JP7516761B2 - Refrigeration Cycle Equipment - Google Patents

Description

The present invention relates to a refrigeration cycle device configured to be able to switch refrigerant circuits.

Conventionally, Patent Document 1 discloses a refrigeration cycle device configured to be able to switch between refrigerant circuits that circulate refrigerant. The refrigeration cycle device of Patent Document 1 is applied to a vehicle air conditioning system. The refrigeration cycle device of Patent Document 1 is configured to be able to switch between a refrigerant circuit in a heating mode that heats the blown air and blows it into the vehicle cabin, and a refrigerant circuit in a cooling mode that cools the blown air and blows it into the vehicle cabin.

Furthermore, the refrigeration cycle device of Patent Document 1 is equipped with an accumulator. The accumulator is disposed in a refrigerant flow path extending from the refrigerant outlet side of the heat exchanger, which functions as an evaporator that evaporates the refrigerant, to the suction side of the compressor, and is a low-pressure side liquid storage section that stores excess refrigerant in the cycle as liquid-phase refrigerant. As a result, the refrigeration cycle device of Patent Document 1 circulates an appropriate flow rate of refrigerant even if the amount of excess refrigerant changes when switching operating modes, etc.

JP 2012-225637 A

However, in a refrigeration cycle device equipped with an accumulator, as in Patent Document 1, it is difficult to improve the coefficient of performance (COP) of the cycle. In other words, in a refrigeration cycle device equipped with an accumulator, it is difficult to improve the cooling capacity of the blown air.

The reason for this is that in a refrigeration cycle device equipped with an accumulator, the state of the refrigerant flowing out of the heat exchanger functioning as an evaporator approaches saturated gas-phase refrigerant, making it difficult to increase the amount of heat absorbed by the refrigerant in the heat exchanger functioning as an evaporator.

In view of the above, the present invention aims to provide a refrigeration cycle device that is configured to be able to switch refrigerant circuits and improve the coefficient of performance.

In order to achieve the above object, a refrigeration cycle device according to a first aspect of the present invention includes a compressor (11) that compresses and discharges a refrigerant, a heat dissipation section (12, 62) that dissipates heat from the refrigerant discharged from the compressor, a liquid storage section (15) that accumulates surplus refrigerant in the cycle, a first pressure reduction section (16a) that reduces the pressure of the refrigerant, an outdoor heat exchanger (18) that exchanges heat between the refrigerant flowing out of the first pressure reduction section and outside air, a second pressure reduction section (16b to 16d) that reduces the pressure of the refrigerant, an evaporation section (19, 19a, 30a, 72) that evaporates the refrigerant reduced in pressure by the second pressure reduction section, and a refrigerant circuit switching section (14a to 14c) that switches a refrigerant circuit,
The refrigerant circuit switching unit is configured to be capable of switching between a first circuit that causes the refrigerant flowing out of the heat dissipation unit to flow into the liquid storage unit, the refrigerant flowing out of the liquid storage unit to flow into the first pressure reduction unit, and the refrigerant depressurized by the first pressure reduction unit to flow into the outdoor heat exchanger, and a second circuit that causes the refrigerant flowing out of the outdoor heat exchanger to flow into the liquid storage unit, the refrigerant flowing out of the liquid storage unit to flow into the second pressure reduction unit, and the refrigerant depressurized by the second pressure reduction unit to flow into the evaporation unit.
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit so that the flow direction of the refrigerant in the outdoor heat exchanger when switched to the first circuit coincides with the flow direction of the refrigerant in the outdoor heat exchanger when switched to the second circuit.
The refrigerant circuit switching unit has a first switching unit (22a) that guides the refrigerant discharged from the compressor to at least one of the liquid storage unit side and the outdoor heat exchanger side, a joint unit (13b) that guides at least one of the refrigerant flowing out of the first switching unit and the refrigerant flowing out of the liquid storage unit to the outdoor heat exchanger side, and a second switching unit (22b) that guides the refrigerant flowing out of the outdoor heat exchanger to at least one of the suction port side and the liquid storage unit side of the compressor. The first pressure reduction unit and the second switching unit are integrated to enable heat exchange between the refrigerant flowing into the first pressure reduction unit and the refrigerant guided from the second switching unit to the suction port side of the compressor.

As a result, the refrigerant circuit switching unit (14a to 14c) is provided, making it possible to switch between the first circuit and the second circuit.

When switching to the first circuit, the refrigerant decompressed in the first decompression section (16a) can be evaporated in the outdoor heat exchanger (18). At this time, the high-pressure liquid-phase refrigerant condensed in the heat dissipation section (12, 62) can be stored in the liquid storage section (15) as surplus refrigerant. Therefore, the refrigerant on the outlet side of the outdoor heat exchanger (18) can be superheated.

When switching to the second circuit, the refrigerant depressurized in the second pressure reduction section (16b to 16d) can be evaporated in the evaporation section (19...72). At this time, the high-pressure liquid phase refrigerant condensed in the outdoor heat exchanger (18) can be stored in the liquid storage section (15) as surplus refrigerant. Therefore, the refrigerant on the outlet side of the evaporation section (19...72) can be given a degree of superheat.

In other words, according to the refrigeration cycle device described in claim 1, when switching to any of the refrigerant circuits, the refrigerant on the outlet side of the outdoor heat exchanger (18) or the evaporation section (19...72) functioning as an evaporator can be made to have a degree of superheat. This makes it possible to increase the amount of heat absorbed by the refrigerant in the outdoor heat exchanger (18) or the evaporation section (19...72) functioning as an evaporator.

As a result, it is possible to provide a refrigeration cycle device capable of improving the coefficient of performance even if the refrigerant circuit is configured to be switchable.
A refrigeration cycle device according to a third aspect of the present invention includes a compressor (11) that compresses and discharges a refrigerant, a heat dissipation section (12, 62) that dissipates heat from the refrigerant discharged from the compressor, a liquid storage section (15) that stores surplus refrigerant in the cycle, a first pressure reduction section (16a) that reduces the pressure of the refrigerant, an outdoor heat exchanger (18) that exchanges heat between the refrigerant flowing out of the first pressure reduction section and outside air, a second pressure reduction section (16b-16d) that reduces the pressure of the refrigerant, an evaporation section (19, 19a, 30a, 72) that evaporates the refrigerant reduced in pressure by the second pressure reduction section, a refrigerant circuit switching section (14a-14c) that switches a refrigerant circuit, and a liquid storage section side pressure reduction section ( 23a ) that reduces the pressure of the refrigerant flowing into the liquid storage section to thereby reduce the enthalpy of the refrigerant in the liquid storage section,
The refrigerant circuit switching unit is configured to be capable of switching between a first circuit, which causes the refrigerant discharged from the compressor to flow into the heat radiating unit, causes the refrigerant flowing out from the heat radiating unit to flow into the liquid storage unit side pressure reducing unit, causes the refrigerant depressurized by the liquid storage unit side pressure reducing unit to flow into the liquid storage unit, causes the refrigerant flowing out from the liquid storage unit to flow into the first pressure reducing unit, and causes the refrigerant depressurized by the first pressure reducing unit to flow into the outdoor heat exchanger, and a second circuit, which causes the refrigerant discharged from the compressor to flow into the outdoor heat exchanger, causes the refrigerant flowing out from the outdoor heat exchanger to flow into the liquid storage unit side pressure reducing unit, causes the refrigerant depressurized by the liquid storage unit side pressure reducing unit to flow into the liquid storage unit, causes the refrigerant flowing out from the liquid storage unit to flow into the second pressure reducing unit, and causes the refrigerant depressurized by the second pressure reducing unit to flow into the evaporation unit.
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit so that the flow direction of the refrigerant in the outdoor heat exchanger when switched to the first circuit coincides with the flow direction of the refrigerant in the outdoor heat exchanger when switched to the second circuit, and switches the refrigerant circuit so that the flow direction of the refrigerant in the liquid storage section side pressure reduction section when switched to the first circuit coincides with the flow direction of the refrigerant in the liquid storage section side pressure reduction section when switched to the second circuit.
The reservoir-side pressure reducing section reduces the pressure of the refrigerant flowing into the reservoir regardless of whether the refrigerant circuit switching section is switching to the first circuit or the second circuit.
According to this, the same effect as that of the invention described in claim 1 can be obtained.

A refrigeration cycle device according to a twelfth aspect of the present invention includes a compressor (111) having a suction port (111a) for sucking a low-pressure refrigerant, an intermediate-pressure suction port (111b) for sucking an intermediate-pressure refrigerant, and a discharge port (111c) for discharging a compressed refrigerant, a heat dissipation section (12, 62) for dissipating heat from the refrigerant discharged from the discharge port, a liquid storage section (15) for storing surplus refrigerant in the cycle, a first pressure reduction section (16a) for reducing the pressure of the refrigerant, and a discharge port (111c) for discharging the refrigerant flowing out of the first pressure reduction section. the refrigerant circulation system includes an outdoor heat exchanger (18) for exchanging heat with outside air, a second pressure reduction section (16b-16d) for reducing the pressure of a refrigerant, an evaporation section (19, 19a, 30a, 72) for evaporating the refrigerant reduced in pressure by the second pressure reduction section, a third pressure reduction section (16e) for reducing the pressure of at least a portion of either the refrigerant on the upstream side of the liquid storage section or the refrigerant flowing out of the liquid storage section, and causing the refrigerant to flow out to an intermediate pressure suction port side, and a refrigerant circuit switching section (14a-14d) for switching a refrigerant circuit;
The refrigerant circuit switching unit is configured to be able to switch between a first circuit that allows the refrigerant flowing out of the heat dissipation unit to flow into the liquid storage unit, allows the refrigerant flowing out of the liquid storage unit to flow into the first pressure reduction unit, and allows the refrigerant depressurized by the first pressure reduction unit to flow into the outdoor heat exchanger, and a second circuit that allows the refrigerant flowing out of the outdoor heat exchanger to flow into the liquid storage unit, allows the refrigerant flowing out of the liquid storage unit to flow into the second pressure reduction unit, and allows the refrigerant depressurized by the second pressure reduction unit to flow into the evaporation unit,
the refrigerant circuit switching unit, when switching to at least one of the first circuit and the second circuit, switches to a refrigerant circuit that draws the refrigerant decompressed by the third decompression unit through the intermediate pressure suction port;
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit so that the flow direction of the refrigerant in the outdoor heat exchanger when switched to the first circuit coincides with the flow direction of the refrigerant in the outdoor heat exchanger when switched to the second circuit.
The refrigerant circuit switching unit has a first switching unit (22a) that guides the refrigerant discharged from the compressor to at least one of the liquid storage unit side and the outdoor heat exchanger side, a joint unit (13b) that guides at least one of the refrigerant flowing out of the first switching unit and the refrigerant flowing out of the liquid storage unit to the outdoor heat exchanger side, and a second switching unit (22b) that guides the refrigerant flowing out of the outdoor heat exchanger to at least one of the suction port side of the compressor and the liquid storage unit side,
The first pressure reducing section and the second switching section are integrated to enable heat exchange between the refrigerant flowing into the first pressure reducing section and the refrigerant guided from the second switching section to the suction port side of the compressor.

According to this, since the refrigerant circuit switching unit (14a to 14d) is provided, it is possible to switch between the first circuit and the second circuit, as in the invention described in claim 1. When switching to the first circuit, it is possible to provide superheat to the refrigerant on the outlet side of the outdoor heat exchanger (18) functioning as an evaporator. Also, when switching to the second circuit, it is possible to provide superheat to the refrigerant on the outlet side of the evaporation unit (19...72) functioning as an evaporator.

In other words, according to the refrigeration cycle device described in claim 12, when switching to any of the refrigerant circuits, the refrigerant on the outlet side of the outdoor heat exchanger (18) or the evaporation section (19...72) functioning as an evaporator can be made to have a degree of superheat. This makes it possible to increase the amount of heat absorbed by the refrigerant in the outdoor heat exchanger (18) or the evaporation section (19...72) functioning as an evaporator.

As a result, it is possible to provide a refrigeration cycle device that can improve the coefficient of performance even if the refrigerant circuit is configured to be switchable.

Furthermore, when switching to at least one of the first and second circuits, the refrigerant decompressed in the third decompression section (16e) is drawn through the intermediate pressure intake port (111b) of the compressor (111). This allows a so-called gas injection cycle to be configured, further improving the coefficient of performance.

Note that the symbols in parentheses for each means described in this section and in the claims indicate the corresponding relationship with the specific means described in the embodiments described below.

1 is an overall configuration diagram of a refrigeration cycle device according to a first embodiment; FIG. 1 is a schematic configuration diagram of an indoor air conditioning unit according to a first embodiment. 2 is a block diagram showing an electric control unit of the vehicle air conditioner according to the first embodiment; FIG. FIG. 6 is an overall configuration diagram of a refrigeration cycle device according to a second embodiment. FIG. 11 is an overall configuration diagram of a refrigeration cycle device according to a third embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a fourth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a fifth embodiment. FIG. 13 is a Mollier diagram showing a change in state of a refrigerant in a refrigeration cycle device of a fifth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a modified example of the fifth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to another modified example of the fifth embodiment. FIG. 13 is a schematic cross-sectional view of an integrated valve according to a sixth embodiment. FIG. 13 is a Mollier diagram showing a change in state of a refrigerant in a refrigeration cycle device of a sixth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a seventh embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to an eighth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a ninth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device according to a modified example of the ninth embodiment. FIG. 13 is an overall configuration diagram of a refrigeration cycle device of another modified example of the ninth embodiment. FIG. 19 is an overall configuration diagram of a refrigeration cycle device according to a tenth embodiment. FIG. 19 is an overall configuration diagram of a refrigeration cycle device according to an eleventh embodiment. FIG. 23 is an overall configuration diagram of a refrigeration cycle device according to a twelfth embodiment. FIG. 23 is an overall configuration diagram of a refrigeration cycle device according to a thirteenth embodiment. FIG. 23 is an overall configuration diagram of a refrigeration cycle device according to a fourteenth embodiment. FIG. 23 is an overall configuration diagram of a refrigeration cycle device according to a fifteenth embodiment. FIG. 23 is an overall configuration diagram of a refrigeration cycle device according to a sixteenth embodiment. FIG. 11 is an overall configuration diagram of a refrigeration cycle device according to another embodiment. FIG. 11 is an overall configuration diagram of a refrigeration cycle device including a four-way joint according to another embodiment. FIG. 11 is an explanatory diagram for explaining a heat exchange mode of an internal heat exchanger in a refrigeration cycle device according to another embodiment.

Below, several embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment will be given the same reference numerals, and duplicated explanations may be omitted. In cases where only a portion of the configuration is described in each embodiment, other previously described embodiments may be applied to the other portions of the configuration. In addition to combinations of parts that are specifically specified as being possible in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

First Embodiment
A first embodiment of a refrigeration cycle device 10 according to the present invention will be described with reference to Figures 1 to 3. The refrigeration cycle device 10 is applied to a vehicle air conditioner mounted on an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The vehicle air conditioner of this embodiment is an air conditioner that conditions the interior of the vehicle cabin, which is a space to be air-conditioned, in the electric vehicle, and has an in-vehicle equipment cooling function that cools a battery 30, which is an in-vehicle equipment.

The refrigeration cycle device 10 cools or heats the ventilation air that is blown into the vehicle cabin in a vehicle air conditioner. Furthermore, the refrigeration cycle device 10 cools the battery 30. Therefore, the objects to be temperature-adjusted by the refrigeration cycle device 10 are the ventilation air and the battery 30. Furthermore, the refrigeration cycle device 10 is configured to be able to switch the refrigerant circuit in order to condition the air in the vehicle cabin and cool the battery 30.

The refrigeration cycle device 10 uses an HFO refrigerant (specifically, R1234yf) as the refrigerant. The refrigeration cycle device 10 configures a vapor compression subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. The refrigerant is mixed with refrigeration oil (specifically, PAG oil) to lubricate the compressor 11. A portion of the refrigeration oil circulates through the cycle together with the refrigerant.

The compressor 11 in the refrigeration cycle device 10 draws in, compresses, and discharges the refrigerant. The compressor 11 is disposed in a drive unit room at the front of the vehicle cabin. The drive unit room forms a space in which at least a part of a drive unit (e.g., an electric motor) for outputting driving force for traveling is disposed.

The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-capacity compression mechanism with a fixed discharge capacity. The rotation speed (i.e., the refrigerant discharge pressure) of the compressor 11 is controlled by a control signal output from the control device 50, which will be described later.

The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11. The indoor condenser 12 is arranged inside the casing 41 of the indoor air conditioning unit 40 described later. The indoor condenser 12 is a heat dissipation section that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air, causing the high-pressure refrigerant to dissipate heat. In other words, the indoor condenser 12 is a heating section that heats the blown air using the high-pressure refrigerant discharged from the compressor 11 as a heat source.

The refrigerant outlet of the indoor condenser 12 is connected to the inlet side of a first three-way joint 13a, which has three inlet and outlet ports that communicate with each other. Such a three-way joint can be formed by joining multiple pipes, or by providing multiple refrigerant passages in a metal block or resin block.

Furthermore, the refrigeration cycle device 10 includes a second three-way joint 13b to an eighth three-way joint 13h, as described below. The basic configurations of the second three-way joint 13b to the eighth three-way joint 13h are all the same as the first three-way joint 13a.

When one of the three inlet/outlets is used as an inlet and two are used as outlets, the first three-way joints 13a to the eighth three-way joints 13h can function as a branching section that branches the flow of refrigerant that has flowed in from one inlet. When two of the three inlet/outlets are used as inlets and one is used as an outlet, the first three-way joints 13a to the eighth three-way joints 13h can function as a merging section that merges the flow of refrigerant that has flowed in from the two inlets.

In this embodiment, the first three-way joint 13a, the third three-way joint 13c, the sixth three-way joint 13f, and the seventh three-way joint 13g are connected so as to function as a branching section. Also, the second three-way joint 13b, the fourth three-way joint 13d, the fifth three-way joint 13e, and the eighth three-way joint 13h are connected so as to function as a merging section.

One outlet of the first three-way joint 13a is connected to the inlet side of the receiver 15 via the first on-off valve 14a and the fifth three-way joint 13e. The other outlet of the first three-way joint 13a is connected to the inlet side of the heating expansion valve 16a via the second on-off valve 14b and the second three-way joint 13b.

The first on-off valve 14a is an electromagnetic valve that opens and closes the inlet side passage 21a that runs from one outlet of the first three-way joint 13a to the inlet of the receiver 15. The opening and closing operation of the first on-off valve 14a is controlled by a control voltage output from the control device 50. Furthermore, the refrigeration cycle device 10 is equipped with a third on-off valve 14c, as described below. The basic configurations of the second on-off valve 14b and the third on-off valve 14c are the same as that of the first on-off valve 14a.

The fifth three-way joint 13e is connected at one inlet to the outlet side of the first opening/closing valve 14a in the inlet side passage 21a. Furthermore, the fifth three-way joint 13e is connected at one outlet to the inlet side of the receiver 15 in the inlet side passage 21a.

The receiver 15 is a liquid storage section that has a gas-liquid separation function. That is, the receiver 15 separates the gas and liquid of the refrigerant that flows out of the heat exchange section that functions as a condenser that condenses the refrigerant in the refrigeration cycle device 10. The receiver 15 then allows a portion of the separated liquid-phase refrigerant to flow downstream, and stores the remaining liquid-phase refrigerant as surplus refrigerant in the cycle.

The second opening/closing valve 14b is an electromagnetic valve that opens and closes the outside air side passage 21c that runs from the other outlet of the first three-way joint 13a to one inlet of the second three-way joint 13b. The other inlet of the second three-way joint 13b is connected to the outlet side of the receiver 15. The sixth three-way joint 13f and the first check valve 17a are arranged in the outlet side passage 21b that connects the outlet of the receiver 15 and the other inlet of the second three-way joint 13b.

The sixth three-way joint 13f has an inlet connected to the outlet side of the receiver 15 in the outlet side passage 21b. One outlet of the sixth three-way joint 13f is connected to the inlet side of the first check valve 17a in the outlet side passage 21b. Furthermore, the other outlet of the sixth three-way joint 13f is connected to the inlet side of the seventh three-way joint 13g.

The outlet of the second three-way joint 13b is connected to the refrigerant inlet side of the outdoor heat exchanger 18 via the heating expansion valve 16a. Therefore, the first check valve 17a arranged in the outlet passage 21b allows the refrigerant to flow from the outlet side of the receiver 15 to the heating expansion valve 16a side, and prohibits the refrigerant from flowing from the heating expansion valve 16a side to the outlet side of the receiver 15.

The heating expansion valve 16a is a first pressure reducing section that reduces the pressure of the refrigerant flowing out of the receiver 15 and adjusts the flow rate of the refrigerant flowing downstream at least when the refrigerant circuit is switched to the outdoor air heating mode described below.

The heating expansion valve 16a is an electrically operated variable throttle mechanism having a valve body configured to change the throttle opening and an electrically operated actuator (specifically, a stepping motor) that displaces the valve body. The operation of the heating expansion valve 16a is controlled by a control signal (specifically, a control pulse) output from the control device 50.

The heating expansion valve 16a has a fully open function that functions simply as a refrigerant passage with almost no flow rate adjustment or refrigerant pressure reduction effect when the valve is fully open, and a fully closed function that blocks the refrigerant passage when the valve is fully closed.

The refrigeration cycle device 10 further includes a cooling expansion valve 16b and a cooling expansion valve 16c, as described below. The basic configuration of the cooling expansion valve 16b and the cooling expansion valve 16c is the same as that of the heating expansion valve 16a. Of course, the heating expansion valve 16a, etc. may be formed by combining a variable throttle mechanism that does not have a full closing function with an opening and closing valve.

The exterior heat exchanger 18 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 16a and the outside air blown by an outside air fan (not shown). The exterior heat exchanger 18 is disposed at the front side of the drive unit compartment. Therefore, when the vehicle is traveling, the traveling wind can be applied to the exterior heat exchanger 18.

The inlet side of the third three-way joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 18. One of the outlets of the third three-way joint 13c is connected to one of the inlet sides of the fourth three-way joint 13d via the third opening/closing valve 14c. The other of the outlets of the third three-way joint 13c is connected to the other inlet side of the fifth three-way joint 13e via the second check valve 17b.

The third on-off valve 14c is a solenoid valve that opens and closes the suction side passage 21d that runs from one outlet of the third three-way joint 13c to one inlet of the fourth three-way joint 13d. The outlet of the fourth three-way joint 13d is connected to the suction side of the compressor 11. The second check valve 17b allows the refrigerant to flow from the refrigerant outlet side of the outdoor heat exchanger 18 to the inlet side of the receiver 15, and prohibits the refrigerant from flowing from the inlet side of the receiver 15 to the refrigerant outlet side of the outdoor heat exchanger 18.

As described above, the other outlet of the sixth three-way joint 13f arranged in the outlet passage 21b is connected to the inlet side of the seventh three-way joint 13g. One outlet of the seventh three-way joint 13g is connected to the inlet side of the cooling expansion valve 16b. The other outlet of the seventh three-way joint 13g is connected to the inlet side of the cooling expansion valve 16c.

The cooling expansion valve 16b is a second pressure reducing section that reduces the pressure of the refrigerant flowing out of the receiver 15 and adjusts the flow rate of the refrigerant flowing downstream at least when the refrigerant circuit is switched to the cooling mode described below.

The outlet of the cooling expansion valve 16b is connected to the refrigerant inlet side of the indoor evaporator 19. The indoor evaporator 19 is arranged in the casing 41 of the indoor air conditioning unit 40. The indoor evaporator 19 is an evaporation section that evaporates the low-pressure refrigerant decompressed by the cooling expansion valve 16b by heat exchange with the blown air blown from the indoor blower 42. The indoor evaporator 19 is a blown air cooling section that cools the blown air by evaporating the low-pressure refrigerant and exerting a heat absorption effect. One of the inlets of the eighth three-way joint 13h is connected to the refrigerant outlet of the indoor evaporator 19.

The cooling expansion valve 16c is a second pressure reducing section that reduces the pressure of the refrigerant flowing out of the receiver 15 when cooling the battery 30, and adjusts the flow rate of the refrigerant flowing downstream. The outlet of the cooling expansion valve 16c is connected to the inlet side of the refrigerant passage 30a of the battery 30.

Battery 30 supplies power to on-board electric devices such as an electric motor. Battery 30 is a battery pack formed by electrically connecting multiple battery cells in series or parallel. The battery cells are secondary batteries (lithium ion batteries in this embodiment) that can be charged and discharged. Battery 30 is made up of multiple battery cells stacked in a roughly rectangular parallelepiped shape and housed in a dedicated case.

When the temperature of this type of battery is low, the chemical reaction does not proceed easily and the output is easily reduced. The battery generates heat during operation (i.e., charging and discharging). Furthermore, when the temperature of the battery is high, the battery is easily deteriorated. For this reason, it is desirable to maintain the battery temperature within an appropriate temperature range (in this embodiment, 15°C or higher and 55°C or lower) that allows the battery's charging and discharging capacity to be fully utilized.

The refrigerant passage 30a of the battery 30 is formed in a dedicated case for the battery 30. The refrigerant passage 30a is an evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 16c and the battery 30, and evaporates the low-pressure refrigerant. In other words, the refrigerant passage 30a is a so-called direct-cooling type battery cooling section that cools the battery 30 by having the low-pressure refrigerant absorb the heat of the battery 30 (i.e., the waste heat of the battery 30).

The refrigerant passage 30a has a passage configuration in which multiple passages are connected in parallel inside a dedicated case. This allows the refrigerant passage 30a to absorb the waste heat of the battery 30 evenly from the entire area of the battery 30. In other words, the refrigerant passage 30a is configured to absorb the heat of all battery cells evenly and cool all battery cells evenly.

The other inlet of the eighth three-way joint 13h is connected to the outlet of the refrigerant passage 30a of the battery 30. The outlet of the eighth three-way joint 13h is connected to the suction side of the compressor 11 via the fourth three-way joint 13d.

As is clear from the above description, in the refrigeration cycle device 10, the first on-off valve 14a, the second on-off valve 14b, and the third on-off valve 14c open and close the refrigerant passage, thereby switching the refrigerant circuit. Therefore, the first on-off valve 14a, the second on-off valve 14b, the third on-off valve 14c, etc. are included in the refrigerant circuit switching unit.

The first on-off valve 14a, the second on-off valve 14b, and the first three-way joint 13a constitute a first switching unit 22a of the refrigerant circuit switching unit that guides the refrigerant discharged from the compressor 11 to one of the receiver 15 side and the outdoor heat exchanger 18 side. More specifically, in this embodiment, the first switching unit 22a guides the refrigerant flowing out from the indoor condenser 12 to one of the receiver 15 side and the second three-way joint 13b side.

The second three-way joint 13b also forms a joint part of the refrigerant circuit switching part that guides at least one of the refrigerant flowing out of the first three-way joint 13a and the refrigerant flowing out of the receiver 15 to the outdoor heat exchanger 18. More specifically, the joint part of this embodiment guides either the refrigerant flowing out of the first three-way joint 13a or the refrigerant flowing out of the receiver 15 to the heating expansion valve 16a.

The third on-off valve 14c and the third three-way joint 13c form the second switching section 22b of the refrigerant circuit switching section, which directs the refrigerant flowing out from the outdoor heat exchanger 18 to one of the suction side of the compressor 11 and the receiver 15 side.

Next, the interior air conditioning unit 40 will be described with reference to FIG. 2. The interior air conditioning unit 40 is a unit in a vehicle air conditioning system that blows out appropriately temperature-controlled ventilation air to appropriate locations within the vehicle cabin. The interior air conditioning unit 40 is located inside the instrument panel at the very front of the vehicle cabin.

The indoor air conditioning unit 40 has a casing 41 that forms an air passage for the blown air. An indoor blower 42, an indoor evaporator 19, an indoor condenser 12, etc. are arranged in the air passage formed in the casing 41. The casing 41 is formed from a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

An inside/outside air switching device 43 is disposed on the most upstream side of the blown air flow of the casing 41. The inside/outside air switching device 43 switches between introducing inside air (air inside the vehicle cabin) and outside air (air outside the vehicle cabin) into the casing 41. The operation of the electric actuator for driving the inside/outside air switching device 43 is controlled by a control signal output from the control device 50.

An interior blower 42 is disposed downstream of the inside/outside air switching device 43 in the blown air flow. The interior blower 42 blows the air drawn in through the inside/outside air switching device 43 toward the vehicle interior. The interior blower 42 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (i.e., blowing capacity) of the interior blower 42 is controlled by a control voltage output from the control device 50.

The indoor evaporator 19 and the indoor condenser 12 are arranged in this order downstream of the airflow from the indoor blower 42. In other words, the indoor evaporator 19 is arranged upstream of the airflow from the indoor condenser 12. A cold air bypass passage 45 is formed in the casing 41, which allows the air that has passed through the indoor evaporator 19 to bypass the indoor condenser 12 and flow downstream.

An air mix door 44 is disposed downstream of the indoor evaporator 19 and upstream of the indoor condenser 12. The air mix door 44 adjusts the ratio of the volume of air passing through the indoor condenser 12 and the volume of air passing through the cold air bypass passage 45 after passing through the indoor evaporator 19. The operation of the electric actuator for driving the air mix door is controlled by a control signal output from the control device 50.

A mixing space 46 is provided downstream of the interior condenser 12 in the airflow direction, which mixes the airflow heated by the interior condenser 12 with the airflow that has passed through the cold air bypass passage 45 and has not been heated by the interior condenser 12. Furthermore, at the most downstream portion of the airflow direction of the casing 41, an opening hole (not shown) is provided for blowing the airflow (conditioned air) mixed in the mixing space 46 into the vehicle cabin.

Therefore, by adjusting the ratio of the air volume that the air mix door 44 passes through the interior condenser 12 and the air volume that passes through the cold air bypass passage 45, the temperature of the conditioned air mixed in the mixing space 46 can be adjusted. And the temperature of the blown air blown into the vehicle cabin from each opening can be adjusted.

The openings provided include a face opening, a foot opening, and a defroster opening (none of which are shown). The face opening is an opening for blowing conditioned air toward the upper bodies of occupants in the vehicle cabin. The foot opening is an opening for blowing conditioned air toward the feet of occupants. The defroster opening is an opening for blowing conditioned air toward the inside surface of the vehicle front windshield.

A blowing mode switching door (not shown) is located upstream of these openings. The blowing mode switching door switches the opening from which the conditioned air is blown out by opening and closing each opening. The operation of the electric actuator for driving the blowing mode switching door is controlled by a control signal output from the control device 50.

Next, an overview of the electrical control unit of the vehicle air conditioner will be described using FIG. 3. The control device 50 is composed of a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 50 performs various calculations and processing based on the air conditioning control program stored in the ROM, and controls the operation of the various controlled devices 11, 14a-14c, 16a-16c, 31, 42, 43, 44, etc. connected to the output side.

As shown in FIG. 3, various control sensors are connected to the input side of the control device 50. The control sensors include an inside air temperature sensor 51a, an outside air temperature sensor 51b, and a solar radiation sensor 51c. Further control sensors include a high pressure sensor 51d, an air conditioning air temperature sensor 51e, an evaporator temperature sensor 51f, an evaporator pressure sensor 51g, an outdoor unit temperature sensor 51h, an outdoor unit pressure sensor 51i, and a battery temperature sensor 51j.

The interior air temperature sensor 51a is an interior air temperature detection unit that detects the interior air temperature Tr, which is the temperature inside the vehicle cabin. The exterior air temperature sensor 51b is an exterior air temperature detection unit that detects the exterior air temperature Tam, which is the temperature outside the vehicle cabin. The solar radiation sensor 51c is an exterior radiation detection unit that detects the amount of solar radiation As irradiated into the vehicle cabin.

The high-pressure pressure sensor 51d is a high-pressure pressure detection unit that detects the high-pressure pressure Pd, which is the pressure of the high-pressure refrigerant discharged from the compressor 11. The conditioned air temperature sensor 51e is an conditioned air temperature detection unit that detects the temperature TAV of the air blown out from the mixing space 46 into the vehicle cabin.

The evaporator temperature sensor 51f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Te in the indoor evaporator 19. In this embodiment, the evaporator temperature sensor 51f specifically detects the temperature of the refrigerant on the outlet side of the indoor evaporator 19.

The evaporator pressure sensor 51g is an evaporator pressure detection unit that detects the refrigerant evaporation pressure Pe in the indoor evaporator 19. In this embodiment, the evaporator pressure sensor 51g specifically detects the pressure of the refrigerant on the outlet side of the indoor evaporator 19.

The outdoor unit temperature sensor 51h is an outdoor unit temperature detection unit that detects the outdoor unit refrigerant temperature T1, which is the temperature of the refrigerant flowing through the outdoor heat exchanger 18. In this embodiment, the outdoor unit temperature sensor 51h specifically detects the temperature of the refrigerant on the outlet side of the outdoor heat exchanger 18.

The outdoor unit pressure sensor 51i is an outdoor unit temperature detection unit that detects the outdoor unit refrigerant pressure P1, which is the pressure of the refrigerant flowing through the outdoor heat exchanger 18. In this embodiment, the outdoor unit pressure sensor 51i specifically detects the pressure of the refrigerant on the outlet side of the outdoor heat exchanger 18.

The battery temperature sensor 51j is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 30. The battery temperature sensor 51j has multiple temperature detection units and detects the temperature of multiple locations on the battery 30. Therefore, the control device 50 can also detect the temperature difference between each part of the battery 30. Furthermore, the average value of the detection values of the multiple temperature sensors is used as the battery temperature TB.

Furthermore, an operation panel 52 located near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 50, and operation signals are input from various operation switches provided on this operation panel 52.

Specific examples of the various operation switches provided on the operation panel 52 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, etc.

The auto switch is an operation switch that sets or cancels the automatic control operation of the refrigeration cycle device 10. The air conditioner switch is an operation switch that requests the cooling of the blown air by the interior evaporator 19. The air volume setting switch is an operation switch that manually sets the air volume of the interior blower 42. The temperature setting switch is an operation switch that sets the target temperature Tset in the vehicle cabin.

The control device 50 of this embodiment is also configured as an integrated control unit that controls the various controlled devices connected to its output side. Therefore, the configuration (i.e., hardware and software) that controls the operation of each controlled device constitutes a control unit that controls the operation of each controlled device.

For example, the components of the control device 50 that control the operation of the first on-off valve 14a, the second on-off valve 14b, and the third on-off valve 14c, which are the refrigerant circuit switching unit, constitute the refrigerant circuit control unit 50a.

Next, the operation of the vehicle air conditioner of this embodiment configured as described above will be described. The refrigeration cycle device 10 is configured to be able to switch the refrigerant circuit in order to air condition the vehicle interior and cool the battery 30.

Specifically, in the refrigeration cycle device 10 of this embodiment, in order to condition the air inside the vehicle cabin, the refrigerant circuit can be switched between an outside air heating mode refrigerant circuit, a cooling mode refrigerant circuit, and an outside air parallel dehumidification heating mode refrigerant circuit. The outside air heating mode is an operation mode in which heated ventilation air is blown into the vehicle cabin. The cooling mode is an operation mode in which cooled ventilation air is blown into the vehicle cabin. The outside air parallel dehumidification heating mode is an operation mode in which cooled and dehumidified ventilation air is reheated and blown into the vehicle cabin.

These operating modes are switched by executing an air conditioning control program that is pre-stored in the control device 50. The air conditioning control program is executed when the auto switch on the operation panel 52 is turned on. The air conditioning control program switches operating modes based on detection signals from various control sensors and operation signals from the operation panel. The operation of each operating mode is explained below.

(a) Outdoor Air Heating Mode In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a to a throttling state that exerts a refrigerant decompression effect, and sets the cooling expansion valve 16b to a fully closed state.

As a result, in the refrigeration cycle device 10 in outdoor air heating mode, the refrigerant discharged from the compressor 11 is switched to the first circuit in which it circulates in the following order: indoor condenser 12 → receiver 15 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port of the compressor 11.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the compressor 11, the control device 50 controls the discharge capacity so that the high-pressure pressure Pd detected by the high-pressure pressure sensor 51d approaches the target high-pressure PDO. The target high-pressure PDO is determined based on the target blowing temperature TAO by referring to a control map for the outdoor air heating mode that is pre-stored in the control device 50. The target blowing temperature TAO is calculated using the detection signals of the various control sensors and the operation signals of the operation panel.

For the heating expansion valve 16a, the control device 50 controls the throttle opening so that the degree of superheat SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches a predetermined target degree of superheat KSH (5°C in this embodiment). The degree of superheat SH1 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.

The control device 50 also controls the opening of the air mix door 44 so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO. In the outdoor air heating mode, the opening of the air mix door 44 may be controlled so that the entire volume of the blown air that has passed through the indoor evaporator 19 flows into the indoor condenser 12.

In the refrigeration cycle device 10, when the compressor 11 is operated, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 releases heat to the blown air that has passed through the indoor evaporator 19 and condenses. This heats the blown air.

The refrigerant flowing out of the indoor condenser 12 flows into the receiver 15 via the first three-way joint 13a and the inlet side passage 21a. The refrigerant flowing into the receiver 15 is separated into gas and liquid in the receiver 15. A portion of the liquid phase refrigerant separated in the receiver 15 flows into the heating expansion valve 16a via the outlet side passage 21b and the second three-way joint 13b. The remaining liquid phase refrigerant separated in the receiver 15 is stored in the receiver 15 as surplus refrigerant.

The refrigerant that flows into the heating expansion valve 16a is decompressed until it becomes a low-pressure refrigerant. At this time, the throttle opening of the heating expansion valve 16a is controlled so that the superheat degree SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target superheat degree KSH. In the outdoor air heating mode, the superheat degree of the refrigerant on the outlet side of the outdoor heat exchanger 18 is essentially controlled so that it approaches the target superheat degree KSH.

The low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18. The refrigerant that flows into the outdoor heat exchanger 18 exchanges heat with the outside air blown by the outdoor air fan, absorbing heat from the outside air and evaporating. The refrigerant that flows out of the outdoor heat exchanger 18 is sucked into the compressor 11 via the third three-way joint 13c, the suction side passage 21d, and the fourth three-way joint 13d, and is compressed again.

Therefore, in the outside air heating mode, the interior of the vehicle can be heated by blowing out the ventilation air heated by the interior condenser 12 into the vehicle interior.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state and the cooling expansion valve 16b in a throttled state.

As a result, in the refrigeration cycle device 10 in cooling mode, the refrigerant discharged from the compressor 11 is switched to the second circuit in which it circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of the compressor 11.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the compressor 11, the discharge capacity is controlled so that the evaporator temperature Te detected by the evaporator temperature sensor 51f approaches the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target blowing temperature TAO by referring to a control map for the cooling mode that is stored in advance in the control device 50.

In this control map, the target evaporator temperature TEO is determined to increase with an increase in the target air outlet temperature TAO. Furthermore, the target evaporator temperature TEO is determined to a value within a range (specifically, 1°C or higher) that can suppress frost formation on the indoor evaporator 19.

For the cooling expansion valve 16b, the control device 50 controls the throttle opening so that the superheat degree SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target superheat degree KSH. The superheat degree SH2 is calculated from the evaporator temperature Te and the refrigerant evaporation pressure Pe detected by the evaporator pressure sensor 51g. For the air mix door 44, the control device 50 controls the opening of the air mix door 44 so that the entire volume of the blown air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45.

In the refrigeration cycle device 10, when the compressor 11 is operated, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. In the cooling mode, the entire volume of the blown air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45. Therefore, the refrigerant that has flowed into the indoor condenser 12 flows out of the indoor condenser 12 without exchanging heat with the blown air.

The refrigerant that flows out of the indoor condenser 12 flows into the heating expansion valve 16a via the first three-way joint 13a and the outside air passage 21c. In the cooling mode, the heating expansion valve 16a is fully open. Therefore, the refrigerant that flows into the heating expansion valve 16a flows out of the heating expansion valve 16a without being decompressed. In other words, in the cooling mode, the indoor condenser 12 and the heating expansion valve 16a simply function as a refrigerant passage.

The refrigerant that flows out of the heating expansion valve 16a flows into the outdoor heat exchanger 18. The refrigerant that flows into the outdoor heat exchanger 18 exchanges heat with the outside air blown by the outdoor air fan, dissipating heat into the outside air and condensing.

The refrigerant flowing out of the outdoor heat exchanger 18 flows into the receiver 15 via the third three-way joint 13c, the fifth three-way joint 13e, and the inlet side passage 21a. The refrigerant flowing into the receiver 15 is separated into gas and liquid in the receiver 15. A portion of the liquid phase refrigerant separated in the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the sixth three-way joint 13f. The remaining liquid phase refrigerant separated in the receiver 15 is stored in the receiver 15 as surplus refrigerant.

The refrigerant that flows into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant. At this time, the throttle opening of the cooling expansion valve 16b is controlled so that the superheat degree SH2 approaches the target superheat degree KSH. In the cooling mode, the superheat degree of the refrigerant on the outlet side of the indoor evaporator 19 is essentially controlled so that it approaches the target superheat degree KSH.

The low-pressure refrigerant decompressed by the cooling expansion valve 16b flows into the indoor evaporator 19. The refrigerant that flows into the indoor evaporator 19 exchanges heat with the air blown from the indoor blower 42, absorbing heat from the air and evaporating. This cools the air. The refrigerant that flows out of the indoor evaporator 19 is sucked into the compressor 11 via the eighth three-way joint 13h and the fourth three-way joint 13d and is compressed again.

Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

(c) Outdoor Air Parallel Dehumidification Heating Mode In the outdoor air parallel dehumidification heating mode, the control device 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a throttled state, and the cooling expansion valve 16b in a throttled state.

As a result, in the refrigeration cycle device 10 in the outdoor air parallel dehumidification heating mode, the refrigerant discharged from the compressor 11 flows in the order of the indoor condenser 12 → receiver 15. Furthermore, the refrigerant circulates in the order of the receiver 15 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port of the compressor 11, and also in the order of the receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of the compressor 11, forming a third circuit.

In other words, the refrigeration cycle device 10 in the outdoor air parallel dehumidification heating mode is switched to a circuit in which the outdoor heat exchanger 18 and the indoor evaporator 19 are connected in parallel to the flow of refrigerant flowing out of the receiver 15.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the compressor 11, the discharge capacity is controlled in the same way as in the cooling mode. For the heating expansion valve 16a, the throttle opening is controlled in the same way as in the outdoor air heating mode. For the cooling expansion valve 16b, the throttle opening is controlled in the same way as in the cooling mode. For the air mix door 44, the control device 50 controls the opening so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.

In the refrigeration cycle device 10, when the compressor 11 is operated, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 condenses by releasing heat to the blown air that has passed through the indoor evaporator 19. This heats up the blown air that was cooled when passing through the indoor evaporator 19.

The refrigerant flowing out of the indoor condenser 12 flows into the receiver 15 via the first three-way joint 13a and the inlet side passage 21a. The refrigerant that flows into the receiver 15 is separated into gas and liquid in the receiver 15.

A portion of the liquid phase refrigerant separated in the receiver 15 flows into the heating expansion valve 16a via the outlet side passage 21b and the second three-way joint 13b. Another portion of the liquid phase refrigerant separated in the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the sixth three-way joint 13f. The remaining liquid phase refrigerant separated in the receiver 15 is stored in the receiver 15 as surplus refrigerant.

The refrigerant that flows from the receiver 15 into the heating expansion valve 16a is reduced in pressure until it becomes a low-pressure refrigerant. At this time, the throttle opening of the heating expansion valve 16a is controlled so that the outdoor unit refrigerant temperature T1 is lower than the outside air temperature Tam.

The low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18. The refrigerant that flows into the outdoor heat exchanger 18 exchanges heat with the outside air blown by the outdoor air fan, absorbing heat from the outside air and evaporating. The refrigerant that flows out of the outdoor heat exchanger 18 flows into the fourth three-way joint 13d via the third three-way joint 13c and the suction side passage 21d.

The refrigerant that flows from the receiver 15 into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant. At this time, the throttle opening of the cooling expansion valve 16b is controlled so that the superheat degree SH2 approaches the target superheat degree KSH.

The low-pressure refrigerant decompressed by the cooling expansion valve 16b flows into the indoor evaporator 19. The refrigerant that flows into the indoor evaporator 19 exchanges heat with the air blown from the indoor blower 42, absorbing heat from the air and evaporating. This cools the air. The refrigerant that flows out of the indoor evaporator 19 flows into the fourth three-way joint 13d via the eighth three-way joint 13h.

At the fourth three-way joint 13d, the flow of refrigerant flowing out of the outdoor heat exchanger 18 and the flow of refrigerant flowing out of the indoor evaporator 19 join together. The refrigerant flowing out of the fourth three-way joint 13d is sucked into the compressor 11 and compressed again.

Therefore, in the outdoor air parallel dehumidification heating mode, the ventilation air that has been cooled and dehumidified in the interior evaporator 19 is reheated in the interior condenser 12 and blown out into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin.

As described above, in the vehicle air conditioning system of this embodiment, the refrigeration cycle device 10 can achieve comfortable air conditioning in the vehicle cabin by switching the refrigerant circuit according to each operating mode.

Note that in the above-mentioned (a) outdoor air heating mode, (b) cooling mode, and (c) outdoor air parallel dehumidification heating mode, the battery 30 is not cooled, but the vehicle air conditioner of this embodiment can execute an operation mode that cools the battery 30.

The operating mode for cooling the battery 30 can be executed while the refrigeration cycle device 10 is in operation, regardless of whether or not any of the air conditioning operating modes is being executed. In other words, the operating mode for cooling the battery 30 can be executed in parallel with any of the air conditioning operating modes, or can be executed independently.

In other words, the vehicle air conditioning system of this embodiment can execute a battery-only mode in which only the battery 30 is cooled without conditioning the vehicle interior. Furthermore, various operating modes can be executed in which the battery 30 is cooled while the vehicle interior is air-conditioned.

The operation mode for cooling the battery 30 is executed when the battery temperature TB detected by the battery temperature sensor 51j becomes equal to or higher than a predetermined reference battery temperature KTB. The operation of the operation mode for cooling the battery 30 is described below.

(d) Battery Only Mode In the battery only mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 fully opens the heating expansion valve 16a, fully closes the cooling expansion valve 16b, and throttles the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10 in battery only mode, the refrigerant discharged from the compressor 11 is switched to the second circuit in which it circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → receiver 15 → cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → suction port of the compressor 11.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the compressor 11, the discharge capacity is controlled so that the battery temperature TB approaches the target battery temperature KTB2. The target battery temperature KTB2 is determined based on the battery temperature TB by referring to a control map for the battery only mode that is pre-stored in the control device 50.

In addition, for the cooling expansion valve 16c, the control device 50 controls the throttle opening so that the superheat degree SH3 of the outlet side refrigerant of the refrigerant passage 30a of the battery 30 approaches the target superheat degree KSH. The control device 50 also stops the indoor blower 42.

In the refrigeration cycle device 10, when the compressor 11 is operated, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. In the battery-only mode, the indoor blower 42 is stopped. Therefore, the refrigerant that flows into the indoor condenser 12 flows out of the indoor condenser 12 without exchanging heat with the blown air.

The refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 18, just like in the cooling mode. The refrigerant that flows into the outdoor heat exchanger 18 exchanges heat with the outdoor air blown by the outdoor air fan, and condenses by dissipating heat into the outdoor air. Furthermore, the refrigerant that flows out of the outdoor heat exchanger 18 flows into the receiver 15 via the third three-way joint 13c, the fifth three-way joint 13e, and the inlet side passage 21a, just like in the cooling mode.

A portion of the liquid-phase refrigerant separated in the receiver 15 flows into the cooling expansion valve 16c via the outlet passage 21b, the sixth three-way joint 13f, and the seventh three-way joint 13g. The remaining liquid-phase refrigerant separated in the receiver 15 is stored in the receiver 15 as surplus refrigerant. The refrigerant that flows into the cooling expansion valve 16c is decompressed until it becomes a low-pressure refrigerant. At this time, the throttle opening of the cooling expansion valve 16c is controlled so that the superheat degree SH3 approaches the target superheat degree KSH.

The low-pressure refrigerant decompressed by the cooling expansion valve 16c flows into the refrigerant passage 30a of the battery 30. The refrigerant that flows into the refrigerant passage 30a absorbs heat from the battery 30 (i.e., waste heat from the battery 30) and evaporates. This cools the battery 30. The refrigerant that flows out of the refrigerant passage 30a of the battery 30 is sucked into the compressor 11 via the eighth three-way joint 13h and the fourth three-way joint 13d.

Therefore, in battery only mode, only the battery 30 can be cooled without air conditioning the interior of the vehicle.

In the above-mentioned (d) battery only mode, an example has been described in which the interior blower 42 is stopped on the assumption that air conditioning in the vehicle cabin is not performed, but the interior blower 42 may be operated when the (d) battery only mode is executed. In this case, it is possible to cool the battery 30 and at the same time operate in a blowing mode in which the blown air is blown into the vehicle cabin without adjusting the temperature.

In addition, in an operation mode that simultaneously conditions the air inside the vehicle cabin and cools the battery 30, the control device 50 controls the same controlled devices as in each operation mode for air conditioning, and also throttles the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10, regardless of the air conditioning operating mode, a circuit for cooling the battery is added in which the refrigerant flowing out of the receiver 15 flows in the following order: cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → intake port of the compressor 11.

That is, when the outdoor air heating mode and the cooling of the battery 30 are executed in parallel, the refrigeration cycle device 10 is switched to a circuit in which the outdoor heat exchanger 18 and the refrigerant passage 30a of the battery 30 are connected in parallel to the flow of the refrigerant flowing out of the receiver 15. In the following description, the operating mode in which the outdoor air heating mode and the cooling of the battery 30 are executed in parallel is referred to as (e) outdoor air waste heat heating mode.

When the cooling mode and the cooling of the battery 30 are performed in parallel, the refrigeration cycle device 10 is switched to a circuit in which the indoor evaporator 19 and the refrigerant passage 30a of the battery 30 are connected in parallel to the flow of refrigerant flowing out of the receiver 15. In the following description, the operating mode in which the cooling mode and the cooling of the battery 30 are performed in parallel is referred to as (f) cooling battery mode.

When the outdoor air parallel dehumidification heating mode and the cooling of the battery 30 are executed in parallel, the refrigeration cycle device 10 is switched to a circuit in which the outdoor heat exchanger 18, the indoor evaporator 19, and the refrigerant passage 30a of the battery 30 are connected in parallel to the flow of refrigerant flowing out from the receiver 15. In the following description, the operating mode in which the outdoor air parallel dehumidification heating mode and the cooling of the battery 30 are executed in parallel is referred to as (g) outdoor air waste heat parallel dehumidification heating mode.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the cooling expansion valve 16c, the control device 50 controls the throttle opening so that the superheat degree SH3 of the outlet side refrigerant of the refrigerant passage 30a of the battery 30 approaches the target superheat degree KSH, as in the battery only mode.

In the refrigeration cycle device 10, the refrigerant flowing out of the receiver 15 flows into the cooling expansion valve 16c via the sixth three-way joint 13f and the seventh three-way joint 13g. The refrigerant flowing from the receiver 15 into the cooling expansion valve 16c is reduced in pressure until it becomes a low-pressure refrigerant.

The low-pressure refrigerant decompressed by the cooling expansion valve 16c flows into the refrigerant passage 30a of the battery 30. The refrigerant that flows into the refrigerant passage 30a absorbs heat from the battery 30 (i.e., waste heat from the battery 30) and evaporates. This cools the battery 30. The refrigerant that flows out of the refrigerant passage 30a of the battery 30 is sucked into the compressor 11 via the eighth three-way joint 13h and the fourth three-way joint 13d.

As described above, in the vehicle air conditioning system of this embodiment, by executing (e) the outside air waste heat heating mode, (f) the cooling battery mode, and (g) the outside air waste heat parallel dehumidification heating mode, it is possible to simultaneously condition the air inside the vehicle cabin and cool the battery 30. Furthermore, in (e) the outside air waste heat heating mode and (g) the outside air waste heat parallel dehumidification heating mode, the waste heat of the battery 30 can be used as a heat source for heating the blown air.

In addition, in the refrigeration cycle device 10 of this embodiment, as described in (a) outdoor air heating mode, when switching to the first circuit, the refrigerant decompressed by the heating expansion valve 16a can be evaporated in the outdoor heat exchanger 18. At this time, the high-pressure liquid phase refrigerant condensed in the indoor condenser 12 can be stored in the receiver 15 as surplus refrigerant. Therefore, the refrigerant on the outlet side of the outdoor heat exchanger 18 can be superheated.

This allows the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 18, which is the heat exchange part that evaporates the refrigerant, to be increased compared to a refrigeration cycle device that has an accumulator that is a low-pressure side liquid storage part as a liquid storage part (hereinafter referred to as a comparative refrigeration cycle device). As a result, the amount of heat released by the refrigerant in the indoor condenser 12 can be increased, and the heating capacity of the indoor condenser 12 for heating the blown air can be improved.

Therefore, (a) the refrigeration cycle device 10 in outdoor air heating mode can improve the coefficient of performance of the cycle compared to the refrigeration cycle device of the comparative example.

The accumulator is a low-pressure liquid storage section that is arranged in the refrigerant flow path from the refrigerant outlet side of the heat exchange section that evaporates the refrigerant to the suction side of the compressor, and stores the excess refrigerant in the cycle as liquid-phase refrigerant. The amount of heat absorbed by the refrigerant in the heat exchange section that evaporates the refrigerant is defined as the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side from the enthalpy of the refrigerant on the outlet side of the heat exchange section that evaporates the refrigerant.

In addition, in the refrigeration cycle device 10 of this embodiment, as described in (b) cooling mode, when switching to the second circuit, the refrigerant decompressed by the cooling expansion valve 16b can be evaporated in the indoor evaporator 19. At this time, the high-pressure liquid phase refrigerant condensed in the outdoor heat exchanger 18 can be stored in the receiver 15 as surplus refrigerant. Therefore, the refrigerant on the outlet side of the indoor evaporator 19 can be superheated.

This allows the amount of heat absorbed by the refrigerant in the indoor evaporator 19, which is the heat exchanger that evaporates the refrigerant, to be increased compared to the refrigeration cycle device of the comparative example. As a result, the cooling capacity of the indoor evaporator 19 for the blown air can be improved.

Therefore, (b) the refrigeration cycle device 10 in cooling mode can improve the coefficient of performance of the cycle compared to the refrigeration cycle device of the comparative example.

In addition, in the refrigeration cycle device 10 of this embodiment, as described in (c) outdoor air parallel dehumidification heating mode, when switching to the third circuit, the refrigerant decompressed by the cooling expansion valve 16b can be evaporated in the indoor evaporator 19. Furthermore, the refrigerant decompressed by the cooling expansion valve 16b can be evaporated in the indoor evaporator 19.

At this time, the high-pressure liquid-phase refrigerant condensed in the indoor condenser 12 can be stored in the receiver 15 as excess refrigerant. Therefore, it is possible to provide a degree of superheat to both the outlet side refrigerant of the outdoor heat exchanger 18 and the outlet side refrigerant of the indoor evaporator 19.

This allows the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 18, which is the heat exchanger that evaporates the refrigerant, to be increased compared to the refrigeration cycle device of the comparative example. As a result, the amount of heat released by the refrigerant in the indoor condenser 12 is increased, and the heating capacity of the indoor condenser 12 for heating the blown air can be improved.

Furthermore, the amount of heat absorbed by the refrigerant in the indoor evaporator 19, which is the heat exchanger that evaporates the refrigerant, can be increased compared to the refrigeration cycle device of the comparative example. As a result, the cooling capacity of the blown air in the indoor evaporator 19 can be improved.

Therefore, in the (c) outdoor air parallel dehumidification heating mode refrigeration cycle device 10, the coefficient of performance of the cycle can be improved more than that of the comparative example refrigeration cycle device. In other words, according to the refrigeration cycle device 10 of this embodiment, even if the refrigerant circuit is configured to be switchable, the coefficient of performance can be improved.

In this embodiment, the first switching unit 22a is composed of the first opening/closing valve 14a, the second opening/closing valve 14b, and the first three-way joint 13a. Specifically, the first switching unit 22a in this embodiment guides the refrigerant flowing out of the indoor condenser 12 to one of the receiver 15 side and the second three-way joint 13b side.

Furthermore, the second three-way joint 13b constituting the joint portion of this embodiment specifically guides one of the refrigerant flowing out of the first three-way joint 13a and the refrigerant flowing out of the receiver 15 to the heating expansion valve 16a side.

The third on-off valve 14c, the third three-way joint 13c, and the second check valve 17b constitute the second switching unit 22b. Specifically, the second switching unit 22b in this embodiment guides the refrigerant flowing out of the outdoor heat exchanger 18 to one of the suction port side of the compressor 11 and the receiver 15 side.

This makes it easy to realize a refrigeration cycle device in which the flow direction of the refrigerant in the receiver 15 does not change even when the refrigerant circuit is switched. Therefore, the gas-liquid separation performance of the receiver 15 is unlikely to change even when the refrigerant circuit is switched. Furthermore, it is easy to realize a refrigeration cycle device in which excess refrigerant in the cycle is stored in the common receiver 15 even when the refrigerant circuit is switched. Therefore, it is possible to prevent the refrigeration cycle device 10 from becoming too large overall.

The operating modes of the refrigeration cycle device 10 are not limited to the above-mentioned operating modes. For example, the following (h) Eva-only dehumidifying and heating mode, (i) waste heat heating mode, and (j) waste heat parallel dehumidifying and heating mode may be executed. The (h) Eva-only dehumidifying and heating mode, (i) waste heat heating mode, and (j) waste heat parallel dehumidifying and heating mode are operating modes in which refrigerant is not circulated through the outdoor heat exchanger 18.

(h) Eva-only dehumidifying and heating mode In the eva-only dehumidifying and heating mode, the control device 50 opens the first on-off valve 14a and closes the second on-off valve 14b. Furthermore, the control device 50 fully closes the heating expansion valve 16a, throttles the cooling expansion valve 16b, and fully closes the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10 in the Eva-only dehumidification and heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: indoor condenser 12 → receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of the compressor 11.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 and the cooling expansion valve 16b are controlled in the same way as in the cooling mode.

For this reason, in the refrigeration cycle device 10 in the Eva-only dehumidifying and heating mode, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser and the indoor evaporator 19 functions as an evaporator.

Therefore, in the EVA only dehumidifying and heating mode, the ventilation air that has been cooled and dehumidified in the interior evaporator 19 is reheated in the interior condenser 12 and blown out into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin.

(i) Waste heat heating mode In the waste heat heating mode, the controller 50 opens the first on-off valve 14a and closes the second on-off valve 14b. Furthermore, the controller 50 fully closes the heating expansion valve 16a, fully closes the cooling expansion valve 16b, and throttles the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10 in waste heat heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: indoor condenser 12 → receiver 15 → cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → suction port of the compressor 11.

In this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 is controlled in the same way as in the outside air heating mode. In this case, if cooling the battery 30 is prioritized over heating the vehicle interior, the operation of the compressor 11 may be controlled in the same way as in the battery only mode. In addition, the cooling expansion valve 16c is controlled in the same way as in the battery only mode.

Therefore, in the refrigeration cycle device 10 in the waste heat heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser and the refrigerant passage 30a of the battery 30 functions as an evaporator.

Therefore, in the waste heat heating mode, the vehicle interior can be heated by blowing out the ventilation air heated by the interior condenser 12 into the vehicle interior. Furthermore, the refrigerant flowing through the refrigerant passage 30a of the battery 30 absorbs heat from the battery 30, thereby cooling the battery 30. The heat absorbed by the refrigerant from the battery 30 can then be used as a heating source for the ventilation air.

(j) Waste Heat Parallel Dehumidifying and Heating Mode In the waste heat parallel dehumidifying and heating mode, the control device 50 opens the first on-off valve 14a and closes the second on-off valve 14b. Furthermore, the control device 50 fully closes the heating expansion valve 16a, throttles the cooling expansion valve 16b, and throttles the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10 in the waste heat parallel dehumidification heating mode, the refrigerant discharged from the compressor 11 flows in the order of the indoor condenser 12 → receiver 15. Furthermore, a refrigerant circuit is formed in which the refrigerant circulates in the order of the receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of the compressor 11, and also circulates in the order of the receiver 15 → cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → suction port of the compressor 11.

In other words, the refrigeration cycle device 10 in the waste heat parallel dehumidification heating mode is switched to a circuit in which the refrigerant passage 30a of the indoor evaporator 19 and the battery 30 are connected in parallel to the flow of refrigerant flowing out from the receiver 15. In other words, the waste heat parallel dehumidification heating mode is an operating mode in which the evaporator only dehumidification heating mode and the cooling of the battery 30 are performed in parallel.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 and cooling expansion valve 16b are controlled in the same way as in cooling mode. The cooling expansion valve 16c is controlled in the same way as in battery only mode.

Therefore, in the refrigeration cycle device 10 in the waste heat parallel dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser and the indoor evaporator 19 and the refrigerant passage 30a of the battery 30 function as an evaporator.

Therefore, in the waste heat parallel dehumidification heating mode, the ventilation air that has been cooled and dehumidified by the interior evaporator 19 is reheated by the interior condenser 12 and blown out into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin. Furthermore, the refrigerant flowing through the refrigerant passage 30a of the battery 30 absorbs heat from the battery 30, thereby cooling the battery 30. The heat absorbed by the refrigerant from the battery 30 can then be used as a heating source for the ventilation air.

In addition, the refrigeration cycle device 10 may operate in the following modes: (k) series evaporator only dehumidifying and heating mode, (m) series waste heat heating mode, and (n) series waste heat parallel dehumidifying and heating mode. The (k) series evaporator only dehumidifying and heating mode, (m) series waste heat heating mode, and (n) series waste heat parallel dehumidifying and heating mode are operation modes in which the indoor condenser 12 and the outdoor heat exchanger 18 are directly connected via the heating expansion valve 16a.

(k) Series Evaporator Only Dehumidifying and Heating Mode In the series evaporator only dehumidifying and heating mode, the controller 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the controller 50 throttles the heating expansion valve 16a, throttles the cooling expansion valve 16b, and fully closes the cooling expansion valve 16c.

As a result, in the refrigeration cycle device 10 in the series evaporator only dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12 → heating expansion valve 16a → outdoor heat exchanger 18 → receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of compressor 11.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 and the cooling expansion valve 16b are controlled in the same way as in the cooling mode.

The throttle opening of the heating expansion valve 16a is adjusted so that the temperature of the high-pressure refrigerant flowing out of the indoor condenser 12 becomes a reference temperature. More specifically, the throttle opening is adjusted so that the high-pressure pressure Pd detected by the high-pressure pressure sensor 51d becomes a predetermined reference high-pressure KPd. Furthermore, the throttle opening of the heating expansion valve 16a is adjusted within a range in which the temperature of the refrigerant flowing into the outdoor heat exchanger 18 is higher than the outside air temperature.

Therefore, in the refrigeration cycle device 10 in the series evaporator only dehumidification and heating mode, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 and the outdoor heat exchanger 18 function as condensers and the indoor evaporator 19 functions as an evaporator.

Therefore, in the series evaporator only dehumidification heating mode, the ventilation air that has been cooled and dehumidified in the interior evaporator 19 is reheated in the interior condenser 12 and blown out into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin.

In addition, in the series evaporator only dehumidification heating mode, the amount of heat released by the refrigerant in the indoor condenser 12 can be adjusted by adjusting the throttle opening of the heating expansion valve 16a. Therefore, the heating capacity of the indoor condenser 12 for the blown air can be appropriately adjusted.

(m) Serial Waste Heat Heating Mode In the serial waste heat heating mode, the controller 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a in a throttled state, the cooling expansion valve 16b in a fully closed state, and the cooling expansion valve 16c in a throttled state.

As a result, in the refrigeration cycle device 10 in the serial waste heat heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: indoor condenser 12 → heating expansion valve 16a → outdoor heat exchanger 18 → receiver 15 → cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → suction port of the compressor 11.

In this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 is controlled in the same way as in the outside air heating mode. In this case, if cooling the battery 30 is prioritized over heating the vehicle interior, the operation of the compressor 11 may be controlled in the same way as in the battery only mode. In addition, the heating expansion valve 16a is controlled in the same way as in the series evaporator only dehumidification heating mode. The cooling expansion valve 16c is controlled in the same way as in the battery only mode.

Therefore, in the refrigeration cycle device 10 in the serial waste heat heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 12 and the outdoor heat exchanger 18 function as condensers, and the refrigerant passage 30a of the battery 30 functions as an evaporator.

Therefore, in the serial waste heat heating mode, the interior of the vehicle can be heated by blowing out the ventilation air heated by the interior condenser 12 into the vehicle. Furthermore, the refrigerant flowing through the refrigerant passage 30a of the battery 30 absorbs heat from the battery 30, thereby cooling the battery 30. The heat absorbed by the refrigerant from the battery 30 can then be used as a heating source for the ventilation air.

In addition, in the serial waste heat heating mode, the amount of heat released by the refrigerant in the indoor condenser 12 can be adjusted by adjusting the throttle opening of the heating expansion valve 16a. Therefore, the heating capacity of the ventilation air in the indoor condenser 12 can be appropriately adjusted.

(n) Serial Waste Heat Parallel Dehumidifying and Heating Mode In the serial waste heat parallel dehumidifying and heating mode, the controller 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a to a throttled state, the cooling expansion valve 16b to a throttled state, and the cooling expansion valve 16c to a throttled state.

As a result, in the refrigeration cycle device 10 in the series waste heat parallel dehumidification heating mode, the refrigerant discharged from the compressor 11 flows in the following order: indoor condenser 12 → heating expansion valve 16a → outdoor heat exchanger 18 → receiver 15. Furthermore, a refrigerant circuit is formed in which the refrigerant circulates in the following order: receiver 15 → cooling expansion valve 16b → indoor evaporator 19 → suction port of the compressor 11, and also circulates in the following order: receiver 15 → cooling expansion valve 16c → refrigerant passage 30a of the battery 30 → suction port of the compressor 11.

In other words, in the refrigeration cycle device 10 in the series waste heat parallel dehumidification heating mode, the flow of refrigerant flowing out of the receiver 15 is switched to a circuit in which the indoor evaporator 19 and the refrigerant passage 30a of the battery 30 are connected in parallel.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, the compressor 11 and cooling expansion valve 16b are controlled in the same way as in the cooling mode. The cooling expansion valve 16c is controlled in the same way as in the battery only mode. The heating expansion valve 16a is controlled in the same way as in the series evaporator only dehumidification heating mode.

Therefore, in the refrigeration cycle device 10 in the series waste heat parallel dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 12 and the outdoor heat exchanger 18 function as condensers, and the indoor evaporator 19 and the refrigerant passage 30a of the battery 30 function as evaporators.

Therefore, in the series waste heat parallel dehumidifying and heating mode, the ventilation air cooled and dehumidified by the interior evaporator 19 is reheated by the interior condenser 12 and blown out into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin. Furthermore, the refrigerant flowing through the refrigerant passage 30a of the battery 30 absorbs heat from the battery 30, thereby cooling the battery 30. The heat absorbed by the refrigerant from the battery 30 can then be used as a heating source for the ventilation air.

In addition, in the series waste heat parallel dehumidification heating mode, the amount of heat released by the refrigerant in the indoor condenser 12 can be adjusted by adjusting the throttle opening of the heating expansion valve 16a. Therefore, the heating capacity of the indoor condenser 12 for the blown air can be appropriately adjusted.

In the above-mentioned (a) outdoor air heating mode, (c) outdoor air parallel dehumidification heating mode, (e) outdoor air waste heat heating mode, and (g) outdoor air waste heat parallel dehumidification heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger 18 is below the outdoor air temperature. Therefore, when these operating modes are executed when the outdoor air temperature is low, there is a risk of frost forming on the outdoor heat exchanger 18.

Therefore, when frosting conditions are met that indicate that frost is likely to occur on the outdoor heat exchanger 18, the outdoor heat exchanger 18 may be defrosted by switching to (b) cooling mode, (d) battery only mode, or (f) cooling battery mode for a predetermined period of time. In this way, the outdoor heat exchanger 18 can be defrosted by flowing high-temperature refrigerant discharged from the compressor 11 into the outdoor heat exchanger 18.

Furthermore, when switching to (b) cooling mode, (d) battery only mode, or (f) cooling battery mode in order to defrost the outdoor heat exchanger 18, the control device 50 may control the operation of the compressor 11 to exert a predetermined defrosting capacity. In addition, the frosting condition may be satisfied, for example, when the time during which the outdoor unit refrigerant temperature T1 is below a reference frosting temperature (e.g., -5°C) becomes equal to or longer than a reference frosting time (e.g., 5 minutes).

In addition, if the frosting conditions are met during the execution of (c) outdoor air parallel dehumidification heating mode, the mode can be switched to (b) cooling mode to defrost the outdoor heat exchanger 18. This allows the outdoor heat exchanger 18 to be defrosted quickly, since there is no need to change the control mode of the cooling expansion valve 16b and the cooling expansion valve 16c.

Similarly, if frost conditions are met during (e) outdoor air waste heat heating mode, the mode can be switched to (d) battery only mode in order to defrost the outdoor heat exchanger 18. Similarly, if frost conditions are met during (g) outdoor air waste heat parallel dehumidification heating mode, the mode can be switched to (f) cooling battery mode in order to defrost the outdoor heat exchanger 18.

Second Embodiment
In this embodiment, an example in which the cycle configuration of the refrigeration cycle device 10 is changed from that of the first embodiment, as shown in the overall configuration diagram of FIG. 4, will be described.

In the refrigeration cycle device 10 of this embodiment, the indoor condenser 12 is disposed in the inlet side passage 21a. The refrigerant inlet of the indoor condenser 12 is connected to the outlet side of the first opening/closing valve 14a in the inlet side passage 21a. Furthermore, the refrigerant outlet of the indoor condenser 12 is connected to one inlet side of the fifth three-way joint 13e in the inlet side passage 21a.

For this reason, the first switching unit 22a of the refrigerant circuit switching unit of this embodiment specifically guides the refrigerant discharged from the compressor 11 to one of the indoor condenser 12 side and the second three-way joint 13b side. In addition, the second three-way joint 13b that constitutes the joint section specifically guides one of the refrigerant flowing out of the first three-way joint 13a and the refrigerant flowing out of the receiver 15 to the heating expansion valve 16a side. The other configurations and operations are the same as those of the first embodiment.

Therefore, the refrigeration cycle device 10 of this embodiment operates in the same manner as the first embodiment, and can obtain the same effects as the first embodiment. That is, when switching to any operation mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, even if the first switching unit 22a and the joint unit are connected as in this embodiment, the same effect as in the first embodiment can be obtained. That is, even if the refrigerant circuit is switched, the flow direction of the refrigerant in the receiver 15 does not change, and further, a refrigeration cycle device that stores excess refrigerant in the cycle in the common receiver 15 can be easily realized.

In addition, in the refrigeration cycle device 10 of this embodiment, the refrigerant is not allowed to flow into the indoor condenser 12 in the cooling mode. Therefore, in the cooling mode, there is no pressure loss that occurs when the refrigerant flows through the indoor condenser 12. This reduces the power consumption of the compressor 11 in the cooling mode, and further improves the coefficient of performance.

Third Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 5, an example in which the cycle configuration of the refrigeration cycle device 10 is changed from that of the second embodiment will be described.

In the refrigeration cycle device 10 of this embodiment, the heating expansion valve 16a is disposed in the outlet side passage 21b. The inlet of the heating expansion valve 16a is connected to one outlet side of the sixth three-way joint 13f in the outlet side passage 21b. Furthermore, the outlet of the heating expansion valve 16a is connected to the other inlet side of the second three-way joint 13b in the outlet side passage 21b. In addition, the first check valve 17a has been eliminated.

For this reason, the first switching unit 22a of the refrigerant circuit switching unit of this embodiment specifically guides the refrigerant discharged from the compressor 11 to one of the indoor condenser 12 side and the second three-way joint 13b side. In addition, the second three-way joint 13b, which constitutes the joint unit, specifically guides one of the refrigerant flowing out of the first three-way joint 13a and the refrigerant flowing out of the heating expansion valve 16a to the outdoor heat exchanger 18 side. The other configurations and operations are the same as those of the second embodiment.

Therefore, the refrigeration cycle device 10 of this embodiment operates in the same manner as the second embodiment, and can obtain the same effects as the second embodiment. That is, when switching to any operation mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, even if the first switching unit 22a and the joint unit are connected as in this embodiment, the same effect as in the second embodiment can be obtained. That is, even if the refrigerant circuit is switched, the flow direction of the refrigerant in the receiver 15 does not change, and further, a refrigeration cycle device that can store surplus refrigerant in the cycle in the common receiver 15 can be easily realized.

In addition, in the refrigeration cycle device 10 of this embodiment, the refrigerant is not allowed to flow into the indoor condenser 12 in the cooling mode. Therefore, as in the second embodiment, the coefficient of performance can be further improved in the cooling mode. Furthermore, since the first check valve 17a can be eliminated, the cycle configuration can be simplified.

Fourth Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 6, an example in which the cycle configuration of the refrigeration cycle device 10 is changed from that of the first embodiment will be described.

In the refrigeration cycle device 10 of this embodiment, the heating expansion valve 16a is disposed in the outlet side passage 21b, as in the third embodiment. In addition, the first check valve 17a has been eliminated.

For this reason, the first switching unit 22a of the refrigerant circuit switching unit of this embodiment specifically guides the refrigerant flowing out from the indoor condenser 12 to one of the receiver 15 side and the second three-way joint 13b side. In addition, the second three-way joint 13b constituting the joint section specifically guides one of the refrigerant flowing out from the first three-way joint 13a and the refrigerant flowing out from the heating expansion valve 16a to the outdoor heat exchanger 18 side. The other configurations and operations are the same as those of the first embodiment.

Therefore, the refrigeration cycle device 10 of this embodiment operates in the same manner as the first embodiment, and can obtain the same effects as the first embodiment. That is, when switching to any operation mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, even if the first switching unit 22a and the joint unit are connected as in this embodiment, the same effect as in the first embodiment can be obtained. That is, even if the refrigerant circuit is switched, the flow direction of the refrigerant in the receiver 15 does not change, and further, a refrigeration cycle device that can store surplus refrigerant in the cycle in the common receiver 15 can be easily realized.

In addition, in the refrigeration cycle device 10 of this embodiment, as in the third embodiment, the first check valve 17a can be eliminated, thereby simplifying the cycle configuration.

Fifth Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 7, an example in which the cycle configuration of the refrigeration cycle device 10 is changed from that of the first embodiment will be described.

In the refrigeration cycle device 10 of this embodiment, a fixed throttle 23a is disposed in the inlet side passage 21a. The fixed throttle 23a is a liquid storage side pressure reducing section that reduces the pressure of the refrigerant flowing into the receiver 15. The fixed throttle 23a is disposed in the inlet side passage 21a in the range from the outlet of the fifth three-way joint 13e to the inlet of the receiver 15. An orifice, a capillary tube, or the like can be used as such a fixed throttle 23a. The rest of the configuration and operation are the same as those of the first embodiment.

Therefore, the refrigeration cycle device 10 of this embodiment operates in the same manner as the first embodiment, and can obtain the same effects as the first embodiment. That is, when switching to any operation mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, the refrigeration cycle device 10 of this embodiment is equipped with a fixed throttle 23a, which further improves the coefficient of performance.

This will be explained using Figure 8. Figure 8 is a Mollier diagram showing the state of the refrigerant in the refrigeration cycle device 10 in the outdoor air heating mode. In the outdoor air heating mode, the indoor condenser 12 is the heat exchanger that condenses the refrigerant. Furthermore, the outdoor heat exchanger 18 is the heat exchanger that evaporates the refrigerant.

In addition, in Figure 8, the change in the state of the refrigerant in the refrigeration cycle device 10 of this embodiment, which is equipped with a fixed throttle 23a, is shown by a thick solid line. Furthermore, the change in the state of the refrigerant in the refrigeration cycle device of the comparative example, which is not equipped with a fixed throttle 23a, is shown by a thin dashed line.

In addition, in FIG. 8, the state of the refrigerant in the receiver 15 in the refrigeration cycle device 10 of this embodiment is indicated by point Lq1. Furthermore, in FIG. 8, the state of the refrigerant in the receiver 15 in the refrigeration cycle device of the comparative example is indicated by point Lqex.

The refrigeration cycle device 10 of this embodiment is equipped with a fixed throttle 23a, so the pressure of the refrigerant in the receiver 15 is lower than the pressure of the high-pressure refrigerant in the heat exchange section where the refrigerant is condensed. Therefore, as shown in FIG. 8, the refrigerant pressure at point Lq1 in the refrigeration cycle device 10 of this embodiment is lower than the refrigerant pressure at point Lqex in the refrigeration cycle device of the comparative example.

Furthermore, along the slope of the saturated liquid line of the Mollier diagram, the enthalpy of the refrigerant at point Lq1 in the refrigeration cycle device 10 of this embodiment is lower than the enthalpy of the refrigerant at point Lqex in the refrigeration cycle device of the comparative example. Therefore, in the refrigeration cycle device 10 of this embodiment, the refrigerant on the outlet side of the heat exchanger that condenses the refrigerant becomes supercooled liquid phase refrigerant SC1.

Therefore, in the refrigeration cycle device 10 of this embodiment, the enthalpy of the refrigerant flowing into the heat exchange section that evaporates the refrigerant can be reduced more than in the refrigeration cycle device 10 of the comparative example. As a result, the amount of heat absorbed by the refrigerant in the heat exchange section that evaporates the refrigerant can be increased, improving the coefficient of performance. This effect can also be obtained in other operating modes.

Here, in the refrigeration cycle device 10 of this embodiment, an example has been described in which a fixed throttle 23a is used as the liquid storage section side pressure reduction section, but the liquid storage section side pressure reduction section is not limited to this.

For example, as shown in FIG. 9, a fixed throttle 23b may be disposed in the inlet passage 21a in the range from the outlet of the first on-off valve 14a to one of the inlets of the fifth three-way joint 13e. The fixed throttle 23b serves as a first liquid storage side pressure reducing section that reduces the pressure of the refrigerant flowing into the receiver 15 when the refrigerant circuit switching section is switched to the first circuit or the third circuit. This can improve the coefficient of performance in the outdoor air heating mode and the outdoor air parallel dehumidification heating mode.

For example, as shown in FIG. 10, a fixed throttle 23c may be disposed in the range from the other outlet of the third three-way joint 13c to the other inlet of the fifth three-way joint 13e. The fixed throttle 23c serves as a second reservoir side pressure reducing section that reduces the pressure of the refrigerant flowing into the receiver 15 when the refrigerant circuit switching section is switched to the second circuit. This can improve the coefficient of performance in the cooling mode.

Of course, both the fixed throttle 23b, which is the first liquid storage section side pressure reduction section, and the fixed throttle 23c, which is the second liquid storage section side pressure reduction section, may be used. In the refrigeration cycle device 10 of this embodiment, an example in which a fixed throttle is used as the liquid storage section side pressure reduction section has been described, but this is not limited to this, and a variable throttle mechanism may also be used.

Sixth Embodiment
In the refrigeration cycle apparatus 10 of the present embodiment, as compared to the first embodiment, as shown in Fig. 11 , an example will be described in which the heating expansion valve 16a and the third on-off valve 14c, which is a part of the second switching unit 22b, are integrated into an integrated valve 24. Note that Fig. 11 shows the flow of refrigerant through the integrated valve 24 in the outdoor air heating mode and the outdoor air parallel dehumidification heating mode.

The integrated valve 24 has a body 240. The body 240 is made of a metal (aluminum in this embodiment) that has excellent heat conductivity. The body 240 is formed with a first inlet portion 24a, a first outlet portion 24b, a second inlet portion 24c, and a second outlet portion 24d.

The first inlet portion 24a is a refrigerant inlet portion that is connected to the outlet side of the second three-way joint 13b. The first outlet portion 24b is a refrigerant outlet portion that is connected to the refrigerant inlet side of the outdoor heat exchanger 18. The first inlet portion 24a and the first outlet portion 24b are connected within the body 240.

A throttle passage 161 is formed in the refrigerant passage from the first inlet 24a to the first outlet 24b in the body 240. Furthermore, a valve body 162 that changes the throttle passage cross-sectional area of the throttle passage 161 is arranged in the refrigerant passage from the first inlet 24a to the first outlet 24b. The valve body 162 is connected to a stepping motor 163 via a shaft. The stepping motor 163 displaces the valve body 162 to change the throttle passage cross-sectional area.

In other words, in the integrated valve 24, the heating expansion valve 16a is formed by the throttle passage 161, the valve body portion 162, the stepping motor 163, etc.

The second inlet portion 24c is a refrigerant inlet portion that is connected to the refrigerant outlet side of the outdoor heat exchanger 18. The second outlet portion 24d is a refrigerant outlet portion that is connected to one of the inlet sides of the fourth three-way joint 13d. The second inlet portion 24c and the second outlet portion 24d are connected within the body 240.

A valve body 141 that opens and closes the refrigerant passage from the second inlet 24c to the second outlet 24d in the body 240 is disposed in the refrigerant passage. The valve body 141 is connected to a solenoid 142 via a shaft. The solenoid 142 displaces the valve body 141 to open and close the refrigerant passage from the second inlet 24c to the second outlet 24d.

In other words, in the integrated valve 24, the third opening/closing valve 14c is formed by the valve body portion 141, the solenoid 142, etc.

Furthermore, within the body 240, the upstream passage 241 and the downstream passage 242 are arranged adjacent to each other. The upstream passage 241 is a portion of the refrigerant passage extending from the first inlet 24a to the first outlet 24b that is upstream of the throttle passage 161 in the refrigerant flow direction. The downstream passage 242 is a portion of the refrigerant passage extending from the second inlet 24c to the second outlet 24d that is downstream of the valve body 141 in the refrigerant flow direction.

In other words, the refrigerant flowing through the upstream passage 241 is the refrigerant that flows into the heating expansion valve 16a. Also, the refrigerant flowing through the downstream passage 242 is the refrigerant that is guided from the second switching section through the fourth three-way joint 13d to the suction port side of the compressor 11.

As a result, in the integrated valve 24, as shown by the thin dashed arrow in FIG. 11, heat transfer is possible between the refrigerant flowing through the upstream passage 241 and the refrigerant flowing through the downstream passage 242 via the body 240. In other words, in the integrated valve 24, heat exchange can be performed between the refrigerant flowing into the heating expansion valve 16a and the refrigerant guided from the second switching section to the suction port side of the compressor 11. The other configurations and operations are the same as those of the first embodiment.

Therefore, the refrigeration cycle device 10 of this embodiment operates in the same manner as the first embodiment, and can obtain the same effects as the first embodiment. That is, regardless of which operating mode the refrigerant circuit is switched to, high-pressure liquid-phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, the refrigeration cycle device 10 of this embodiment is equipped with an integrated valve 24, which further improves the coefficient of performance in outdoor air heating mode and outdoor air parallel dehumidification heating mode.

This will be explained using Figure 12. Figure 12 is a Mollier diagram showing the state of the refrigerant in the refrigeration cycle device 10 in the outdoor air heating mode. In Figure 12, the thick solid line shows the change in the state of the refrigerant in the refrigeration cycle device 10 of this embodiment that is equipped with the integrated valve 24. Furthermore, the thin dashed line shows the change in the state of the refrigerant in the refrigeration cycle device of the comparative example that is not equipped with the integrated valve 24.

In addition, in FIG. 12, the state of the refrigerant on the inlet side of the outdoor heat exchanger 18 in the refrigeration cycle device 10 of this embodiment is shown by point Ev. Furthermore, in FIG. 12, the state of the refrigerant on the inlet side of the outdoor heat exchanger 18 in the refrigeration cycle device of the comparative example is shown by point Evex.

In the integrated valve 24, heat exchange can be performed between the refrigerant flowing through the upstream passage 241 and the refrigerant flowing through the downstream passage 242. Therefore, as shown in FIG. 12, the enthalpy of the refrigerant at point Ev in the refrigeration cycle device 10 of this embodiment is lower than the enthalpy of the refrigerant at point Evex in the refrigeration cycle device of the comparative example. Therefore, in the refrigeration cycle device 10 of this embodiment, the refrigerant on the outlet side of the heat exchange section that condenses the refrigerant becomes supercooled liquid phase refrigerant SC2.

Therefore, in the refrigeration cycle device 10 of this embodiment, the enthalpy of the refrigerant flowing into the heat exchange section that evaporates the refrigerant can be reduced more than in the refrigeration cycle device 10 of the comparative example. As a result, the amount of heat absorbed by the refrigerant in the heat exchange section that evaporates the refrigerant can be increased, improving the coefficient of performance. This effect can also be obtained in the outdoor air parallel dehumidification heating mode.

Here, in the cooling mode, the third opening/closing valve 14c is closed. That is, the valve body portion 141 closes the refrigerant passage from the second inlet portion 24c to the second outlet portion 24d. Therefore, the refrigerant does not flow through the downstream passage 242. In other words, in the cooling mode, heat exchange does not take place between the refrigerant flowing through the upstream passage 241 and the refrigerant flowing through the downstream passage 242.

Seventh Embodiment
In the refrigeration cycle device 10 of the present embodiment, as compared to the first embodiment, an example will be described in which a configuration corresponding to the third three-way joint 13c of the second switching unit 22b is integrated into the outdoor heat exchanger 18 as shown in FIG.

More specifically, in this embodiment, the outdoor heat exchanger 18 is a so-called tank-and-tube type heat exchanger having multiple tubes and a pair of tanks connected to both ends of the multiple tubes. The tank forms a collection space in which the refrigerant that has circulated through the multiple tubes and exchanged heat with the outside air is collected, and two refrigerant outlets are provided in the tank, which branches the refrigerant flow in the same way as the third three-way joint 13c.

The rest of the configuration and operation are the same as in the first embodiment. Therefore, the refrigeration cycle device 10 of this embodiment can also achieve the same effects as in the first embodiment. That is, when switching to any operating mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, the outdoor heat exchanger 18 and the second switching unit 22b may be integrated by accommodating the third opening/closing valve 14c in the tank of the outdoor heat exchanger 18 of this embodiment. Also, the outdoor heat exchanger 18 and the integrated valve 24 may be integrated by accommodating the integrated valve described in the sixth embodiment in the tank of the outdoor heat exchanger 18 of this embodiment.

Eighth embodiment
In this embodiment, an example in which the cycle configuration of the refrigeration cycle apparatus 10 of the first embodiment is changed as shown in the overall configuration diagram of Fig. 14 will be described. In the refrigeration cycle apparatus 10 of this embodiment, a ninth three-way joint 13i, a tenth three-way joint 13j, a rear cooling expansion valve 16d, and a rear indoor evaporator 19a are added.

The basic configuration of the ninth three-way joint 13i and the tenth three-way joint 13j is the same as that of the first three-way joint 13a, etc. The other outlet side of the seventh three-way joint 13g is connected to the inlet of the ninth three-way joint 13i. The inlet side of the rear cooling expansion valve 16d is connected to one outlet of the ninth three-way joint 13i. The inlet side of the cooling expansion valve 16c is connected to the other outlet of the ninth three-way joint 13i.

The rear cooling expansion valve 16d is a second pressure reducing section that reduces the pressure of the refrigerant flowing out from one outlet of the ninth three-way joint 13i and adjusts the flow rate of the refrigerant flowing downstream. The basic configuration of the rear cooling expansion valve 16d is the same as that of the heating expansion valve 16a, etc.

The refrigerant inlet side of the rear interior evaporator 19a is connected to the outlet of the rear cooling expansion valve 16d. The rear interior evaporator 19a is an evaporation section that evaporates the low-pressure refrigerant decompressed by the rear cooling expansion valve 16d by heat exchange with the blown air blown to the rear seat side. The rear interior evaporator 19a is a rear seat blown air cooling section that cools the blown air blown to the rear seat side. For this reason, in this embodiment, the interior evaporator 19 is used as the front seat blown air cooling section.

One inlet of the tenth three-way joint 13j is connected to the refrigerant outlet of the rear interior evaporator 19a. The other inlet of the tenth three-way joint 13j is connected to the outlet side of the refrigerant passage 30a of the battery 30. The other inlet of the eighth three-way joint 13h is connected to the outlet of the tenth three-way joint 13j.

In other words, in the refrigeration cycle device 10 of this embodiment, the interior evaporator 19, the rear interior evaporator 19a, and the refrigerant passage 30a of the battery 30 are connected in parallel with respect to the refrigerant flow. The rest of the configuration of the refrigeration cycle device 10 is the same as that of the first embodiment.

Next, the operation of the refrigeration cycle device 10 of this embodiment configured as described above will be described. The basic operation of the refrigeration cycle device 10 of this embodiment is the same as that of the first embodiment. Furthermore, in the refrigeration cycle device 10 of this embodiment, the rear cooling expansion valve 16d is throttled in (b) cooling mode, (f) cooling battery mode, etc., so that the air blown not only to the front seats but also to the rear seats can be cooled.

In these driving modes, when cooling the air blown toward the rear seats, the control device 50 controls the throttle opening so that the superheat degree SH4 of the outlet side refrigerant of the rear interior evaporator 19a approaches the target superheat degree KSH. In addition, in these driving modes, when passengers are only seated in the rear seats, such as when the vehicle is stopped, the cooling expansion valve 16b may be fully closed to cool only the air blown toward the rear seats.

Other operations are the same as in the first embodiment. Therefore, the refrigeration cycle device 10 of this embodiment can also achieve the same effects as in the first embodiment. That is, regardless of which operating mode is switched to, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

In this embodiment, an example has been described in which the air conditioning expansion valve 16b, the rear air conditioning expansion valve 16d, and the cooling expansion valve 16c are all electrically operated variable throttle mechanisms that are activated by the supply of electricity, but the present invention is not limited to this.

For example, the cooling expansion valve 16b may be a thermostatic expansion valve that changes the throttle opening so that the superheat degree SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target superheat degree KSH. Furthermore, in addition to the thermostatic expansion valve, an on-off valve that opens and closes the refrigerant flow path to prevent the refrigerant from flowing into the indoor evaporator 19 may be provided.

The temperature-type expansion valve is a mechanical variable throttle mechanism that has a temperature-sensing part with a deformable member (specifically, a diaphragm) that deforms according to the temperature and pressure of the refrigerant at the outlet side of the indoor evaporator 19, and a valve body part that displaces according to the deformation of the deformable member to change the throttle opening.

Similarly, the rear cooling expansion valve 16d may be a temperature-type expansion valve that changes the throttle opening so that the superheat degree SH4 of the refrigerant on the outlet side of the rear interior evaporator 19a approaches the target superheat degree KSH. In addition, an opening/closing valve that opens and closes the refrigerant flow path to prevent the refrigerant from flowing into the rear interior evaporator 19a may be provided.

Similarly, the cooling expansion valve 16c may be a temperature-type expansion valve that changes the throttle opening so that the superheat degree SH3 of the outlet side refrigerant of the refrigerant passage 30a of the battery 30 approaches the target superheat degree KSH. In addition, an opening/closing valve that opens and closes the refrigerant flow path to prevent the refrigerant from flowing into the refrigerant passage 30a may be provided.

Ninth embodiment
In the refrigeration cycle apparatus 10 of the present embodiment, an example will be described in which an internal heat exchanger 26 is added to the first embodiment, as shown in Fig. 15. The internal heat exchanger 26 exchanges heat between the high-pressure refrigerant flowing out from the receiver 15 and the low-pressure refrigerant to be drawn into the compressor 11. Therefore, in the internal heat exchanger 26, the high-pressure refrigerant is cooled to reduce the enthalpy, and the low-pressure refrigerant is heated to increase the enthalpy.

The internal heat exchanger 26 has a high-pressure refrigerant passage 26a through which the high-pressure refrigerant flowing out of the receiver 15 flows, and a low-pressure refrigerant passage 26b through which the low-pressure refrigerant to be drawn into the compressor 11 flows. The high-pressure refrigerant passage 26a is disposed in a refrigerant passage extending from one outlet of the seventh three-way joint 13g to the inlet of the cooling expansion valve 16b. The low-pressure refrigerant passage 26b is disposed in a refrigerant passage extending from the refrigerant outlet of the indoor evaporator 19 to one inlet of the eighth three-way joint 13h.

Here, in FIG. 15, for clarity, the internal heat exchanger 26 is illustrated diagrammatically. More specifically, FIG. 15 diagrammatically illustrates the arrangement of the high-pressure refrigerant passage 26a and the low-pressure refrigerant passage 26b in the refrigeration cycle device 10. The heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant passage 26a and the low-pressure refrigerant flowing through the low-pressure refrigerant passage 26b is indicated by thick arrows. This is also the case in FIG. 16, FIG. 17, etc., which will be described later.

The rest of the configuration and operation are the same as in the first embodiment. Therefore, the refrigeration cycle device 10 of this embodiment can also achieve the same effects as in the first embodiment. That is, when switching to any operating mode, high-pressure liquid phase refrigerant can be stored in the receiver 15 as surplus refrigerant, thereby improving the coefficient of performance.

Furthermore, according to the refrigeration cycle device 10 of this embodiment, the coefficient of performance can be further improved at least in (b) cooling mode, (c) outdoor air parallel dehumidification heating mode, (f) cooling battery mode, and (g) outdoor air waste heat parallel dehumidification heating mode. In other words, the coefficient of performance can be further improved in the operation mode in which the refrigerant decompressed by the cooling expansion valve 16b is evaporated by the indoor evaporator 19.

More specifically, in these operating modes, the high-pressure refrigerant flowing out from the receiver 15 can be supercooled in the internal heat exchanger 26. This reduces the enthalpy of the refrigerant flowing into the indoor evaporator 19, and increases the amount of heat absorbed by the refrigerant in the indoor evaporator 19. As a result, in these operating modes, the coefficient of performance can be improved.

In this embodiment, an example has been described in which the internal heat exchanger 26 is positioned to improve the coefficient of performance during an operation mode in which the refrigerant decompressed by the cooling expansion valve 16b is evaporated by the indoor evaporator 19, but the positioning of the internal heat exchanger 26 is not limited to this.

For example, the arrangement of the internal heat exchanger 26 may be changed, as in the modified example shown in FIG. 16. That is, the high-pressure refrigerant passage 26a may be arranged in the refrigerant passage leading from the other outlet of the seventh three-way joint 13g to the inlet of the refrigerant passage 30a of the battery 30. Furthermore, the low-pressure refrigerant passage 26b may be arranged in the refrigerant passage leading from the inlet of the refrigerant passage 30a of the battery 30 to the other inlet of the eighth three-way joint 13h.

This not only provides the same effects as the first embodiment, but also further improves the coefficient of performance at least in (d) battery only mode, (e) outdoor air waste heat heating mode, (f) cooling battery mode, and (g) outdoor air waste heat parallel dehumidification heating mode. In other words, the coefficient of performance can be further improved in the operating mode in which the refrigerant decompressed by the cooling expansion valve 16c is evaporated in the refrigerant passage 30a of the battery 30.

Also, for example, the arrangement of the internal heat exchanger 26 may be changed, as in the modified example shown in FIG. 17. That is, the high-pressure refrigerant passage 26a may be arranged in the refrigerant passage leading from the outlet of the second three-way joint 13b to the inlet of the heating expansion valve 16a. Furthermore, the low-pressure refrigerant passage 26b may be arranged in the refrigerant passage leading from the outlet of the third opening/closing valve 14c of the suction side passage 21d to one of the inlets of the fourth three-way joint 13d.

This not only makes it possible to obtain the same effects as in the first embodiment, but also makes it possible to further improve the coefficient of performance at least in (a) outdoor air heating mode, (c) outdoor air parallel dehumidification heating mode, (e) outdoor air waste heat heating mode, and (g) outdoor air waste heat parallel dehumidification heating mode. In other words, the coefficient of performance can be further improved in the operation mode in which the refrigerant decompressed by the heating expansion valve 16a is evaporated in the outdoor heat exchanger 18.

Tenth embodiment
In this embodiment, a refrigeration cycle apparatus 10a having a cycle configuration changed from that of the refrigeration cycle apparatus 10 of the fifth embodiment will be described as shown in the overall configuration diagram of Fig. 18. The refrigeration cycle apparatus 10a can configure a gas injection cycle when switched to a refrigerant circuit of a predetermined operation mode.

For this reason, the refrigeration cycle device 10a employs a two-stage boost compressor 111 as the compressor. The compressor 111 is a two-stage boost electric compressor that uses a common electric motor to drive both a low-stage compression mechanism and a high-stage compression mechanism, both of which have fixed discharge capacities. The rotation speed (i.e., the refrigerant discharge pressure) of the compressor 111 is controlled by a control signal output from the control device 50.

The compressor 111 further has a housing that houses a low-stage compression mechanism, a high-stage compression mechanism, an electric motor, etc. The housing forms the outer shell of the compressor 111. The housing has an intake port 111a, an intermediate pressure intake port 111b, and a discharge port 111c.

The suction port 111a is an opening that allows low-pressure refrigerant to be sucked into the low-stage compression mechanism from outside the housing. The intermediate-pressure suction port 111b is an opening that allows intermediate-pressure refrigerant to flow from the outside to the inside of the housing and join the refrigerant in the process of compression from low pressure to high pressure. The intermediate-pressure suction port 111b is connected to the discharge port side of the low-stage compression mechanism and the suction port side of the high-stage compression mechanism inside the housing. The discharge port 111c is an opening that allows high-pressure refrigerant discharged from the high-stage compression mechanism to be discharged to the outside of the housing. The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port 111c.

The refrigeration cycle device 10a also includes an eleventh three-way joint 13k, an intermediate pressure expansion valve 16e, and an internal heat exchanger 26.

The eleventh three-way joint 13k is disposed in the refrigerant passage that extends from the outlet of the first check valve 17a in the outlet-side passage 21b to the other inlet of the second three-way joint 13b. One outlet of the eleventh three-way joint 13k is connected to an injection passage 21e that guides the refrigerant flow branched at the eleventh three-way joint 13k to the intermediate pressure suction port 111b of the compressor 111.

The intermediate pressure expansion valve 16e is disposed in the injection passage 21e. The intermediate pressure expansion valve 16e is a third pressure reducing section that reduces the pressure of a portion of the refrigerant that flows out of the receiver 15 when switching to a predetermined operation mode (in this embodiment, the outdoor air heating mode). The basic configuration of the intermediate pressure expansion valve 16e is the same as that of the heating expansion valve 16a, etc.

The internal heat exchanger 26 exchanges heat between the high-pressure refrigerant flowing out from the other outlet of the eleventh three-way joint 13k and the intermediate-pressure refrigerant decompressed by the intermediate-pressure expansion valve 16e. In the internal heat exchanger 26, the high-pressure refrigerant is cooled to reduce the enthalpy, and the intermediate-pressure refrigerant is heated to increase the enthalpy.

In this embodiment, the high-pressure refrigerant passage of the internal heat exchanger 26 is arranged in the refrigerant passage from the other outlet of the eleventh three-way joint 13k in the outlet side passage 21b to the other inlet of the second three-way joint 13b. The intermediate-pressure refrigerant passage of the internal heat exchanger 26 is arranged in the refrigerant passage from the outlet of the intermediate-pressure expansion valve 16e in the injection passage 21e to the intermediate-pressure suction port 111b of the compressor 111.

In addition, an intermediate temperature sensor and an intermediate pressure sensor (not shown) are connected to the input side of the control device 50 of the refrigeration cycle device 10a.

The intermediate temperature sensor is an intermediate pressure temperature detection unit that detects the temperature of the refrigerant that flows out of the intermediate pressure refrigerant passage of the internal heat exchanger 26 and is sucked into the intermediate pressure suction port 111b of the compressor 111. The intermediate pressure sensor is an intermediate pressure pressure detection unit that detects the pressure of the refrigerant that flows out of the intermediate pressure refrigerant passage of the internal heat exchanger 26 and is sucked into the intermediate pressure suction port 111b of the compressor 111.

The rest of the configuration of the refrigeration cycle device 10a is the same as that of the refrigeration cycle device 10 described in the fifth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a in a throttled state, the cooling expansion valve 16b in a fully closed state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in the outdoor air heating mode, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a first circuit in which the refrigerant circulates in the following order: indoor condenser 12 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant flowing out of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

In this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the intermediate pressure expansion valve 16e, the control device 50 controls the throttle opening so that the superheat degree SH5 of the refrigerant sucked into the intermediate pressure suction port 111b of the compressor 111 approaches a predetermined target superheat degree KSH5 for the intermediate pressure refrigerant. The superheat degree SH5 is calculated using the detection signal of the intermediate temperature sensor and the detection signal of the intermediate pressure sensor. Other controls are the same as those in the outdoor air heating mode of the fifth embodiment.

In the refrigeration cycle device 10a, when the compressor 111 operates, the high-pressure refrigerant discharged from the discharge port 111c of the compressor 111 flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 releases heat to the blown air that has passed through the indoor evaporator 19 and condenses. This heats the blown air.

The refrigerant flowing out from the indoor condenser 12 is decompressed by the fixed throttle 23a in the same manner as in the outdoor air heating mode of the fifth embodiment, and flows into the receiver 15. The refrigerant that flows into the receiver 15 is separated into gas and liquid in the receiver 15. The flow of the liquid phase refrigerant separated in the receiver 15 is branched at the eleventh three-way joint 13k arranged in the outlet side passage 21b.

One of the refrigerants branched at the 11th three-way joint 13k flows into the intermediate pressure expansion valve 16e arranged in the injection passage 21e. The refrigerant flowing into the intermediate pressure expansion valve 16e is depressurized until it becomes an intermediate pressure refrigerant. The intermediate pressure refrigerant depressurized by the intermediate pressure expansion valve 16e flows into the intermediate pressure refrigerant passage of the internal heat exchanger 26.

The other refrigerant branched off at the eleventh three-way joint 13k flows into the high-pressure refrigerant passage of the internal heat exchanger 26. Therefore, in the internal heat exchanger 26, the high-pressure refrigerant flowing through the high-pressure refrigerant passage reduces enthalpy, and the intermediate-pressure refrigerant flowing through the intermediate-pressure refrigerant passage increases enthalpy.

The refrigerant flowing out of the intermediate pressure refrigerant passage of the internal heat exchanger 26 is sucked in from the intermediate pressure suction port 111b of the compressor 111. The refrigerant flowing out of the high pressure refrigerant passage of the internal heat exchanger 26 flows into the heating expansion valve 16a via the outlet side passage 21b and the second three-way joint 13b. The refrigerant flowing into the heating expansion valve 16a is decompressed to a low pressure refrigerant, as in the outdoor air heating mode of the fifth embodiment.

The low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18. The refrigerant that flows into the outdoor heat exchanger 18 absorbs heat from the outside air and evaporates. The refrigerant that flows out of the outdoor heat exchanger 18 passes through the third three-way joint 13c, the suction side passage 21d, and the fourth three-way joint 13d, is sucked into the suction port 111a of the compressor 111, and is compressed again.

In other words, in the refrigeration cycle device 10a in the outdoor air heating mode, an internal heat exchange type gas injection cycle is configured in which the indoor condenser 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing the ventilation air heated by the indoor condenser 12 into the vehicle interior.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 fully opens the heating expansion valve 16a, throttles the cooling expansion valve 16b, and fully closes the intermediate pressure expansion valve 16e.

When the intermediate pressure expansion valve 16e is fully closed, the refrigerant no longer flows into the injection passage 21e. Therefore, the compressor 111 is no longer able to draw in the intermediate pressure refrigerant from the intermediate pressure suction port 111b. As a result, the compressor 111 functions as a single-stage boost compressor. Furthermore, the intermediate pressure refrigerant no longer flows through the intermediate pressure refrigerant passage of the internal heat exchanger 26. As a result, the internal heat exchanger 26 does not exchange heat between the high pressure refrigerant and the intermediate pressure refrigerant.

For this reason, in the cooling mode, the refrigeration cycle device 10a is switched to the second circuit in which the refrigerant circulates, exactly like the cooling mode of the fifth embodiment. Furthermore, in the cooling mode, the control device 50 controls the operation of various controlled devices, similar to the fifth embodiment. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the blown air cooled by the interior evaporator 19 into the vehicle cabin, similar to the fifth embodiment.

In addition, in the refrigeration cycle device 10a of this embodiment, in other operating modes, the control device 50 fully closes the intermediate pressure expansion valve 16e, and operates in the same manner as the refrigeration cycle device 10 of the fifth embodiment. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effects as those of the fifth embodiment can be obtained.

Furthermore, in the refrigeration cycle device 10a of this embodiment, a gas injection cycle can be configured in (a) outdoor air heating mode. In the gas injection cycle, the compression efficiency of the compressor 111 can be improved by merging the intermediate pressure refrigerant with the refrigerant in the process of being pressurized in the compressor 111. Therefore, in (a) outdoor air heating mode, the coefficient of performance can be further improved.

Eleventh Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 19, a refrigeration cycle apparatus 10a in which the arrangement of an eleventh three-way joint 13k is changed from that of the tenth embodiment will be described.

The eleventh three-way joint 13k in this embodiment is disposed in the refrigerant passageway from the outlet of the first on-off valve 14a in the inlet passageway 21a to one inlet of the fifth three-way joint 13e. The intermediate pressure expansion valve 16e in this embodiment is a third pressure reducing section that reduces the pressure of a portion of the refrigerant upstream of the receiver 15 when switching to a predetermined operating mode (in this embodiment, the outdoor air heating mode). The rest of the configuration and basic operation of the refrigeration cycle device 10a are the same as those of the tenth embodiment.

Therefore, in the refrigeration cycle device 10a in the outdoor air heating mode of this embodiment, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a first circuit in which the refrigerant circulates in the following order: indoor condenser 12 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant upstream of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

In other words, in the outdoor air heating mode refrigeration cycle device 10a of this embodiment, similar to the tenth embodiment, an internal heat exchange type gas injection is configured in which the indoor condenser 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effect as the tenth embodiment can be obtained.

Twelfth Embodiment
In this embodiment, as shown in the overall configuration diagram of Fig. 20, an example in which the arrangement of the internal heat exchanger 26 is changed from that of the tenth embodiment will be described. The high-pressure refrigerant passage of the internal heat exchanger 26 of this embodiment is arranged in the refrigerant passage leading from the other outlet of the sixth three-way joint 13f to the inlet of the seventh three-way joint 13g. The other configurations are the same as those of the tenth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 controls the heating expansion valve 16a to be in a throttled state, the cooling expansion valve 16b to be in a fully closed state, and the intermediate pressure expansion valve 16e to be in a fully closed state.

For this reason, in the outdoor air heating mode, the refrigeration cycle device 10a is switched to the first circuit in which the refrigerant circulates, exactly like the outdoor air heating mode of the fifth embodiment. Furthermore, in the outdoor air heating mode, the control device 50 controls the operation of various controlled devices, similar to the fifth embodiment. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing out the blown air heated by the interior condenser 12 into the vehicle cabin, similar to the fifth embodiment.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state, the cooling expansion valve 16b in a throttled state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in cooling mode, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a second circuit in which the refrigerant circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → cooling expansion valve 16b → indoor evaporator 19 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant flowing out of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

In this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the intermediate pressure expansion valve 16e, the control device 50 controls the throttle opening so that the superheat degree SH5 of the refrigerant sucked into the intermediate pressure suction port 111b of the compressor 111 approaches the target superheat degree KSH5. Other controls are the same as those in the cooling mode of the fifth embodiment.

In other words, in the cooling mode, the refrigeration cycle device 10a configures an internal heat exchange type gas injection cycle in which the exterior heat exchanger 18 functions as a condenser and the interior evaporator 19 functions as an evaporator. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

In addition, in the refrigeration cycle device 10a of this embodiment, in other operating modes, the control device 50 fully closes the intermediate pressure expansion valve 16e, and operates in the same manner as the refrigeration cycle device 10 of the fifth embodiment. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effects as those of the fifth embodiment can be obtained.

Furthermore, in the refrigeration cycle device 10a of this embodiment, a gas injection cycle can be configured in (b) cooling mode. Therefore, in (b) cooling mode, the coefficient of performance can be further improved.

Thirteenth Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 21, a refrigeration cycle apparatus 10a in which the arrangements of an eleventh three-way joint 13k and an internal heat exchanger 26 are changed from those of the tenth embodiment will be described.

In this embodiment, the eleventh three-way joint 13k is disposed in the refrigerant passage that extends from the outlet of the fifth three-way joint 13e in the inlet-side passage 21a to the inlet of the fixed throttle 23a. Therefore, the intermediate pressure expansion valve 16e in this embodiment is a third pressure reducing section that reduces the pressure of a portion of the refrigerant upstream of the receiver 15 when switching to a predetermined operating mode (in this embodiment, the cooling mode).

In addition, the high-pressure refrigerant passage of the internal heat exchanger 26 in this embodiment is arranged in a refrigerant passage that runs from the other outlet of the sixth three-way joint 13f to the inlet of the seventh three-way joint 13g, as in the twelfth embodiment. The other configurations are the same as in the tenth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 controls the heating expansion valve 16a to be in a throttled state, the cooling expansion valve 16b to be in a fully closed state, and the intermediate pressure expansion valve 16e to be in a fully closed state.

For this reason, in the outdoor air heating mode, the refrigeration cycle device 10a is switched to the first circuit in which the refrigerant circulates, exactly like the outdoor air heating mode of the fifth embodiment. Furthermore, in the outdoor air heating mode, the control device 50 controls the operation of various controlled devices, similar to the fifth embodiment. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing out the blown air heated by the interior condenser 12 into the vehicle cabin, similar to the fifth embodiment.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state, the cooling expansion valve 16b in a throttled state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the cooling mode refrigeration cycle device 10a, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a second circuit in which the refrigerant circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → cooling expansion valve 16b → indoor evaporator 19 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant upstream of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

With this circuit configuration, the control device 50 controls the operation of various controlled devices in the same way as in the cooling mode of the 12th embodiment.

In other words, in the cooling mode, the refrigeration cycle device 10a configures an internal heat exchange type gas injection cycle in which the exterior heat exchanger 18 functions as a condenser and the interior evaporator 19 functions as an evaporator. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

In addition, in the refrigeration cycle device 10a of this embodiment, in other operating modes, the control device 50 fully closes the intermediate pressure expansion valve 16e, and operates in the same manner as the refrigeration cycle device 10 of the fifth embodiment. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effects as those of the fifth embodiment can be obtained.

Furthermore, in the refrigeration cycle device 10a of this embodiment, a gas injection cycle can be configured in (b) cooling mode. Therefore, in (b) cooling mode, the coefficient of performance can be further improved.

Fourteenth Embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 22, a refrigeration cycle apparatus 10a in which the arrangements of an eleventh three-way joint 13k and an internal heat exchanger 26 are changed from those of the tenth embodiment will be described.

In this embodiment, the eleventh three-way joint 13k is disposed in the refrigerant passage that extends from the outlet of the fifth three-way joint 13e in the inlet passage 21a to the inlet of the fixed throttle 23a. Therefore, the intermediate pressure expansion valve 16e in this embodiment is a third pressure reducing section that reduces the pressure of a portion of the refrigerant upstream of the receiver 15 when switching to a predetermined operating mode (in this embodiment, the outdoor air heating mode and the cooling mode).

In addition, the high-pressure refrigerant passage of the internal heat exchanger 26 in this embodiment is arranged in the refrigerant passage in the outlet side passage 21b that runs from the outlet of the receiver 15 to the inlet of the sixth three-way joint 13f. The rest of the configuration is the same as in the tenth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a in a throttled state, the cooling expansion valve 16b in a fully closed state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in the outdoor air heating mode, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a first circuit in which the refrigerant circulates in the following order: indoor condenser 12 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant upstream of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

With this circuit configuration, the control device 50 controls the operation of various controlled devices in the same way as in the outdoor air heating mode of the 10th embodiment.

In other words, in the refrigeration cycle device 10a in the outdoor air heating mode, an internal heat exchange type gas injection cycle is configured in which the indoor condenser 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing the ventilation air heated by the indoor condenser 12 into the vehicle interior.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state, the cooling expansion valve 16b in a throttled state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the cooling mode refrigeration cycle device 10a, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a second circuit in which the refrigerant circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → cooling expansion valve 16b → indoor evaporator 19 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant upstream of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

With this circuit configuration, the control device 50 controls the operation of various controlled devices in the same way as in the cooling mode of the 12th embodiment.

In other words, in the cooling mode, the refrigeration cycle device 10a configures an internal heat exchange type gas injection cycle in which the exterior heat exchanger 18 functions as a condenser and the interior evaporator 19 functions as an evaporator. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

In addition, in the refrigeration cycle device 10a of this embodiment, in other operating modes, the control device 50 fully closes the intermediate pressure expansion valve 16e, and operates in the same manner as the refrigeration cycle device 10 of the fifth embodiment. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effects as those of the fifth embodiment can be obtained.

Furthermore, in the refrigeration cycle device 10a, a gas injection cycle can be configured in (a) outdoor air heating mode and (b) cooling mode. Therefore, the coefficient of performance can be further improved in (a) outdoor air heating mode and (b) cooling mode.

Fifteenth embodiment
In this embodiment, as shown in the overall configuration diagram of FIG. 23, a refrigeration cycle apparatus 10a in which the arrangements of an eleventh three-way joint 13k and an internal heat exchanger 26 are changed from those of the thirteenth embodiment will be described.

In this embodiment, the eleventh three-way joint 13k is disposed in the refrigerant passage in the outlet side passage 21b that runs from the outlet of the receiver 15 to the inlet of the sixth three-way joint 13f. Therefore, the intermediate pressure expansion valve 16e in this embodiment is a third pressure reducing section that reduces the pressure of a portion of the refrigerant that flows out of the receiver 15 in a predetermined operating mode (in this embodiment, the outdoor air heating mode and the cooling mode).

In addition, the high-pressure refrigerant passage of the internal heat exchanger 26 in this embodiment is arranged in the refrigerant passage that runs from the other outlet of the eleventh three-way joint 13k in the outlet-side passage 21b to the inlet of the sixth three-way joint 13f. The rest of the configuration is the same as in the tenth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, and opens the third on-off valve 14c. Furthermore, the controller 50 sets the heating expansion valve 16a in a throttled state, the cooling expansion valve 16b in a fully closed state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in the outdoor air heating mode, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a first circuit in which the refrigerant circulates in the following order: indoor condenser 12 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → heating expansion valve 16a → outdoor heat exchanger 18 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant flowing out of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

With this circuit configuration, the control device 50 controls the operation of various controlled devices in the same way as in the outdoor air heating mode of the 10th embodiment.

In other words, in the refrigeration cycle device 10a in the outdoor air heating mode, an internal heat exchange type gas injection cycle is configured in which the indoor condenser 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing the ventilation air heated by the indoor condenser 12 into the vehicle interior.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, and closes the third on-off valve 14c. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state, the cooling expansion valve 16b in a throttled state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in cooling mode, the refrigerant discharged from the discharge port 111c of the compressor 111 is switched to a second circuit in which the refrigerant circulates in the following order: (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → fixed throttle 23a → receiver 15 → high-pressure refrigerant passage of the internal heat exchanger 26 → cooling expansion valve 16b → indoor evaporator 19 → suction port 111a of the compressor 111. Furthermore, a portion of the refrigerant flowing out of the receiver 15 flows in the following order: intermediate pressure expansion valve 16e → intermediate pressure refrigerant passage of the internal heat exchanger 26 → intermediate pressure suction port 111b of the compressor 111.

With this circuit configuration, the control device 50 controls the operation of various controlled devices in the same way as in the cooling mode of the 12th embodiment.

In other words, in the cooling mode, the refrigeration cycle device 10a configures an internal heat exchange type gas injection cycle in which the exterior heat exchanger 18 functions as a condenser and the interior evaporator 19 functions as an evaporator. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

In addition, in the refrigeration cycle device 10a of this embodiment, in other operating modes, the control device 50 fully closes the intermediate pressure expansion valve 16e, and operates in the same manner as the refrigeration cycle device 10 of the fifth embodiment. Therefore, according to the refrigeration cycle device 10a of this embodiment, the same effects as those of the fifth embodiment can be obtained.

Furthermore, in the refrigeration cycle device 10a, a gas injection cycle can be configured in (a) outdoor air heating mode and (b) cooling mode. Therefore, the coefficient of performance can be further improved in (a) outdoor air heating mode and (b) cooling mode.

Sixteenth Embodiment
In this embodiment, as shown in the overall configuration diagram of Fig. 24, an example in which the cycle configuration of the refrigeration cycle apparatus 10a is changed from that of the tenth embodiment will be described. In the refrigeration cycle apparatus 10a of this embodiment, a fourth on-off valve 14d is added, and the fixed throttle 23a, the eleventh three-way joint 13k, and the internal heat exchanger 26 are eliminated. Furthermore, in the refrigeration cycle apparatus 10a of this embodiment, the arrangement of the intermediate pressure expansion valve 16e is changed.

The fourth on-off valve 14d is a solenoid valve that opens and closes the injection passage 21e. The basic configuration of the fourth on-off valve 14d is the same as that of the first on-off valve 14a, etc. In this embodiment, the intermediate pressure expansion valve 16e is disposed in the refrigerant passage from the outlet of the fifth three-way joint 13e in the inlet side passage 21a to the inlet of the receiver 15.

Furthermore, the receiver 15 of this embodiment has a gas phase refrigerant outlet through which the separated gas phase refrigerant flows out. The gas phase refrigerant outlet of this embodiment is connected to the inlet side of the injection passage 21e. Therefore, the intermediate pressure expansion valve 16e of this embodiment is a third pressure reducing section that reduces the pressure of the refrigerant flowing into the receiver 15 when switching to a predetermined operation mode (in this embodiment, the outdoor air heating mode and the cooling mode).

The intermediate temperature sensor of this embodiment is arranged to detect the temperature of the refrigerant flowing into the intermediate pressure expansion valve 16e. The pressure sensor of this embodiment is arranged to detect the pressure of the refrigerant flowing into the intermediate pressure expansion valve 16e. The rest of the configuration of the refrigeration cycle device 10a is the same as that of the tenth embodiment.

Next, the operation of the refrigeration cycle device 10a configured as described above will be described. In the refrigeration cycle device 10a of this embodiment, the operation modes are switched in the same manner as in the first embodiment. The operation of each operation mode will be described below.

In the outdoor air heating mode, the controller 50 opens the first on-off valve 14a, closes the second on-off valve 14b, opens the third on-off valve 14c, and opens the fourth on-off valve 14d. Furthermore, the controller 50 sets the heating expansion valve 16a in a throttled state, the cooling expansion valve 16b in a fully closed state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in the outdoor air heating mode, the refrigerant discharged from the discharge port 111c of the compressor 111 flows in the order of the indoor condenser 12 → intermediate pressure expansion valve 16e → receiver 15, and the refrigerant flowing out from the liquid phase refrigerant outlet of the receiver 15 is switched to the first circuit in which it circulates in the order of the outdoor heat exchanger 18 → suction port 111a of the compressor 111. Furthermore, the refrigerant flowing out from the gas phase refrigerant outlet of the receiver 15 is sucked into the intermediate pressure suction port 111b of the compressor 111 via the injection passage 21e.

With this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the intermediate pressure expansion valve 16e, the control device 50 controls the throttle opening so that the degree of subcooling SC of the refrigerant flowing into the intermediate pressure expansion valve 16e approaches a predetermined target degree of subcooling KSC. The degree of subcooling SC is calculated using the detection signal of the intermediate temperature sensor and the detection signal of the intermediate pressure sensor. Other controls are the same as those in the outdoor air heating mode of the tenth embodiment.

In the refrigeration cycle device 10a, when the compressor 111 operates, the high-pressure refrigerant discharged from the discharge port 111c of the compressor 111 flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 condenses by releasing heat to the blown air that has passed through the indoor evaporator 19. This heats the blown air. The refrigerant that flows out of the indoor condenser 12 flows into the intermediate pressure expansion valve 16e and is reduced in pressure until it becomes an intermediate pressure refrigerant.

The intermediate pressure refrigerant decompressed by the intermediate pressure expansion valve 16e flows into the receiver 15. The refrigerant that flows into the receiver 15 is separated into gas and liquid in the receiver 15. A portion of the gas phase refrigerant separated in the receiver 15 is sucked through the intermediate pressure suction port 111b of the compressor 111 via the injection passage 21e.

A portion of the liquid phase refrigerant separated in the receiver 15 flows into the heating expansion valve 16a via the outlet side passage 21b and the second three-way joint 13b. The refrigerant that flows into the heating expansion valve 16a is reduced in pressure until it becomes a low-pressure refrigerant.

The low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18. The refrigerant that flows into the outdoor heat exchanger 18 absorbs heat from the outside air and evaporates. The refrigerant that flows out of the outdoor heat exchanger 18 passes through the third three-way joint 13c, the suction side passage 21d, and the fourth three-way joint 13d, is sucked into the suction port 111a of the compressor 111, and is compressed again.

In other words, in the refrigeration cycle device 10a in the outdoor air heating mode, a gas injection cycle with a gas-liquid separation system is configured in which the indoor condenser 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator. Therefore, in the outdoor air heating mode, the interior of the vehicle can be heated by blowing the ventilation air heated by the indoor condenser 12 into the vehicle interior.

(b) Cooling Mode In the cooling mode, the control device 50 closes the first on-off valve 14a, opens the second on-off valve 14b, closes the third on-off valve 14c, and opens the fourth on-off valve 14d. Furthermore, the control device 50 puts the heating expansion valve 16a in a fully open state, the cooling expansion valve 16b in a throttled state, and the intermediate pressure expansion valve 16e in a throttled state.

As a result, in the refrigeration cycle device 10a in cooling mode, the refrigerant discharged from the compressor 111 flows in the order of (indoor condenser 12 → heating expansion valve 16a →) outdoor heat exchanger 18 → intermediate pressure expansion valve 16e → receiver 15, and the refrigerant flowing out from the liquid phase refrigerant outlet of the receiver 15 is switched to the second circuit in which it circulates in the order of cooling expansion valve 16b → indoor evaporator 19 → suction port 111a of the compressor 111. Furthermore, the refrigerant flowing out from the gas phase refrigerant outlet of the receiver 15 is sucked into the intermediate pressure suction port 111b of the compressor 111 via the injection passage 21e.

In this circuit configuration, the control device 50 controls the operation of various controlled devices. For example, for the intermediate pressure expansion valve 16e, the control device 50 controls the throttle opening so that the degree of subcooling SC of the refrigerant flowing into the intermediate pressure expansion valve 16e approaches the target degree of subcooling KSC, as in the outdoor air heating mode. Other controls are the same as in the cooling mode of the twelfth embodiment.

In other words, in the cooling mode, the refrigeration cycle device 10a configures a gas-liquid separation type gas injection cycle in which the exterior heat exchanger 18 functions as a condenser and the interior evaporator 19 functions as an evaporator. Therefore, in the cooling mode, the interior of the vehicle can be cooled by blowing the ventilation air cooled by the interior evaporator 19 into the vehicle cabin.

In addition, in the refrigeration cycle apparatus 10a of this embodiment, in other operation modes, the control device 50 closes the fourth on-off valve 14d to operate the refrigeration cycle apparatus 10 in the same manner as the refrigeration cycle apparatus 10 of the fifth embodiment. Therefore, the refrigeration cycle apparatus 10a of this embodiment can provide the same effects as the fifth embodiment. Furthermore, in the refrigeration cycle apparatus 10a, a gas injection cycle can be configured in (a) outdoor air heating mode and (b) cooling mode. Therefore, in (a) outdoor air heating mode and (b) cooling mode, the coefficient of performance can be further improved.

Other Embodiments
The present invention is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present invention.

(1) In the above embodiment, an example was described in which the refrigeration cycle device 10 was applied to an air conditioner with an in-vehicle equipment cooling function, but the application of the refrigeration cycle device 10 is not limited to this. It may also be applied to a stationary air conditioner, etc., without being limited to use in a vehicle. For example, it may be applied to an air conditioner with a server temperature adjustment function that cools a computer that functions as a server and also conditions the air in the room in which the server is housed.

In the above embodiment, the battery 30 is used as the in-vehicle device, but the present invention is not limited to this. For example, an in-vehicle device that generates heat during operation, such as a motor generator, a power control unit (PCU), or a control device for an advanced driver assistance system (ADAS), may be used.

The refrigeration cycle device 10 may also be applied to an air conditioning device that does not have a cooling function, such as an in-vehicle device. In this case, the seventh three-way joint 13g, the cooling expansion valve 16c, and the eighth three-way joint 13h may be eliminated.

(2) The components of the refrigeration cycle device 10, 10a are not limited to those disclosed in the above embodiment.

For example, in the above embodiment, an example was described in which the indoor condenser 12 is used as a heating section that heats the blown air using a high-pressure refrigerant as a heat source, but the present invention is not limited to this. For example, as shown in FIG. 25, a heating section may be formed by adding a high-temperature side heat medium circuit 60 that circulates a high-temperature side heat medium to the refrigeration cycle device 10 described in the first embodiment.

More specifically, the high-temperature side heat medium circuit 60 may include a high-temperature side water pump 61, a heat medium-refrigerant heat exchanger 62, a heater core 63, etc.

The heat medium-refrigerant heat exchanger 62 is a heat dissipation section that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the high-temperature side heat medium, dissipating heat from the high-pressure refrigerant. The high-temperature side water pump 61 is an electric pump that pumps the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 60 to the heat medium-refrigerant heat exchanger 62. The high-temperature side water pump 61 has its rotation speed (i.e., water pumping capacity) controlled by a control signal output from the control device 50. The heater core 63 is a heat exchange section that exchanges heat between the heat medium heated in the heat medium-refrigerant heat exchanger and the blown air, heating the blown air.

In addition, for example, in the above embodiment, an example was described in which a direct-cooling type battery cooling section (in other words, a cooling section for vehicle-mounted equipment) is used in which heat is exchanged between the low-pressure refrigerant decompressed by the cooling expansion valve 16c and the battery 30, but this is not limited to the above. For example, as shown in FIG. 25, a cooling section for vehicle-mounted equipment may be formed by adding a low-temperature side heat medium circuit 70.

More specifically, the low-temperature side heat medium circuit 70 may include a low-temperature side water pump 71, a chiller 72, a heat medium passage for the on-board equipment (in FIG. 25, the refrigerant passage 30a for the battery 30), etc.

The chiller 72 is an evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 16c and the low-temperature heat medium to evaporate the low-pressure refrigerant. The low-temperature water pump 71 is an electric pump that pumps the low-temperature heat medium circulating in the low-temperature heat medium circuit 70 to the heat medium passage of the on-board equipment. The basic configuration of the low-temperature water pump 71 is the same as that of the high-temperature water pump 61.

When the low-temperature heat medium circuit 70 is employed, for example, in (d) battery only mode, the control device 50 may control the aperture of the cooling expansion valve 16c so that the temperature of the low-temperature heat medium flowing out of the chiller 72 approaches a predetermined reference heat medium temperature. This is also true in (e) outdoor air waste heat heating mode, (f) cooling battery mode, (g) outdoor air waste heat parallel dehumidification heating mode, etc.

Furthermore, as the high-temperature side heat medium or the low-temperature side heat medium, a solution containing ethylene glycol, dimethylpolysiloxane, nanofluid, etc., an antifreeze, an aqueous liquid medium containing alcohol, etc., a liquid medium containing oil, etc., etc. can be used.

In addition, each component included in the refrigerant circuit switching unit may be integrated, such as the integrated valve 24 described in the sixth embodiment.

For example, a first three-way valve may be used that integrates the first on-off valve 14a, the second on-off valve 14b, and the first three-way joint 13a that constitute the first switching unit 22a. For example, a second three-way valve may be used that integrates the third on-off valve 14c and the third three-way joint 13c that constitute the second switching unit 22b.

Furthermore, as in the integrated valve 24 of the sixth embodiment, the heating expansion valve 16a and the above-mentioned second three-way valve may be integrated. Similarly, the heating expansion valve 16a and the above-mentioned first three-way valve may be integrated.

In the fifth embodiment described above, a fixed throttle is used as each of the reservoir side pressure reduction sections 23a to 23b, but this is not limiting. A variable throttle mechanism may be used as each of the reservoir side pressure reduction sections 23a to 23b.

An evaporation pressure regulating valve may be added to the refrigeration cycle device 10 described in the above embodiment. The evaporation pressure regulating valve is a pressure regulating valve that maintains the refrigerant pressure upstream of it at or above a predetermined reference pressure. As such an evaporation pressure regulating valve, a mechanical variable throttle mechanism that increases the valve opening in response to an increase in the pressure of the refrigerant on the outlet side of the evaporation section may be used.

For example, an evaporation pressure adjustment valve may be added between the refrigerant outlet of the indoor evaporator 19 and one of the inlets of the eighth three-way joint 13h. This allows the refrigerant evaporation temperature in the indoor evaporator 19 to be maintained at a temperature at which frost formation can be suppressed (e.g., 0°C or higher), thereby suppressing frost formation on the indoor evaporator 19.

In the above-described eighth embodiment, a refrigeration cycle device 10 was described that includes an interior evaporator 19, a rear interior evaporator 19a, and a refrigerant passage 30a of the battery 30, which are connected in parallel to each other with respect to the refrigerant flow as the evaporating section. The connection manner of the interior evaporator 19, the rear interior evaporator 19a, and the refrigerant passage 30a of the battery 30 is not limited to the example disclosed in the eighth embodiment.

For example, in the eighth embodiment, one of the refrigerants branched at the seventh three-way joint 13g flows into the interior evaporator 19 via the cooling expansion valve 16b, and the other refrigerant flows into the ninth three-way joint 13i. Then, one of the refrigerants branched at the ninth three-way joint 13i flows into the refrigerant passage 30a of the battery 30 via the cooling expansion valve 16c, and the other refrigerant flows into the rear interior evaporator 19a via the rear cooling expansion valve 16d.

Alternatively, one of the refrigerants branched at the seventh three-way joint 13g may be allowed to flow into the refrigerant passage 30a of the battery 30 via the cooling expansion valve 16c, and the other refrigerant may be allowed to flow into the ninth three-way joint 13i. Then, one of the refrigerants branched at the ninth three-way joint 13i may be allowed to flow into the interior evaporator 19 via the cooling expansion valve 16b, and the other refrigerant may be allowed to flow into the rear interior evaporator 19a via the rear cooling expansion valve 16d.

For example, in the eighth embodiment, the refrigerant flowing out of the refrigerant passage 30a of the battery 30 and the refrigerant flowing out of the rear interior evaporator 19a are joined at the tenth three-way joint 13j. The refrigerant flowing out of the interior evaporator 19 and the refrigerant flowing out of the tenth three-way joint 13j are joined at the eighth three-way joint 13h.

Alternatively, the refrigerant flowing out of the interior evaporator 19 and the refrigerant flowing out of the rear interior evaporator 19a may be joined at the tenth three-way joint 13j. The refrigerant flowing out of the refrigerant passage 30a of the battery 30 and the refrigerant flowing out of the tenth three-way joint 13j may be joined at the eighth three-way joint 13h.

Furthermore, as shown in FIG. 26, a first four-way joint 27a may be arranged upstream of the refrigerant flow of the refrigerant passage 30a of the interior evaporator 19, the rear interior evaporator 19a, and the battery 30, and the refrigerant flow may be branched at the first use joint 27a. Also, a second four-way joint 27b may be arranged downstream of the refrigerant flow of the refrigerant passage 30a of the interior evaporator 19, the rear interior evaporator 19a, and the battery 30, and the refrigerant flow flowing out of the evaporation section may be merged at the second four-way joint 27b.

In this way, by changing the connection state of the interior evaporator 19, the rear interior evaporator 19a, and the downstream side of the refrigerant flow of the refrigerant passage 30a of the battery 30, the freedom of arrangement of the above-mentioned evaporation pressure adjustment valve can be improved.

In addition, in the above-mentioned tenth to sixteenth embodiments, a compressor 111 is used in which two compression mechanisms are housed in one housing, but the two-stage boost type compressor that can be applied to the tenth to sixteenth embodiments is not limited to this.

For example, if the intermediate pressure refrigerant flowing in from the intermediate pressure intake port 111b can be merged with the refrigerant undergoing the compression process from low pressure to high pressure, the compressor may be an electric compressor configured with a fixed displacement compression mechanism and an electric motor that rotates and drives the compression mechanism housed inside the housing.

Furthermore, a two-stage boost compressor may be constructed by connecting two compressors, a low-stage compressor and a high-stage compressor, in series. In this case, the suction port of the low-stage compressor located on the low-stage side is the suction port 111a of the two-stage boost compressor as a whole. The discharge port of the high-stage compressor located on the high-stage side is the discharge port 111c of the two-stage boost compressor as a whole. Furthermore, an intermediate pressure suction port 111b of the two-stage boost compressor as a whole may be provided in the refrigerant passage connecting the discharge port of the low-stage compressor and the suction port of the high-stage compressor.

In addition, in the above tenth to sixteenth embodiments, an example was described in which an electrically operated variable throttle mechanism was used as the intermediate pressure expansion valve 16e, but this is not limited thereto.

For example, in the tenth to fifteenth embodiments, the intermediate pressure expansion valve 16e may be a thermostatic expansion valve that changes the throttle opening so that the superheat degree SH5 of the refrigerant drawn into the intermediate pressure suction port 111b of the compressor 111 approaches the target superheat degree KSH5. Furthermore, in addition to the thermostatic expansion valve, a fourth opening/closing valve 14d that opens and closes the injection passage 21e may be provided.

For example, in the sixteenth embodiment, a high-pressure control valve may be used as the intermediate pressure expansion valve 16e. The high-pressure control valve is a mechanical variable throttle mechanism that changes the throttle opening so that the pressure of the high-pressure refrigerant flowing into the intermediate pressure expansion valve 16e becomes a target high pressure determined according to the temperature of the high-pressure refrigerant. Furthermore, in addition to the high-pressure control valve, a fourth opening/closing valve 14d that opens and closes the injection passage 21e may be provided.

In the above embodiment, an example was described in which R1234yf was used as the refrigerant, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be used. Alternatively, a mixed refrigerant made by mixing two or more of these refrigerants may be used.

(3) In the above ninth embodiment, an example of the arrangement of the internal heat exchanger 26 in the refrigeration cycle device 10 was described, but the arrangement of the internal heat exchanger 26 is not limited to this.

For example, as shown in the overall configuration diagram of FIG. 27, the high-pressure refrigerant passage 26a may be arranged in the refrigerant passage leading from the outlet of the receiver 15 to the inlet of the sixth three-way joint 13f (area HA in FIG. 27). The high-pressure refrigerant passage 26a may also be arranged in the refrigerant passage leading from the other outlet of the sixth three-way joint 13f to the inlet of the seventh three-way joint 13g (area HB in FIG. 27). The high-pressure refrigerant passage 26a may also be arranged in the outlet side passage 21b leading from one outlet of the sixth three-way joint 13f to the other inlet of the second three-way joint 13b (area HC in FIG. 27).

On the other hand, the low-pressure refrigerant passage 26b may be arranged in the refrigerant passage extending from the outlet of the fourth three-way joint 13d to the suction port of the compressor 11 (area LA in FIG. 27). Also, the low-pressure refrigerant passage 26b may be arranged in the refrigerant passage extending from the outlet of the eighth three-way joint 13h to the other inlet of the fourth three-way joint 13d (area LB in FIG. 27).

In other words, the internal heat exchanger 26 needs to be positioned so that it can exchange heat between the refrigerant that flows out of the receiver 15 and before it is decompressed by the heating expansion valve 16a, the cooling expansion valve 16b, the cooling expansion valve 16c, and the rear cooling expansion valve 16d, and the refrigerant that flows out of the heat exchanger that functions as an evaporator and before it is sucked into the compressor 11.

(4) In the refrigeration cycle device 10a described in the tenth to sixteenth embodiments above, an example was described in which the refrigerant circuit is switched to form a gas injection cycle in (a) outdoor air heating mode or (b) cooling mode, but this is not limiting.

For example, in the refrigeration cycle device 10a described in the thirteenth embodiment, (d) in the battery only mode, the intermediate pressure expansion valve 16e may be throttled to configure a gas injection cycle. In other operating modes, the gas injection cycle may also be configured to the extent possible.

(5) The control sensors are not limited to those disclosed in the above embodiments.

For example, a pressure detector that detects the pressure of the refrigerant flowing out of the second three-way joint 13b and into the heating expansion valve 16a, and a temperature detector that detects the temperature of the refrigerant may be used. The detection signals of these detectors can be used to estimate the flow rate of the refrigerant circulating in the cycle.

A pressure detection unit that detects the pressure of the refrigerant flowing out of the heating expansion valve 16a and into the outdoor heat exchanger 18, and a temperature detection unit that detects the temperature of the refrigerant may also be used. The detection signals of these detection units can be used to estimate the flow rate of the refrigerant circulating in the cycle.

In addition, a pressure detector that detects the pressure of the refrigerant flowing through the refrigerant passage from the outlet of the third on-off valve 14c in the suction side passage 21d to one inlet of the fourth three-way joint 13d, and a temperature detector that detects the temperature of the refrigerant may be employed. The detection signals of these detectors can be used to detect the state of the refrigerant on the outlet side of the outdoor heat exchanger 18.

A pressure detection unit may also be used to detect the pressure of the refrigerant flowing into or out of the receiver 15. The detection signal of these detection units can be used to detect the pressure inside the receiver 15.

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing through the refrigerant passage from the other outlet of the third three-way joint 13c to the other inlet of the fifth three-way joint 13e, and a temperature detection unit that detects the temperature of the refrigerant may be used. The detection signals of these detection units can be used to detect the state of the refrigerant flowing out of the outdoor heat exchanger 18.

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing through the refrigerant passage from one outlet of the first three-way joint 13a to one inlet of the fifth three-way joint 13e in the inlet-side passage 21a, and a temperature detection unit that detects the temperature of the refrigerant may be employed. The detection signals of these detection units can be used to detect the state of the refrigerant on the outlet side of the indoor condenser 12.

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out of the seventh three-way joint 13g and into the cooling expansion valve 16b, and a temperature detection unit that detects the temperature of the refrigerant may be used. The detection signals of these detection units can be used to estimate the refrigerant flow rate flowing through the indoor evaporator 19, etc.

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out of the cooling expansion valve 16b and into the indoor evaporator 19, and a temperature detection unit that detects the temperature of the refrigerant may be used. The detection signals of these detection units can be used to estimate the flow rate of the refrigerant flowing through the indoor evaporator 19, etc.

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out of the indoor evaporator 19 and into the eighth three-way joint 13h, and a temperature detection unit that detects the temperature of the refrigerant may be used. The detection signals of these detection units can be used to detect the state of the refrigerant on the outlet side of the indoor evaporator 19.

In addition, a pressure detector that detects the pressure of the refrigerant flowing out of the seventh three-way joint 13g and into the cooling expansion valve 16c, and a temperature detector that detects the temperature of the refrigerant may be used. The detection signals of these detectors can be used to estimate the flow rate of the refrigerant flowing through the refrigerant passage 30a of the battery 30 (or the refrigerant passage of the chiller 72).

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out of the cooling expansion valve 16c and into the refrigerant passage 30a of the battery 30 (or into the refrigerant passage of the chiller 72), and a temperature detection unit that detects the temperature of the refrigerant may be employed. The detection signals of these detection units can be used to estimate the flow rate of the refrigerant flowing through the refrigerant passage 30a of the battery 30 (or into the refrigerant passage of the chiller 72).

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out of the refrigerant passage 30a of the battery 30 (or the refrigerant passage of the chiller 72) and flowing into the eighth three-way joint 13h, and a temperature detection unit that detects the temperature of the refrigerant may be employed. The detection signals of these detection units can be used to detect the state of the refrigerant on the outlet side of the refrigerant passage 30a of the battery 30 (or the refrigerant passage of the chiller 72).

In addition, a pressure detection unit that detects the pressure of the refrigerant flowing out from the outlet of the fourth three-way joint 13d and sucked into the suction port of the compressor 11 or the suction port 111a of the compressor 111, and a temperature detection unit that detects the temperature of the refrigerant may be used. The detection signals of these detection units can be used to detect the state of the refrigerant sucked into the compressors 11 and 111.

(6) Furthermore, the means disclosed in each of the above embodiments may be combined as appropriate to the extent feasible.

For example, the liquid storage side pressure reducing sections 23a to 23b described in the fifth embodiment may be applied to the refrigeration cycle devices 10 described in the second to fourth and seventh to ninth embodiments. For example, the integrated valve 24 described in the sixth embodiment may be applied to the refrigeration cycle devices 10, 10a described in the second to fourth and seventh to sixteenth embodiments.

Furthermore, the refrigeration cycle device 10a described in the tenth to sixteenth embodiments may be added with a rear cooling expansion valve 16d and a rear indoor evaporator 19a, as in the eighth embodiment. Furthermore, in the refrigeration cycle device 10a described in the tenth to sixteenth embodiments, as described with reference to FIG. 25, the heating section may be formed by the high-temperature side heat medium circuit 60, and the cooling section may be formed by the low-temperature side heat medium circuit 70.

10, 10a refrigeration cycle device 11, 111 compressor 12 indoor condenser (heat dissipation section)
13a to 13k: first to eleventh three-way joints; 14a to 14d: first to fourth on-off valves (refrigerant circuit switching unit)
15 Receiver (liquid storage section)
16a Heating expansion valve (first pressure reducing section)
16b to 16d Cooling expansion valve, cooling expansion valve, rear cooling expansion valve (second pressure reducing section)
16e Intermediate pressure expansion valve (third pressure reducing section)
19, 19a Indoor evaporator, rear indoor evaporator (evaporation section)
30a, 72 Refrigerant passage, chiller (evaporation section)
22a, 22b First switching unit, second switching unit

Claims (16)

A compressor (11) that compresses and discharges a refrigerant;
a heat dissipation section (12, 62) that dissipates heat from the refrigerant discharged from the compressor;
A liquid storage section (15) for storing surplus refrigerant in the cycle;
A first pressure reducing section (16a) for reducing the pressure of the refrigerant;
an outdoor heat exchanger (18) for exchanging heat between the refrigerant flowing out of the first pressure reducing section and outside air;
A second pressure reducing section (16b to 16d) for reducing the pressure of the refrigerant;
an evaporation section (19, 19a, 30a, 72) that evaporates the refrigerant decompressed by the second decompression section;
A refrigerant circuit switching unit (14a to 14c) that switches the refrigerant circuit,
The refrigerant circuit switching unit is
a first circuit that causes the refrigerant flowing out of the heat dissipation section to flow into the liquid storage section, causes the refrigerant flowing out of the liquid storage section to flow into the first pressure reduction section, and further causes the refrigerant decompressed in the first pressure reduction section to flow into the outdoor heat exchanger;
a second circuit that allows the refrigerant flowing out of the outdoor heat exchanger to flow into the liquid storage section, allows the refrigerant flowing out of the liquid storage section to flow into the second pressure reduction section, and further allows the refrigerant decompressed in the second pressure reduction section to flow into the evaporation section;
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit such that a flow direction of the refrigerant in the outdoor heat exchanger when the refrigerant circuit is switched to the first circuit coincides with a flow direction of the refrigerant in the outdoor heat exchanger when the refrigerant circuit is switched to the second circuit ,
the refrigerant circuit switching unit has a first switching unit (22a) that guides the refrigerant discharged from the compressor to at least one of the liquid storage unit side and the outdoor heat exchanger side, a joint unit (13b) that guides at least one of the refrigerant flowing out of the first switching unit and the refrigerant flowing out of the liquid storage unit to the outdoor heat exchanger side, and a second switching unit (22b) that guides the refrigerant flowing out of the outdoor heat exchanger to at least one of the suction port side of the compressor and the liquid storage unit side,
A refrigeration cycle device in which the first pressure reduction section and the second switching section are integrated to enable heat exchange between the refrigerant flowing into the first pressure reduction section and the refrigerant guided from the second switching section to the suction port side of the compressor . The refrigeration cycle device according to claim 1, further comprising a liquid storage side pressure reducing section (23a to 23c) for reducing the pressure of the refrigerant flowing into the liquid storage section. A compressor (11) that compresses and discharges a refrigerant;
a heat dissipation section (12, 62) that dissipates heat from the refrigerant discharged from the compressor;
A liquid storage section (15) for storing surplus refrigerant in the cycle;
A first pressure reducing section (16a) for reducing the pressure of the refrigerant;
an outdoor heat exchanger (18) for exchanging heat between the refrigerant flowing out of the first pressure reducing section and outside air;
A second pressure reducing section (16b to 16d) for reducing the pressure of the refrigerant;
an evaporation section (19, 19a, 30a, 72) that evaporates the refrigerant decompressed by the second decompression section;
a refrigerant circuit switching unit (14a to 14c) that switches between refrigerant circuits;
A liquid storage portion side pressure reducing portion ( 23a ) that reduces the enthalpy of the refrigerant in the liquid storage portion by reducing the pressure of the refrigerant flowing into the liquid storage portion,
The refrigerant circuit switching unit is
a first circuit that allows the refrigerant discharged from the compressor to flow into the heat radiating section, allows the refrigerant flowing out from the heat radiating section to flow into the liquid storage section side pressure reducing section, allows the refrigerant depressurized in the liquid storage section side pressure reducing section to flow into the liquid storage section, allows the refrigerant flowing out from the liquid storage section to flow into the first pressure reducing section, and further allows the refrigerant depressurized in the first pressure reducing section to flow into the outdoor heat exchanger;
a second circuit that allows the refrigerant discharged from the compressor to flow into the outdoor heat exchanger, allows the refrigerant flowing out from the outdoor heat exchanger to flow into the liquid storage section side pressure reduction section, allows the refrigerant depressurized in the liquid storage section side pressure reduction section to flow into the liquid storage section, allows the refrigerant flowing out from the liquid storage section to flow into the second pressure reduction section, and further allows the refrigerant depressurized in the second pressure reduction section to flow into the evaporation section,
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit so that a flow direction of the refrigerant in the outdoor heat exchanger when switched to the first circuit coincides with a flow direction of the refrigerant in the outdoor heat exchanger when switched to the second circuit, and switches the refrigerant circuit so that a flow direction of the refrigerant in the liquid storage section side decompression section when switched to the first circuit coincides with a flow direction of the refrigerant in the liquid storage section side decompression section when switched to the second circuit,
The liquid storage side pressure reducing unit reduces the pressure of the refrigerant flowing into the liquid storage unit regardless of whether the refrigerant circuit switching unit is switching to the first circuit or the second circuit. The refrigerant circuit switching unit is
a first switching unit (22a) that guides the refrigerant discharged from the compressor to at least one of the liquid storage unit side and the outdoor heat exchanger side;
a joint portion (13b) that guides at least one of the refrigerant flowing out from the first switching portion and the refrigerant flowing out from the liquid storage portion to the outdoor heat exchanger;
4. The refrigeration cycle apparatus according to claim 3 , further comprising: a second switching portion (22b) that guides the refrigerant flowing out from the outdoor heat exchanger to at least one of a suction port side of the compressor and a liquid storage portion side. The first switching portion guides the refrigerant flowing out from the heat dissipation portion to at least one of the liquid storage portion side and the joint portion side,
The refrigeration cycle apparatus according to claim 1 , wherein the joint portion guides at least one of the refrigerant flowing out of the first switching portion and the refrigerant flowing out of the liquid storage portion to the first pressure reduction portion. The first switching unit guides the refrigerant discharged from the compressor to at least one of the heat dissipation unit side and the joint unit side,
The refrigeration cycle apparatus according to claim 1 , wherein the joint portion guides at least one of the refrigerant flowing out of the first switching portion and the refrigerant flowing out of the liquid storage portion to the first pressure reduction portion. The first switching unit guides the refrigerant discharged from the compressor to at least one of the heat dissipation unit side and the joint unit side,
5. The refrigeration cycle apparatus according to claim 1, wherein the joint portion guides at least one of the refrigerant flowing out of the first switching portion and the refrigerant flowing out of the first pressure reducing portion to the outdoor heat exchanger side. The first switching portion guides the refrigerant flowing out from the heat dissipation portion to at least one of the liquid storage portion side and the joint portion side,
5. The refrigeration cycle apparatus according to claim 1, wherein the joint portion guides at least one of the refrigerant flowing out of the first switching portion and the refrigerant flowing out of the first pressure reducing portion to the outdoor heat exchanger side. 9. The refrigeration cycle device according to claim 1, further comprising an internal heat exchanger (26) for exchanging heat between the refrigerant that has flowed out of the liquid storage section and before it is depressurized in at least one of the first depressurization section and the second depressurization section, and the refrigerant that has flowed out of the evaporator section and before it is sucked into the compressor. 3. The refrigeration cycle device according to claim 2, wherein the liquid storage side pressure reduction section includes a first liquid storage side pressure reduction section (23b) that reduces the pressure of the refrigerant flowing into the liquid storage section when the refrigerant circuit switching section is switched to the first circuit. The refrigeration cycle device according to claim 2 or 10, wherein the liquid storage side pressure reduction section includes a second liquid storage side pressure reduction section (23c) that reduces the pressure of the refrigerant flowing into the liquid storage section when the refrigerant circuit switching section is switched to the second circuit . a compressor (111) having a suction port (111a) for sucking a low-pressure refrigerant, an intermediate-pressure suction port (111b) for sucking an intermediate-pressure refrigerant, and a discharge port (111c) for discharging a compressed refrigerant;
a heat dissipation section (12, 62) that dissipates heat from the refrigerant discharged from the discharge port;
A liquid storage section (15) for storing surplus refrigerant in the cycle;
A first pressure reducing section (16a) for reducing the pressure of the refrigerant;
an outdoor heat exchanger (18) for exchanging heat between the refrigerant flowing out of the first pressure reducing section and outside air;
A second pressure reducing section (16b to 16d) for reducing the pressure of the refrigerant;
an evaporation section (19, 19a, 30a, 72) that evaporates the refrigerant decompressed by the second decompression section;
a third pressure reducing section (16e) for reducing the pressure of at least a portion of either the refrigerant on the upstream side of the liquid storage section or the refrigerant flowing out of the liquid storage section, and causing the refrigerant to flow toward the intermediate pressure suction port;
A refrigerant circuit switching unit (14a to 14d) that switches the refrigerant circuit,
The refrigerant circuit switching unit is
a first circuit that causes the refrigerant flowing out of the heat dissipation section to flow into the liquid storage section, causes the refrigerant flowing out of the liquid storage section to flow into the first pressure reduction section, and causes the refrigerant decompressed in the first pressure reduction section to flow into the outdoor heat exchanger;
a second circuit that allows the refrigerant flowing out of the outdoor heat exchanger to flow into the liquid storage section, allows the refrigerant flowing out of the liquid storage section to flow into the second pressure reduction section, and allows the refrigerant decompressed in the second pressure reduction section to flow into the evaporation section,
the refrigerant circuit switching unit, when switching to at least one of the first circuit and the second circuit, switches to a refrigerant circuit that draws the refrigerant decompressed by the third decompression unit from the intermediate pressure suction port,
Furthermore, the refrigerant circuit switching unit switches the refrigerant circuit such that a flow direction of the refrigerant in the outdoor heat exchanger when the refrigerant circuit is switched to the first circuit coincides with a flow direction of the refrigerant in the outdoor heat exchanger when the refrigerant circuit is switched to the second circuit ,
the refrigerant circuit switching unit has a first switching unit (22a) that guides the refrigerant discharged from the compressor to at least one of the liquid storage unit side and the outdoor heat exchanger side, a joint unit (13b) that guides at least one of the refrigerant flowing out of the first switching unit and the refrigerant flowing out of the liquid storage unit to the outdoor heat exchanger side, and a second switching unit (22b) that guides the refrigerant flowing out of the outdoor heat exchanger to at least one of the suction port side of the compressor and the liquid storage unit side,
A refrigeration cycle device in which the first pressure reduction section and the second switching section are integrated to enable heat exchange between the refrigerant flowing into the first pressure reduction section and the refrigerant guided from the second switching section to the suction port side of the compressor . The refrigeration cycle device according to claim 12, further comprising an internal heat exchanger (26) for exchanging heat between the refrigerant flowing out of the liquid storage section and the refrigerant decompressed in the third decompression section. The refrigerant circuit switching unit switches to a refrigerant circuit in which, in the first circuit, the refrigerant flowing out from the outdoor heat exchanger is drawn through the suction port, and the refrigerant decompressed in the third decompression unit is drawn through the intermediate pressure suction port. The refrigerant cycle device according to claim 12 or 13. The refrigerant circuit switching unit switches to a refrigerant circuit in which, in the second circuit, the refrigerant flowing out of the evaporator is drawn through the suction port, and the refrigerant decompressed in the third decompressor is drawn through the intermediate pressure suction port. The refrigerant cycle device according to claim 12 or 13. The refrigeration cycle device according to claim 12, wherein when the refrigerant circuit switching unit switches to at least one of the first circuit and the second circuit, the refrigerant circuit switching unit switches to a refrigerant circuit in which the refrigerant depressurized in the third depressurization unit flows into the liquid storage unit and the gas-phase refrigerant flowing out of the liquid storage unit is sucked in through the intermediate pressure suction port.

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