heat absorber, the rest of the heat-dissipated refrigerant is decompressed by the expansion valve portion, and heat is absorbed by the outdoor heat exchanger ;
The first on-off valve portion and the second on-off valve portion of the composite valve close the first refrigerant passage and the second refrigerant passage, and the expansion valve portion adjusts the degree of opening of the third refrigerant passage. state, the refrigerant discharged from the compressor is radiated by the radiator and the outdoor heat exchanger, the radiated refrigerant is flowed to the indoor expansion valve through the check valve of the composite valve, and the indoor expansion valve A dehumidifying cooling mode in which the heat absorber absorbs heat after decompressing with
With the first on-off valve portion and the second on-off valve portion of the composite valve closing the first refrigerant passage and the second refrigerant passage, the refrigerant discharged from the compressor is subjected to the outdoor heat exchange. A cooling mode in which the heat is radiated by the device, the radiated refrigerant is flowed to the indoor expansion valve through the check valve of the composite valve, the pressure is reduced by the indoor expansion valve, and the heat is absorbed by the heat absorber;
7. The air conditioner for a vehicle according to claim 6, wherein the operation is performed by switching between . Equipped with a temperature control object cooling device that cools a temperature control object mounted on a vehicle using a refrigerant,
The temperature controlled target cooling device includes a temperature controlled target heat exchanger for absorbing heat from a refrigerant to cool the temperature controlled target, and decompressing the refrigerant flowing into the temperature controlled target heat exchanger. An auxiliary expansion valve is provided, the refrigerant inlet of the heat exchanger for temperature control target is connected to a branch pipe branched from a refrigerant pipe on the refrigerant inlet side of the indoor expansion valve, and the heat exchanger for temperature control target is connected to a branch pipe. A refrigerant outlet is connected to a refrigerant pipe on the suction side of the compressor,
By controlling the driving device of the composite valve, the control device
With the first on-off valve portion and the second on-off valve portion of the composite valve closing the first refrigerant passage and the second refrigerant passage, the refrigerant discharged from the compressor is subjected to the outdoor heat exchange. , the heat-dissipated refrigerant flows through the check valve of the composite valve to the indoor expansion valve and the auxiliary expansion valve, is decompressed by the indoor expansion valve, absorbs heat in the heat absorber, A cooling/temperature-controlled target cooling mode in which heat is absorbed by the temperature-controlled target heat exchanger after the pressure is reduced by the expansion valve;
In a state in which the first refrigerant passage and the second refrigerant passage are closed by the first on-off valve portion and the second on-off valve portion of the composite valve, the refrigerant is prevented from flowing into the heat absorber, Refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, the radiated refrigerant flows through the check valve of the composite valve to the auxiliary expansion valve, is decompressed by the auxiliary expansion valve, and is then heated. a temperature control target cooling mode in which heat is absorbed by the control target heat exchanger;
8. The air conditioner for a vehicle according to claim 6, wherein the operation is performed by switching between .

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