JP5846094B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus applied to an air conditioner.

  In Patent Document 1, using a heat pump system configured by a receiver cycle, a cooling mode for cooling the blown air blown into the air-conditioning target space by the indoor evaporator, and the dehumidified air by cooling the blown air by the indoor evaporator, A refrigeration cycle apparatus that performs a dehumidifying and heating mode in which dehumidified blown air is heated by an indoor condenser is disclosed.

  In this refrigeration cycle device, in the cooling mode, the refrigerant is switched to a refrigerant circuit in which refrigerant flows in the order of compressor → outdoor condenser (outdoor heat exchanger) → receiver → expansion valve → indoor evaporator → compressor. It is configured to be switched to a refrigerant circuit through which refrigerant flows in the order of compressor → indoor condenser → receiver → expansion valve → indoor evaporator → compressor.

Japanese Patent No. 3929606

  By the way, for the refrigeration cycle apparatus of Patent Document 1, it is desired to improve the performance in the cooling mode.

  Further, in the refrigeration cycle apparatus of Patent Document 1, since only two of the indoor evaporator and the indoor condenser are used in the dehumidifying heating mode, there is a problem that the temperature adjustable range of the blown air into the room is narrow. That is, if the heat absorption amount of the indoor evaporator is determined so that desired dehumidification is performed by the indoor evaporator, the heat dissipation amount of the indoor condenser cannot be adjusted, and therefore the temperature of the blown air after passing through the indoor condenser cannot be adjusted.

  In view of the above points, the present invention is a refrigeration cycle apparatus that switches between a cooling mode and a heating mode in a receiver cycle, and can perform a cooling mode that has higher cooling performance than the above-described conventional refrigeration cycle apparatus. A first object is to provide a refrigeration cycle apparatus.

  Furthermore, in addition to the first object, when performing the dehumidifying heating mode in the receiver cycle, the refrigeration cycle apparatus having a wide temperature adjustable range of the blown air to the air-conditioning target space compared to the above-described conventional refrigeration cycle apparatus The second object is to provide the above.

In order to achieve the first object, the invention according to claim 1 is applied to an air conditioner that performs a cooling mode for cooling the blown air blown into the air-conditioning target space and a heating mode for heating the blown air. A refrigeration cycle apparatus,
On the upstream side of the refrigerant flow with respect to the second outdoor heat exchange unit, the first outdoor heat exchange unit and order changing means (13, 132, 133, 200) for changing the order in which the refrigerant flows through the receiver,
In the heating mode, the order changer has the receiver first in the heating mode, the first outdoor heat exchange unit after, and in the cooling mode, the first outdoor heat exchange unit first and the receiver behind,
In the heating mode, the refrigerant is in the order of the compressor, the radiator, the receiver, the first pressure reducing means, the first outdoor heat exchanger, the second outdoor heat exchanger, or the bypass passage (23, 25) that bypasses the second outdoor heat exchanger. Is switched to the refrigerant circuit through which
In the cooling mode, it is configured to be able to switch to a refrigerant circuit through which refrigerant flows in the order of compressor → first outdoor heat exchange unit → receiver → second outdoor heat exchange unit → second decompression means → evaporator. .

  According to this, by providing the order changing means, it is possible to perform switching of the refrigerant circuit in such heating and cooling modes. In the cooling mode, the refrigerant is allowed to flow in the order of the first outdoor heat exchange unit → the receiver → the second outdoor heat exchange unit, so that the liquid-phase refrigerant separated by the receiver is cooled by the second outdoor heat exchange unit. Therefore, the cooling performance can be improved.

  Therefore, according to the present invention, it is possible to provide a refrigeration cycle apparatus capable of implementing a cooling mode having higher cooling performance than the above-described conventional refrigeration cycle apparatus.

In order to achieve the second object, in the invention according to claim 2, in the refrigeration cycle apparatus according to claim 1, the air conditioner cools and dehumidifies the blown air, and heats the dehumidified blown air. The dehumidifying and heating mode is performed, and both the first and second decompression means are configured by a variable throttle mechanism that can change the throttle opening degree.
The order change means is configured so that the refrigerant flows in the first dehumidifying and heating mode with the receiver first and the first outdoor heat exchanging unit after, and in the second dehumidifying and heating mode, the first outdoor heat exchanging unit first and the receiver. After
In the first dehumidifying and heating mode, the compressor → the radiator → the receiver → the first pressure reducing means → the first outdoor heat exchange part → the second outdoor heat exchange part or the bypass path bypassing the second outdoor heat exchange part → second pressure reducing means → Switched to the refrigerant circuit where the refrigerant flows in the order of the evaporator,
In the second dehumidifying and heating mode, switching to the refrigerant circuit in which the refrigerant flows in the order of the compressor, the radiator, the first decompression means, the first outdoor heat exchange section, the receiver, the second outdoor heat exchange section, the second decompression means, and the evaporator. It is configured to be possible.

  According to this, at the time of the 1st and 2nd dehumidification heating mode, it is set as the refrigerant circuit with which the radiator, the 1st outdoor heat exchange part, and the evaporator were connected in series at least with respect to the refrigerant | coolant flow. For this reason, in the first and second dehumidifying and heating modes, the first and second decompression means adjust the pressure of the refrigerant flowing into the outdoor heat exchanger, so that the amount of heat absorbed or released by the first outdoor heat exchange unit is adjusted. The amount of heat can be adjusted. As a result, even if the heat absorption amount of the evaporator is determined, the temperature of the blown air after passing through the heat radiator can be adjusted by adjusting the heat absorption amount or the heat radiation amount of the first outdoor heat exchange unit.

  Therefore, according to this invention, compared with the above-mentioned conventional refrigeration cycle apparatus, the refrigeration cycle apparatus with a wide temperature adjustable range of the blown air to the air-conditioning target space in the dehumidifying heating mode can be provided.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole block diagram which shows the refrigerant circuit at the time of the heating mode of the refrigeration cycle apparatus of 1st Embodiment, and the 1st dehumidification heating mode. It is a whole block diagram which shows the refrigerant circuit at the time of the air_conditioning | cooling mode of the refrigeration cycle apparatus of 1st Embodiment, and the 2nd humidity heating mode. It is a figure which shows arrangement | positioning of the integrated valve 13, the receiver 14, the 1st expansion valve 15, and the 1st, 2nd outdoor heat exchange parts 16 and 17 in FIG. It is a figure which shows the combination of the inflow port which connects in the 1st, 2nd communication state of the integrated valve 13 in FIG. It is a longitudinal cross-sectional view of the integrated valve of 1st Embodiment. FIG. 6 is a sectional view taken along line VI-VI in FIG. 5. It is the VII-VII sectional view taken on the line in FIG. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode in the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 2nd dehumidification heating mode in the refrigerating-cycle apparatus of 1st Embodiment. It is a figure which shows arrangement | positioning of the integrated valve 13, the receiver 14, the 1st expansion valve 15, and the 1st, 2nd outdoor heat exchange parts 16 and 17 in 2nd Embodiment. It is a figure which shows the principal part of the refrigerating-cycle apparatus of 3rd Embodiment. It is a figure which shows the principal part of the refrigerating-cycle apparatus of 4th Embodiment. It is a figure which shows the integrated valve of 5th Embodiment. It is a figure which shows the 1st communication state of the integrated valve of 6th Embodiment. It is a figure which shows the 2nd communication state of the integrated valve of 6th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be described with the same reference numerals.

(First embodiment)
In this embodiment, the refrigeration cycle apparatus 10 according to the present invention is applied to a vehicle air conditioner 1 for an electric vehicle that obtains driving force for traveling from an electric motor for traveling. The refrigeration cycle apparatus 10 functions to cool or heat the vehicle interior air blown into the vehicle interior, which is the air conditioning target space, in the vehicle air conditioner 1.

  In this embodiment, as shown in FIGS. 1 and 2, a refrigerant circuit in a cooling mode (cooling operation) for cooling the vehicle interior, a refrigerant circuit in a heating mode (heating operation) for heating the vehicle interior, while dehumidifying the vehicle interior The refrigerant circuit in the first and second dehumidifying and heating modes (dehumidifying operation) for heating is configured to be switchable.

  Further, the refrigeration cycle apparatus 10 of the present embodiment employs a normal chlorofluorocarbon refrigerant as the refrigerant, and constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant does not exceed the critical pressure of the refrigerant. This refrigerant is mixed with refrigerating machine oil for circulating through the compressor 11 described later, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  The compressor 11 is disposed in the vehicle bonnet, and inhales, compresses and discharges the refrigerant in the refrigeration cycle apparatus 10. The compressor 11 is configured as an electric compressor that rotationally drives a fixed capacity type compression mechanism with a fixed discharge capacity by an electric motor. The operation (rotation speed) of the electric motor of the compressor 11 is controlled by a control signal output from the control device 40 described later.

  The inlet side of the indoor condenser 12 is connected to the discharge port side of the compressor 11. The indoor condenser 12 is disposed in a casing 31 that forms an air passage for air blown into the vehicle interior in the indoor air conditioning unit 30. The indoor condenser 12 exchanges heat between the discharged refrigerant (high-pressure refrigerant) discharged from the compressor 11 and the air blown into the vehicle interior that has passed through the indoor evaporator 20 described later, to dissipate the discharged refrigerant, and to blow air in the vehicle interior. It is a radiator that heats air.

  A first inlet A <b> 1 as a refrigerant inlet of the integrated valve 13 is connected to the outlet side of the indoor condenser 12. The integrated valve 13 is connected to the refrigerant inlet side and the refrigerant outlet side of the receiver 14, the refrigerant inlet side and the refrigerant outlet side of the first outdoor heat exchange unit 16, and the refrigerant inlet side of the second outdoor heat exchange unit 17. ing.

  The integrated valve 13 is connected between the receiver 14 and the first refrigerant between the refrigerant flow after the indoor condenser 12 passes through the refrigerant flow toward the second outdoor heat exchange unit 17, that is, on the upstream side of the refrigerant flow with respect to the second outdoor heat exchange unit. This is an order changing means for changing the order in which the refrigerant flows in the outdoor heat exchange section 16.

  As shown in FIG. 3, the integrated valve 13 of the present embodiment includes a receiver 14 in addition to the first inlet A <b> 1 into which the refrigerant discharged from the compressor 11 that has passed through the indoor condenser 12 flows into one structure. The refrigerant flows out toward the refrigerant inlet side of the first outdoor heat exchanger 16, the first outlet B <b> 1 through which the refrigerant flows out toward the refrigerant inlet side, the second inlet A <b> 2 through which the refrigerant flows out of the receiver 14. The second outlet B2, the third inlet A3 into which the refrigerant after flowing out of the first outdoor heat exchanger 16 flows, and the third outlet B3 from which the refrigerant flows out toward the refrigerant inlet of the second outdoor heat exchanger 17 Is formed.

  Then, after the refrigerant flowing in from the first inflow port A1 flows out from one of the first and second outflow ports B1 and B2, the inside of the integrated valve 13 flows into the integrated valve 13, and the first and second After flowing out from the other of the remaining two outlets B1 and B2, it flows into the integrated valve 13 and flows out from the third outlet B3.

  In other words, as shown in FIG. 4, the integrated valve 13 is a six-way valve configured to be able to switch the communication state between the inflow port and the outflow port between the first communication state and the second communication state. In the first communication state, as shown by the solid line in FIG. 4, the first inlet A1 and the first outlet B1 communicate with each other, the second inlet A2 and the second outlet B2 communicate with each other, In this state, the three inlets A3 and the third outlets B3 communicate with each other. In the second communication state, as shown by the broken line in FIG. 4, the first inlet A1 and the second outlet B2 communicate with each other, the third inlet A3 and the first outlet B1 communicate with each other, The two inlets A2 and the third outlet B3 are in communication with each other. The details of the internal structure of the integrated valve 13 will be described later.

  The receiver 14 is disposed downstream of the refrigerant flow with respect to the indoor condenser 12. The receiver 14 is a gas-liquid separator that separates the gas-liquid refrigerant and stores the liquid-phase refrigerant. The receiver 14 flows out the liquid phase refrigerant.

  A first expansion valve 15 is disposed between the second outlet B2 of the integrated valve 13 and the refrigerant flow in the first outdoor heat exchange unit 16.

  The first expansion valve 15 is a decompression unit that decompresses the refrigerant flowing into the first outdoor heat exchange unit 16. The first expansion valve 15 includes a valve body configured to be able to change the passage opening (throttle opening) of the refrigerant passage, and an electric actuator including a stepping motor that changes the throttle opening of the valve body. This is an electric variable aperture mechanism. The first expansion valve 15 of the present embodiment is composed of a variable throttle mechanism with a fully open function that fully opens the refrigerant passage when the throttle opening is fully opened. That is, the first expansion valve 15 can be configured not to exert the pressure reducing action of the refrigerant. The operation of the first expansion valve 15 is controlled by a control signal output from the control device 40.

  The first outdoor heat exchange unit 16 is disposed downstream of the refrigerant flow with respect to the indoor condenser 12. The second outdoor heat exchange unit 17 is arranged on the downstream side of the refrigerant flow with respect to the first outdoor heat exchange unit 16 and the receiver 14.

  The 1st, 2nd outdoor heat exchange parts 16 and 17 heat-exchange the refrigerant | coolant which distribute | circulates the inside, and the external air ventilated from the ventilation fan which is not shown in figure. The first and second outdoor heat exchange units 16 and 17 function as an evaporator that evaporates the refrigerant and exerts an endothermic effect in the heating mode described later, and dissipates the refrigerant in the cooling mode and the like. Functions as a radiator.

  In the present embodiment, as shown in FIG. 3, the first and second outdoor heat exchange units 16 and 17 are configured by one outdoor heat exchanger 18. The interior of the outdoor heat exchanger 18 is divided into two upper and lower heat exchange units, the upper heat exchange unit is the first outdoor heat exchange unit 16, and the lower heat exchange unit is the second outdoor heat exchange unit 17. It is said. The integrated valve 13 is disposed adjacent to the side surface of the outdoor heat exchanger 18. The receiver 14 is disposed away from the integrated valve 13.

  The outlet side of the second outdoor heat exchange unit 17 is connected to the inlet side of the indoor evaporator 20 via the second expansion valve 19.

  The second expansion valve 19 is a decompression unit that decompresses the refrigerant flowing into the indoor evaporator 20. The second expansion valve 19 includes a valve body configured to be able to change the passage opening (throttle opening) of the refrigerant passage, and an electric actuator including a stepping motor that changes the throttle opening of the valve body. This is an electric variable aperture mechanism.

  The second expansion valve 19 of the present embodiment is a variable throttle mechanism with a fully open function that fully opens the refrigerant passage when the throttle opening is fully opened and a fully closed function that closes the refrigerant passage when the throttle opening is fully closed. It consists of That is, the second expansion valve 19 can prevent the refrigerant from depressurizing and can open and close the refrigerant passage. The operation of the second expansion valve 19 is controlled by a control signal output from the control device.

  The indoor evaporator 20 is arranged in the casing 31 of the indoor air conditioning unit 30 on the upstream side of the air flow in the vehicle interior of the indoor condenser 12. The indoor evaporator 20 cools the air blown into the vehicle interior before passing through the indoor condenser 12 by evaporating the refrigerant flowing through the interior in the cooling mode and in the first and second dehumidifying and heating modes to exert an endothermic effect. It is an evaporator. The outlet side of the indoor evaporator 20 is connected to the suction side of the compressor 11.

  Further, a bypass passage 21 is provided between the outlet side of the second outdoor heat exchange unit 17 and the suction side of the compressor 11 so as to bypass the second expansion valve 19 and the indoor evaporator 20 and allow the refrigerant to flow. .

  An open / close valve (first open / close means) 22 is disposed in the bypass passage 21. The bypass on-off valve 22 is an electromagnetic valve that opens and closes the bypass passage 21, and its operation is controlled by a control signal output from the control device 40.

  When the bypass on-off valve 22 is open, the pressure loss that occurs when the refrigerant passes through the bypass passage 21 is extremely small compared to the pressure loss that occurs when the refrigerant passes through the indoor evaporator 20. Therefore, the refrigerant flowing out of the second outdoor heat exchange unit 17 flows into the bypass passage 21 when the bypass on-off valve 22 is open, and when the bypass on-off valve 22 is closed, the indoor evaporator 20 flows.

  Of the above-described cycle components, the integrated valve 13, the first expansion valve 15, the second expansion valve 19, and the bypass on-off valve 22 circulate as shown in the explanation of the operation in each operation mode described later. The refrigerant circuit switching means for switching the refrigerant circuit to be configured is configured.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 blows the temperature-adjusted vehicle interior air into the vehicle interior, and is disposed inside the instrument panel (instrument panel) at the foremost portion of the vehicle interior to form a casing 31 thereof. It is comprised by accommodating the air blower 32, the above-mentioned indoor condenser 12, the indoor evaporator 20, etc. in the inside.

  The casing 31 is made of resin, and forms an air passage for air blown into the vehicle interior. An inside / outside air switching device 33 for switching and introducing vehicle interior air (inside air) and outside air is disposed on the most upstream side of the air flow of the vehicle interior blown air in the casing 31.

  The inside / outside air switching device 33 is formed with an inside air introduction port for introducing inside air into the casing 31 and an outside air introduction port for introducing outside air. Furthermore, inside / outside air switching device 33 is provided with an inside / outside air switching door that continuously adjusts the opening area of the inside air introduction port and the outside air introduction port to change the air volume ratio between the inside air volume and the outside air volume. Has been.

  On the downstream side of the air flow of the inside / outside air switching device 33, a blower 32 that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is arranged. The blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) 32 a by an electric motor 32 b, and the number of rotations (air flow rate) is controlled by a control voltage output from the control device 40.

  On the downstream side of the air flow of the blower 32, the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the air blown into the vehicle interior. In other words, the indoor evaporator 20 is disposed upstream of the indoor condenser 12 in the flow direction of the air blown into the vehicle interior.

  Further, on the downstream side of the air flow of the indoor evaporator 20 and the upstream side of the air flow of the indoor condenser 12, the ratio of the amount of air passing through the indoor condenser 12 in the blown air after passing through the indoor evaporator 20. An air mix door 34 for adjusting the air pressure is disposed. The air mix door 34 is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the control device 40.

  Further, on the downstream side of the air flow of the indoor condenser 12, the blown air heated by exchanging heat with the refrigerant in the indoor condenser 12 and the blown air that is not heated bypassing the indoor condenser 12 are mixed. A mixing space 35 is provided.

  A blow-off opening that blows the conditioned air mixed in the mixing space 35 into the vehicle interior, which is the air-conditioning target space, is disposed at the most downstream portion of the air flow of the casing 31. Specifically, the blowout opening includes a face blowout opening that blows conditioned air toward the upper body of an occupant in the vehicle interior, a foot blowout opening that blows conditioned air toward the feet of the occupant, and a vehicle front window glass. A defroster blowout opening (not shown) for blowing conditioned air toward the inner surface is provided.

  Therefore, the temperature of the conditioned air mixed in the mixing space 35 is adjusted by adjusting the ratio of the air volume that the air mix door 34 passes through the indoor condenser 12, and the conditioned air blown out from each outlet opening is adjusted. The temperature is adjusted.

  Further, on the upstream side of the air flow of the face blowing opening, the foot blowing opening, and the defroster blowing opening, the face door for adjusting the opening area of the face blowing opening and the opening area of the foot blowing opening are adjusted respectively. A defroster door (both not shown) for adjusting the opening area of the foot door and the defroster blowout opening is disposed. These face doors, foot doors, and defroster doors are driven by a servo motor (not shown) whose operation is controlled by a control signal output from the control device 40 via a link mechanism or the like.

  Next, the electric control unit of this embodiment will be described. The control device 40 is composed of a known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM, and is connected to the output side. Controls the operation of various control devices.

  Further, on the input side of the control device 40, an inside air sensor that detects the temperature inside the vehicle, an outside air sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the temperature of the air blown from the indoor evaporator 20 (evaporation) An evaporator temperature sensor that detects the temperature of the refrigerant, a discharge temperature sensor that detects the temperature of the refrigerant discharged from the compressor 11, a blown air temperature sensor that detects the temperature of the blown air blown into the vehicle interior (the air temperature blown into the vehicle interior), etc. The various air conditioning control sensor groups are connected.

  Further, an operation panel (not shown) arranged near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 40, and operation signals from various operation switches provided on the operation panel are input. The As various air conditioning operation switches provided on the operation panel, specifically, an operation switch of the vehicle air conditioner 1, a vehicle interior temperature setting switch for setting the vehicle interior temperature, a cooling mode, a dehumidifying heating mode, and a heating mode are selected. An operation mode selection switch and the like are provided.

  In addition, although the control means which controls the operation | movement of the various control apparatus connected to the output side is integrally comprised, the control apparatus 40 is the structure (software and hardware) which controls the operation | movement of a control apparatus, respectively. However, they constitute control means for controlling the operation of each control device. For example, the configuration for controlling the integrated valve 13, the first expansion valve 15, the second expansion valve 19, and the bypass on-off valve 22 constitutes a refrigerant circuit switching control means. The configuration for controlling the throttle opening of the first expansion valve 15 constitutes a first throttle control means, and the configuration for controlling the throttle opening of the second expansion valve 19 constitutes a first throttle control means.

  Next, the internal structure of the integrated valve 13 will be described.

  As shown in FIGS. 5 to 7, the integrated valve 13 includes one body 131 in which first to third inflow ports A1 to A3 and first to third outflow ports B1 to B3 are formed. The body 131 constitutes the outer shape of the integrated valve 13 and is constituted by a metal block. In addition, each direction of 1st-3rd inflow port A1-A3 and 1st-3rd outflow port B1-B3 is not restricted to what is shown in figure, It is changed arbitrarily.

  An electric first three-way valve 132 is provided inside the body 131 to communicate the first inlet A1 with one of the first and second outlets B1 and B2.

  The first three-way valve 132 is configured to guide the refrigerant flowing from the first inflow port A1 to one of the first and second outflow ports B1 and B2 in accordance with the opening and closing of the electromagnetic valve 50.

  Specifically, the first main valve 60 is provided between the first inlet A1 and the first outlet B1, and the second main valve 70 is provided between the first inlet A1 and the second outlet B2. Is provided. The first main valve 60 and the second main valve 70 are disposed on the same axis. The first main valve 60 is provided with an electromagnetic valve 50 for reducing the differential pressure between the back pressure acting on the first main valve 60 and the pressure on the communication path side of the first outlet B1. The second main valve 70 is closed and the first main valve 60 is opened when is reduced.

  The first main valve 60 is configured to block or communicate between the first slide valve body 62 having the valve body portion 62a and the large diameter portion 62b, and the first inlet A1 and the first outlet B1. A first valve chamber 64 provided with a valve seat 63 that contacts and separates the portion 62a, a first back pressure chamber 65 provided on the opposite side of the first slide valve body 62 from the first valve chamber 64, and the valve A coil spring 66 is provided as a biasing member that biases the first slide valve body 62 in a direction in which the body portion 62a is closed.

  The 2nd main valve 70 interrupts | blocks between the 2nd slide valve body 72 which has the main valve body part 72a, the subvalve body part 72b, and the large diameter part 72c, and 1st inflow port A1 and 2nd outflow port B2. Alternatively, in order to communicate with each other, the second valve chamber 74 provided with the main valve seat 73 to which the main valve body portion 72a contacts and separates and the second back chamber provided with the sub valve seat 75 to which the sub valve body portion 72b contacts and separates. A pressure chamber 76 and a coil spring 77 as an urging member for urging the second slide valve body 72 in a direction in which the main valve body portion 72a is closed and the sub valve body portion 72b is opened are provided. The auxiliary valve seat 75 is formed on the valve seat forming member 78. A communication passage 78 a is formed inside the valve seat forming member 78. The second valve chamber 74 communicates with the first inflow port A <b> 1 through the communication path 79.

  As shown in FIG. 6, the high-pressure refrigerant introduced into the first inflow port A1 includes the communication passage 81, the first valve chamber 64, the large-diameter portion 62b of the first slide valve body 62, and its sliding wall surface. Between the large-diameter portion 72c of the second slide valve body 72 and its sliding wall surface, and also into the second back pressure chamber 76. Is done.

  Further, the first slide valve body 62 of the first main valve 60 includes a first back pressure chamber 65 and a lower portion of the valve seat 63 (on the opposite side of the first back pressure chamber 65 with the valve body portion 62a interposed therebetween). A pilot passage 82 communicating with the portion) is provided. The pilot passage 82 is opened and closed by the electromagnetic valve 50, and the sub-valve of the second slide valve element 72 applies the pressure in the lower part from the valve seat 63 via the communication passage 78 a of the valve seat forming member 78. It is made to act on the body part 72b.

  The electromagnetic valve 50 includes a coil portion 51, a suction element 52, a valve body (plunger) 53 with a ball 53a, an urging spring 54, and the like. When the solenoid valve 50 is not energized, the valve body 53 is pushed down by the urging spring 54 to close the pilot passage 82. When the solenoid valve 50 is energized, the valve body 53 is pulled up toward the attractor 52 and passes through the pilot passage 82. It can be opened. 5 to 7 show a state where the solenoid valve 50 is energized.

  In the body 131, a first check valve 83 is provided between the first outlet B1 and the third inlet A3, and the first check valve 83 is provided between the second outlet B2 and the second inlet A2. Two check valves 85 are provided.

  The first check valve 83 is disposed in the communication passage 84 that communicates the first outlet B1 and the third inlet A3. The first check valve 83 allows the first outlet B1 and the third inlet A3 to communicate with each other when the refrigerant pressure at the third inlet A3 is higher than the refrigerant pressure at the first outlet B1. When the refrigerant pressure at the outlet B1 is higher than the refrigerant pressure at the third inlet A3, the first outlet B1 and the third inlet A3 are blocked. FIG. 5 shows a state in which the first check valve 83 blocks between the first outlet B1 and the third inlet A3.

  The second check valve 85 is disposed in the communication path 86 that communicates the second outlet B2 and the second inlet A2. The second check valve 85 allows the second outlet B2 and the second inlet A2 to communicate with each other when the refrigerant pressure at the second inlet A2 is higher than the refrigerant pressure at the second outlet B2. When the refrigerant pressure at the outlet B2 is higher than the refrigerant pressure at the second inlet A2, the gap between the second outlet B2 and the second inlet A2 is blocked. FIG. 5 shows a state where the second check valve 85 allows the second outlet B2 and the second inlet A2 to communicate with each other.

  In addition, a non-electrically operated second three-way valve 133 that selectively connects one of the second and third inlets A2 and A3 and the third outlet B3 is provided in the body 131. The second three-way valve 133 is provided between the third check valve 91 provided between the second inlet A2 and the third outlet B3, and between the third inlet A3 and the third outlet B3. The fourth check valve 92 is mechanically interlocked with the third check valve 91.

  The third and fourth check valves 91 and 92 are arranged between the second inlet A2 and the third outlet B3 when the refrigerant pressure at the second inlet A2 is higher than the refrigerant pressure at the third inlet A3. And the third inlet A3 and the third outlet B3 are communicated, and when the refrigerant pressure at the third inlet A3 is higher than the refrigerant pressure at the second inlet A2, the third inlet A3 and The third outlet B3 is blocked, and the second inlet A2 and the third outlet B3 are communicated with each other.

  The third check valve 91 includes a valve hole 93 communicating with the communication passage 86 (second inlet A2), a valve body 94 slidably fitted in the valve hole 92, and a contact between the valve body 94 and the valve body 94. A valve seat 95 is provided, and a valve chamber 96 (common to the fourth check valve 92) communicating with the third outlet B3 via the communication path 100 is provided.

  The fourth check valve 92 includes a valve hole 97 that communicates with the communication passage 84 (third inlet A3), a valve body 98 that is slidably fitted in the valve hole 97, and a contact between the valve body 98 and the valve body 98. A valve seat 99 is provided, and a valve chamber 96 (common to the third check valve 91) communicating with the third outlet B3 via the communication path 100 is provided.

  The third and fourth check valves 91 and 92 are symmetrically arranged on the same axis with the same structure, and the cylindrical tip portions of both valve bodies 94 and 98 are connected to each other, so that both are mechanical. Are linked to each other.

Next, the operation of the vehicle air conditioner 1 of the present embodiment will be described. As described above, the vehicle air conditioner 1 of the present embodiment can be switched to the cooling mode for cooling the passenger compartment, the heating mode for heating the passenger compartment, and the dehumidifying heating mode for heating while dehumidifying the passenger compartment. The operation in each operation mode will be described below.
(A) Heating mode The heating mode is started when the heating mode is selected by the selection switch while the operation switch of the operation panel is turned on (ON).

  In the heating mode, the control device 40 sets the electromagnetic valve 50 of the integrated valve 13 in an energized state, sets the first expansion valve 15 to a control opening degree that exerts a pressure reducing action, sets the second expansion valve 19 in a fully closed state, and bypasses The on-off valve 22 is opened. Thereby, in the refrigerating cycle apparatus 10, it switches to the refrigerant circuit through which a refrigerant | coolant flows as shown by the arrow and white arrow of FIG.

  Moreover, the control apparatus 40 calculates the target blowing temperature TAO which is the target temperature of the air which blows off into a vehicle interior based on the value of the read detection signal and operation signal. Furthermore, the control device 40 determines the operating states of the various control devices connected to the control device 40 (control signals to be output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, the target condenser temperature TCO of the indoor condenser 12 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the control device. Then, based on the deviation between the target condenser temperature TCO and the detection value of the discharge temperature sensor, the compressor is arranged so that the temperature of the air that has passed through the indoor condenser 12 using the feedback control method approaches the target outlet temperature TAO. The control signal output to 11 electric motors is determined.

  Further, the control signal output to the first expansion valve 15 is determined so that the temperature state of the refrigerant flowing out from the second outdoor heat exchange unit 17 becomes a predetermined target temperature state.

  The control signal output to the servo motor of the air mix door 34 is determined so that the total flow rate of the blown air after passing through the indoor evaporator 20 passes through the air passage of the indoor condenser 12.

  Then, the control signal determined as described above is output to various control devices. Thereafter, until the operation stop of the vehicle air conditioner 1 is requested by the operation panel, a control routine such as operation mode determination processing → determination of operation states of various control devices → output of control signals and the like is repeated at predetermined intervals. . Such a control routine is repeated in the other operation modes.

  Here, the refrigerant flow in the integrated valve 13, the receiver 14, the first outdoor heat exchange unit 16, and the second outdoor heat exchange unit 17 in the heating mode will be described.

  When the solenoid valve 50 of the integrated valve 13 is energized, as shown in FIG. 1, the refrigerant that has flowed from the first inlet A1 of the integrated valve 13 is guided to the first outlet B1. Thereby, the order in which the refrigerant flows is the receiver 14 first and the first outdoor heat exchange unit 16 rear.

  Specifically, as shown in FIGS. 5 and 6, when the solenoid valve 50 is energized, the valve body 53 of the solenoid valve 50 is pulled up and the pilot passage 82 is opened. As a result, the pressure in the lower portion of the first main valve 60 from the valve seat 63 is increased and the differential pressure with respect to the first back pressure chamber 65 is reduced, and the increased pressure is communicated with the communication passage 78a of the valve seat forming member 78. Acting on the sub-valve part 72b of the second slide valve body 72. For this reason, the 2nd slide valve body 72 of the 2nd main valve 70 moves, the main valve body part 72a is closed, and the subvalve body part 72b is opened. As a result, the high-pressure refrigerant flowing from the first inflow port A1 is guided to the first valve chamber 64 of the first main valve 60 via the communication passage 81, and enters the large diameter portion 62b of the first slide valve body 62. Works. Thereby, the 1st slide valve body 62 moves against the urging | biasing force of the coil spring 66, and the valve body part 62a is opened. For this reason, it will be in the state which 1st inflow port A1 and 1st outflow port B1 connected, and the refrigerant | coolant which flowed in from 1st inflow port A1 flows out out of 1st outflow port B1. Since the first check valve 83 is pushed and closed by the refrigerant flowing in from the first inlet A1, the refrigerant flowing in from the first inlet A1 does not flow to the third inlet A3.

  The refrigerant flowing out from the first outlet B1 flows into the integrated valve 13 from the second inlet A2 via the receiver 14. The pressure of the refrigerant flowing in from the second inlet A2 acts on the second check valve 85 disposed in the communication path 86 that communicates the second inlet A2 and the second outlet B2, thereby causing the second reverse The stop valve 85 moves and opens. For this reason, the second inlet A2 and the second outlet B2 are in communication with each other, and the refrigerant flowing in from the second inlet A2 flows out of the second outlet B2 via the second check valve 85. .

  The refrigerant that has flowed out from the second outlet B2 flows from the third refrigerant inlet A3 through the first expansion valve 15 and the first outdoor heat exchange unit 16. At this time, since the first expansion valve 15 is set to the control opening degree, the refrigerant decompressed by the first expansion valve 15 flows in from the third refrigerant inflow port A3. For this reason, since the refrigerant pressure at the second inlet A2 is higher than the refrigerant pressure at the third inlet A3, the third check valve 91 on the second inlet A2 side is closed as shown in FIGS. The fourth check valve 92 on the third inlet A3 side is opened. That is, the third and fourth check valves 91 and 92 block between the second inlet A2 and the third outlet B3, and allow the third inlet A3 and the third outlet B3 to communicate with each other.

  As a result, the refrigerant flowing in from the third refrigerant inlet A3 flows out from the third outlet B3. Then, the refrigerant flowing out from the third outlet B3 flows into the second outdoor heat exchange unit 17.

  Therefore, in the refrigeration cycle apparatus 10 in the heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 as shown in FIG. The refrigerant that has flowed into the indoor condenser 12 exchanges heat with the vehicle interior blown air that has been blown from the blower 32 and passed through the indoor evaporator 20 to dissipate heat. Thereby, vehicle interior blowing air is heated.

  The refrigerant flowing out of the indoor condenser 12 flows into the receiver 14 via the integrated valve 13 and is separated into gas and liquid. Then, the liquid-phase refrigerant separated by the receiver 14 flows into the first expansion valve 15 via the integrated valve 13 and is decompressed and expanded by the first expansion valve 15 until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the first expansion valve 15 flows into the first outdoor heat exchange unit 16, absorbs heat from the outside air blown from the blower fan, and evaporates. The refrigerant that has flowed out of the first outdoor heat exchange unit 16 flows into the second outdoor heat exchange unit 17 through the integrated valve 13 and absorbs heat from the outside air blown from the blower fan.

  The refrigerant that has flowed out of the second outdoor heat exchange unit 17 flows into the suction side of the compressor 11 through the bypass passage 21 and is compressed again by the compressor 11. Since the second expansion valve 19 is fully closed, the refrigerant does not flow into the indoor evaporator 20.

  As described above, in the heating mode, the compressor 11 → the indoor condenser 12 → the integrated valve 13 (first inlet A1 → first outlet B1) → receiver 14 → integrated valve 13 (second inlet A2 → second flow). Outlet B2) → first expansion valve 15 (control opening) → first outdoor heat exchange section 16 → integrated valve 13 (third inlet A3 → third outlet B3) → second outdoor heat exchange section 17 → bypass passage It switches to the refrigerant circuit through which a refrigerant flows in order of 21-> compressor 11.

In this heating mode, the heat of the high-pressure refrigerant discharged from the compressor 11 by the indoor condenser 12 can be dissipated to the vehicle interior blowing air, and the heated vehicle interior blowing air can be blown out into the vehicle interior. . As a result, heating in the passenger compartment can be realized.
(B) Cooling mode In the cooling mode, the operation switch of the operation panel is turned on (ON) and is started when the cooling mode is selected by the selection switch.

  In the cooling mode, the control device 40 sets the electromagnetic valve 50 of the integrated valve 13 to a non-energized state, sets the first expansion valve 15 to a fully open state, sets the second expansion valve 19 to a control opening degree that exerts a pressure reducing action, and bypasses The on-off valve 22 is closed. Thereby, in the refrigerating cycle apparatus 10, it switches to the refrigerant | coolant flow path through which a refrigerant | coolant flows as shown by the arrow of FIG.

  Furthermore, the control device 40 determines the operating states of the various control devices connected to the control device 40 (control signals to be output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, the target evaporator temperature TEO of the indoor evaporator 20 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the control device. Then, based on the deviation between the target evaporator temperature TEO and the detected value of the evaporator temperature sensor, the temperature of the air that has passed through the indoor evaporator 20 is compressed using the feedback control method so as to approach the target blowing temperature TAO. A control signal output to the electric motor of the machine 11 is determined.

  Further, the control signal output to the second expansion valve 19 is determined so that the temperature state of the refrigerant flowing out of the indoor evaporator 20 becomes a predetermined target temperature state.

  For the control signal output to the servo motor of the air mix door 34, the air mix door 34 closes the air passage of the indoor condenser 12, and the total flow rate of the blown air after passing through the indoor evaporator 20 is cold air bypass. It is determined to pass through the passage. That is, the air mix door 34 is set to the solid line position in FIG.

  Here, the refrigerant flows in the integrated valve 13, the receiver 14, the first outdoor heat exchange unit 16, and the second outdoor heat exchange unit 17 in the cooling mode will be described.

  When the solenoid valve 50 of the integrated valve 13 is turned off, the refrigerant flowing from the first inlet A1 of the integrated valve 13 is guided to the second outlet B2 as shown in FIG. Thereby, the order in which the refrigerant flows is the first outdoor heat exchange unit 16 first and the receiver 14 later.

  Specifically, when the solenoid valve 50 is turned off, the pilot passage 82 is closed by the solenoid valve 50 (see FIGS. 5 and 6). At this time, the pressure of the refrigerant flowing from the first inlet A1 acts on the large diameter portion 72c of the second slide valve body 72. As a result, the second slide valve body 72 moves, the main valve body portion 72a is opened, and the sub-valve body portion 72b is closed. At this time, since the internal pressure (back pressure) of the first back pressure chamber 65 is higher than the internal pressure of the lower portion of the first main valve 60 from the valve seat 63, the valve body 62 a of the first slide valve body 62. Is closed. For this reason, it will be in the state which 1st inflow port A1 and 2nd outflow port B2 connected, and the refrigerant | coolant which flowed in from 1st inflow port A1 flows out out of 2nd outflow port B2. Since the second check valve 85 is pushed and closed by the refrigerant flowing in from the first inlet A1, the refrigerant flowing in from the first inlet A1 does not flow to the second inlet A2.

  The refrigerant that has flowed out of the second outlet B2 flows into the integrated valve 13 from the third inlet A3 via the first expansion valve 15 and the first outdoor heat exchanger 16. At this time, the first check valve 83 is pushed and opened by the refrigerant flowing in from the third inflow port A3. As a result, the third inlet A3 and the first outlet B1 are in communication with each other, and the refrigerant flowing in from the third inlet A3 flows out of the first outlet B1 via the first check valve 83. .

  The refrigerant that has flowed out of the first outlet B1 flows in from the second refrigerant inlet A2 via the receiver 14. At this time, the refrigerant flowing in from the second refrigerant inlet A2 has a pressure lower than that of the refrigerant flowing in from the third inlet A3 due to the pressure loss accompanying the refrigerant flow. Therefore, since the refrigerant pressure at the third inlet A3 is higher than the refrigerant pressure at the second inlet A2, the fourth check valve 92 on the third inlet A3 side is closed and the second inlet A2 side is closed. The third check valve 91 is opened. That is, the third and fourth check valves 91 and 92 block between the third inlet A3 and the third outlet B3, and communicate the second inlet A2 and the third outlet B3 ( (See FIG. 7).

  As a result, the refrigerant flowing in from the second inlet A2 flows out from the third outlet B3. Then, the refrigerant flowing out from the third outlet B3 flows into the second outdoor heat exchange unit 17.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the air mix door 34 closes the air passage of the indoor condenser 12, the refrigerant flowing into the indoor condenser 12 flows out of the indoor condenser 12 with almost no heat exchange with the air blown into the vehicle interior. To do.

  The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 15 via the integrated valve 13. At this time, since the first expansion valve 15 is fully opened, the refrigerant flowing out from the indoor condenser 12 flows into the first outdoor heat exchange unit 16 without being depressurized by the first expansion valve 15. The refrigerant flowing into the first outdoor heat exchange unit 16 radiates heat to the outside air blown from the blower fan in the first outdoor heat exchange unit 16.

  The refrigerant that has flowed out of the first outdoor heat exchange unit 16 flows into the receiver 14 via the integrated valve 13 and is separated into gas and liquid. The gas-liquid separated liquid-phase refrigerant flows into the second outdoor heat exchange unit 17 through the integrated valve 13, further dissipates heat to the outside air blown from the blower fan, and increases the degree of subcooling (subcool). Have.

  The refrigerant that has flowed out of the second outdoor heat exchange unit 17 flows into the second expansion valve 19 and is decompressed and expanded at the second expansion valve 19 until it becomes a low-pressure refrigerant. The low-pressure refrigerant depressurized by the second expansion valve 19 flows into the indoor evaporator 20, absorbs heat from the vehicle interior air blown from the blower 32, and evaporates. Thereby, vehicle interior blowing air is cooled.

  The refrigerant flowing out of the indoor evaporator 20 is sucked from the suction side of the compressor 11 and is compressed again by the compressor 11.

  As described above, in the cooling mode, the compressor 11 → the indoor condenser 12 → the integrated valve 13 (first inlet A1 → second outlet B2) → first expansion valve 15 (fully open) → first outdoor heat exchanger 16 → Integrated valve 13 (third inlet A3 → first outlet B1) → Receiver 14 → Integrated valve 13 (second inlet A2 → third outlet B3) → Second outdoor heat exchanger 17 → Second expansion valve 19 (control opening degree) → indoor evaporator 20 → the compressor 11 is switched to the refrigerant circuit through which the refrigerant flows.

In this cooling mode, since the air passage of the indoor condenser 12 is blocked by the air mix door 34, the air blown into the vehicle interior cooled by the indoor evaporator 20 can be blown out into the vehicle interior. Thereby, cooling of a vehicle interior is realizable.
(C) First dehumidifying and heating mode In the first dehumidifying and heating mode, the dehumidifying and heating mode is selected by the selection switch in a state where the operation switch of the operation panel is turned on (ON), and further, the target of the blown air to be blown out into the vehicle interior It is started when the target blowing temperature TAO, which is a temperature, is higher than the reference temperature.

  In the first dehumidifying and heating mode, the control device 40 sets the electromagnetic valve 50 of the integrated valve 13 to the energized state and sets the first expansion valve 15 to a control opening degree that exerts a pressure reducing action, as in the heating mode. Further, unlike the heating mode, the control device 40 sets the second expansion valve 19 to a control opening degree that exerts a pressure reducing action, and closes the bypass on-off valve 22.

  Thereby, in the refrigerating cycle apparatus 10, it switches to the refrigerant circuit through which a refrigerant flows, as shown by the arrow of FIG. The refrigerant flow in the first dehumidifying and heating mode is the same as that in the heating mode from the compressor 11 to the second outdoor heat exchanging unit 17, not the bypass passage 21, but the second expansion valve 19 (control opening), indoor evaporation. The point where the refrigerant flows through the vessel 20 is different from the heating mode.

  Accordingly, in the first dehumidifying and heating mode, the compressor 11, the indoor condenser 12, the receiver 14, the first expansion valve 15, the first outdoor heat exchange unit 16, the second outdoor heat exchange unit 17, the second expansion valve 19, and the room. The refrigerant circuit is switched to the refrigerant circuit in the order of the evaporator 20.

  Furthermore, the control device 40 determines the operating states of the various control devices connected to the control device 40 (control signals to be output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For the compressor 11, a control signal output to the electric motor of the compressor 11 is determined so that the temperature of the air that has passed through the indoor evaporator 20 approaches the target evaporator temperature TEO for exhibiting a predetermined dehumidifying performance. Is done.

  The operating state of the air mix door 34 is determined in the same manner as in the heating mode.

  Further, the operating states of the first expansion valve 14 and the second expansion valve 19 are determined according to a target blowing temperature TAO that is a target temperature of the blowing air blown into the vehicle interior. Specifically, the control device 40 decreases the passage area (throttle opening) of the refrigerant passage by the first expansion valve 15 and increases the refrigerant passage by the second expansion valve 19 as the target blowing temperature TAO is higher. Increase the passage area (throttle opening).

  Thereby, in the 1st dehumidification heating mode, about the state of the refrigerant | coolant which circulates through a cycle, as shown to the Mollier diagram of FIG. In FIG. 8, for the sake of convenience, each component of the cycle is shown in the Mollier diagram.

  That is, as shown in FIG. 8, the high-pressure refrigerant (point A in FIG. 8) discharged from the compressor 11 flows into the indoor condenser 12 and is cooled by the indoor evaporator 20 to be dehumidified. Heat is exchanged with the blown air to dissipate heat (point A → point B in FIG. 8). Thereby, vehicle interior blowing air is heated.

  The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 15 via the integrated valve 13 and the receiver 14, and is reduced in pressure until it becomes an intermediate pressure refrigerant having a temperature lower than the outside air temperature (B in FIG. 8). Point → C). Then, the intermediate pressure refrigerant decompressed by the first expansion valve 15 flows into the first outdoor heat exchanging portion 16 and absorbs heat from the outside air blown from the blower fan. 2 It flows into the outdoor heat exchange part 17 and absorbs heat from the outside air blown from the blower fan (point C → point D in FIG. 8).

  The refrigerant that has flowed out of the second outdoor heat exchanger 17 flows into the second expansion valve 19 and is decompressed and expanded at the second expansion valve 19 until it becomes a low-pressure refrigerant (point D → point E in FIG. 8). The low-pressure refrigerant decompressed by the second expansion valve 19 flows into the indoor evaporator 20 and absorbs heat from the air blown from the vehicle interior blown from the blower 32 to evaporate (point E → point F in FIG. 8). Thereby, vehicle interior blowing air is cooled. The refrigerant flowing out of the indoor evaporator 20 flows into the suction side of the compressor 11 and is compressed again by the compressor 11.

  As described above, in the first dehumidifying and heating mode, the vehicle interior blown air cooled and dehumidified by the indoor evaporator 20 can be heated by the indoor condenser 12 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

At this time, in the first dehumidifying and heating mode, the first and second outdoor heat exchange units 16 and 17 are functioned as heat absorbers. And by adjusting the throttle opening degree of the first and second expansion valves 15 and 19, the pressure (temperature) of the refrigerant flowing into the first and second outdoor heat exchange parts 16 and 17 can be adjusted, The amount of heat absorbed by the second outdoor heat exchange units 16 and 17 can be adjusted. As a result, even if the heat absorption amount of the indoor evaporator 20 is determined, the heat dissipation amount of the indoor condenser 12 can be adjusted by adjusting the heat absorption amounts of the first and second outdoor heat exchange units 16 and 17. The temperature of the blast air after 12 passes can be adjusted. That is, by controlling the pressure with the first and second expansion valves 15 and 19 according to the target blowing temperature TAO, the blowing air temperature to the air-conditioning target space can be set as the target blowing air temperature.
(D) Second Dehumidifying Heating Mode In the second dehumidifying heating mode, the operation switch of the operation panel is turned on (ON), the dehumidifying heating mode is selected by the selection switch, and the target of the blown air to be blown out into the passenger compartment It is started when the target blowing temperature TAO, which is a temperature, is lower than the reference temperature.

  In the second dehumidifying and heating mode, as in the cooling mode, the control device 40 sets the electromagnetic valve 50 of the integrated valve 13 to a non-energized state, sets the second expansion valve 19 to a control opening degree that exerts a pressure reducing action, The on-off valve 22 is closed. Further, unlike the cooling mode, the control device 40 sets the first expansion valve 15 to a control opening degree that exerts a pressure reducing action.

  Thereby, in the refrigerating cycle apparatus 10, it switches to the refrigerant circuit through which a refrigerant flows, as shown by the arrow of FIG. The refrigerant flow in the second dehumidifying and heating mode is the same as in the cooling mode. That is, in the second dehumidifying and heating mode, the compressor 11 → the indoor condenser 12 → the first expansion valve 15 → the first outdoor heat exchange unit 16 → the receiver 14 → the second outdoor heat exchange unit 17 → the second expansion valve 19 → the indoor The refrigerant circuit is switched to the refrigerant circuit in the order of the evaporator 20.

  Furthermore, the control device 40 determines the operating states of the various control devices connected to the control device 40 (control signals to be output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For the compressor 11, a control signal output to the electric motor of the compressor 11 is determined so that the temperature of the air that has passed through the indoor evaporator 20 approaches the target evaporator temperature TEO for exhibiting a predetermined dehumidifying performance. Is done.

  The operating state of the air mix door 34 is determined so that the total flow rate of the blown air after passing through the indoor evaporator 20 passes through the air passage of the indoor condenser 12, unlike the cooling mode. That is, the air mix door 34 is in the position of the broken line in FIG.

  Further, the operating states of the first expansion valve 14 and the second expansion valve 19 are determined according to a target blowing temperature TAO that is a target temperature of the blowing air blown into the vehicle interior. Specifically, the control device 40 decreases the passage area (throttle opening) of the refrigerant passage by the first expansion valve 15 and increases the refrigerant passage by the second expansion valve 19 as the target blowing temperature TAO is higher. Increase the passage area (throttle opening). However, in the second dehumidifying and heating mode, the throttle opening of the first expansion valve 15 is set to a larger throttle state than in the first dehumidifying and heating mode, and the throttle opening of the second expansion valve 19 is set to be larger than that in the first dehumidifying and heating mode. Use a small aperture.

  Thereby, in the 2nd dehumidification heating mode, about the state of the refrigerant | coolant which circulates through a cycle, as shown to the Mollier diagram of FIG. In FIG. 9, for convenience, each component of the cycle is shown in the Mollier diagram.

  That is, as shown in FIG. 9, the high-pressure refrigerant (point A in FIG. 9) discharged from the compressor 11 flows into the indoor condenser 12 and is cooled by the indoor evaporator 20 to be dehumidified. Heat is exchanged with the blown air to dissipate heat (point A → point B in FIG. 9). Thereby, vehicle interior blowing air is heated.

  The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 15 via the integrated valve 13 and is depressurized until it becomes an intermediate pressure refrigerant (point B → point C in FIG. 9).

  The intermediate pressure refrigerant decompressed by the first expansion valve 15 flows into the first outdoor heat exchange unit 16 and radiates heat to the outside air blown from the blower fan. The refrigerant that has flowed out of the first outdoor heat exchange unit 16 flows into the receiver 14 via the integrated valve 13 and is separated into gas and liquid. The gas-liquid separated liquid-phase refrigerant flows into the second outdoor heat exchanger 17 through the integrated valve 13, further dissipates heat to the outside air blown from the blower fan, and has a subcool (see FIG. 9). C point → D point).

  The refrigerant that has flowed out of the second outdoor heat exchange unit 17 flows into the second expansion valve 19 and is decompressed and expanded at the second expansion valve 19 until it becomes a low-pressure refrigerant (point D → point E in FIG. 9). The low-pressure refrigerant depressurized by the second expansion valve 19 flows into the indoor evaporator 20 and absorbs heat from the vehicle interior air blown from the blower 32 to evaporate (point E → point F in FIG. 9). Thereby, vehicle interior blowing air is cooled. Then, the refrigerant flowing out of the indoor evaporator 20 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

  As described above, in the second dehumidifying heating mode, the vehicle interior blown air cooled and dehumidified by the indoor evaporator 20 can be heated by the indoor condenser 12 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

  At this time, in the second dehumidifying and heating mode, the first and second outdoor heat exchange units 16 and 17 are caused to function as radiators. And by adjusting the throttle opening degree of the first and second expansion valves 15 and 19, the pressure (temperature) of the refrigerant flowing into the first and second outdoor heat exchange parts 16 and 17 can be adjusted, The heat radiation amount of the second outdoor heat exchange units 16 and 17 can be adjusted. As a result, even if the heat absorption amount of the indoor evaporator 20 is determined, the heat dissipation amount of the indoor condenser 12 can be adjusted by adjusting the heat dissipation amounts of the first and second outdoor heat exchanging units 16 and 17. The temperature of the blast air after 12 passes can be adjusted. That is, by controlling the pressure with the first and second expansion valves 15 and 19 according to the target blowing temperature TAO, the blowing air temperature to the air-conditioning target space can be set as the target blowing air temperature.

  Next, the effect of this embodiment will be described.

  (1) In the refrigeration cycle apparatus 10 of the present embodiment, as described above, switching between the refrigerant circuit in the cooling mode and the refrigerant circuit in the heating mode can be performed by the integrated valve 13 or the like.

  In the cooling mode, the refrigerant is flowed in the order of the first outdoor heat exchange unit 16 → the receiver 14 → the second outdoor heat exchange unit 17, so that the liquid-phase refrigerant separated by the receiver 14 is exchanged in the second outdoor heat exchange. Since it can cool by the part 17 and can be set as a supercooled liquid phase refrigerant | coolant, a cooling performance can be improved.

  Therefore, according to the refrigeration cycle apparatus 10 of the present embodiment, it is possible to execute a cooling mode having higher cooling performance than the refrigeration cycle apparatus described in Patent Document 1 described above.

  (2) In the refrigeration cycle apparatus 10 of the present embodiment, as described above, the refrigerant circuit and the second dehumidifying heating mode in the first dehumidifying heating mode described above are switched by switching the integrated valve 13 according to the target blowing temperature TAO. Switching to the refrigerant circuit at the time is possible.

  In the first dehumidifying and heating mode, the first and second outdoor heat exchange units 16 and 17 function as heat sinks, and in the second dehumidifying and heating mode, the first and second outdoor heat exchange units 16 and 17 are operated. Since it is functioning as a radiator, the temperature of the indoor condenser 12 can be made higher in the first dehumidifying and heating mode than in the second dehumidifying and heating mode.

  In the first and second dehumidifying and heating modes, the first and second expansion valves 15 and 19 adjust the pressure of the refrigerant flowing into the first and second outdoor heat exchange units 16 and 17 to 1. The amount of heat absorbed or radiated by the second outdoor heat exchangers 16, 17 can be adjusted.

  As a result, even if the heat absorption amount of the indoor evaporator 20 is determined, the temperature of the blown air after passing through the indoor condenser 12 can be adjusted by adjusting the heat absorption amount or the heat radiation amount of the first and second outdoor heat exchange units 16 and 17. Can be adjusted in low and high temperature ranges.

  Therefore, according to the refrigeration cycle apparatus 10 of the present embodiment, dehumidification heating with a wide temperature adjustable range of the blown air to the air-conditioning target space is possible as compared with the refrigeration cycle apparatus described in Patent Document 1 described above. .

   (3) In the refrigeration cycle apparatus 10 of the present embodiment, the order in which the refrigerant in the first outdoor heat exchange unit 16 and the receiver 14 flows by the single integrated valve 13 on the upstream side of the refrigerant flow with respect to the second outdoor heat exchange unit 17. This constitutes an order changing means for exchanging.

  According to this, since the order changing means is constituted by one device, the cycle configuration of the refrigeration cycle can be simplified as compared with the case where the order changing means is constituted by a plurality of devices.

  (4) In the refrigeration cycle apparatus 10 of the present embodiment, as described above, the integrated valve 13 includes the body 131, the electric first three-way valve 132 provided in the body 131, and the first check valve 83. The second check valve 85 and the non-electrically operated second three-way valve 133 are included.

  According to this, the structure which replaces the order in which the refrigerant | coolant of the 1st outdoor heat exchange part 16 and the receiver 14 flows can be implement | achieved by one drive means (in this example, electromagnetic valve 50) for driving the 1st three-way valve 132. .

  (5) A general vehicle cooling cycle is a receiver cycle, and a general heat pump cycle is an accumulator cycle. For this reason, in the same type of vehicle, when a vehicle type equipped with a cooling cycle and a vehicle type equipped with a heat pump cycle coexist, in the vehicle type equipped with a heat pump cycle, the following is required for installing the accumulator: .

  For example, when an accumulator is installed near the compressor, it is necessary to provide an installation space in the encoder. Further, when an accumulator is installed near the outdoor heat exchanger, for example, under a lamp, it is necessary to route the piping.

  On the other hand, since the refrigeration cycle apparatus 10 of the present embodiment is a receiver cycle, there is no need for such troublesome installation for the accumulator.

  (6) The accumulator used in the accumulator cycle stores liquid phase refrigerant and supplies gas phase refrigerant to the compressor, and at that time, oil contained in the liquid phase refrigerant is returned to the compressor. For this reason, there is a problem that the oil must be sealed in the cycle rather than the receiver cycle because the oil is stored together with the liquid phase refrigerant in the accumulator. Further, since an oil return structure is required, the accumulator needs a volume corresponding to the oil return structure, and there is a problem that the physique becomes larger than the receiver.

  On the other hand, since the refrigerating cycle apparatus 10 of this embodiment is a receiver cycle, these problems can be solved.

  (7) In the accumulator cycle, since the accumulator temperature becomes lower than the ambient temperature due to the refrigerant temperature, there is a problem that the cooling performance in the cooling mode is lowered due to heat absorption of the accumulator. As a countermeasure, a method of insulating the inside of the accumulator is conceivable. However, this method increases the physique of the accumulator, and thus this method cannot be adopted when the accumulator mounting space is limited.

  On the other hand, since the refrigeration cycle apparatus 10 of this embodiment is a receiver cycle and does not use an accumulator, this problem can be solved. That is, the cooling performance in the cooling mode can be improved as compared with the accumulator cycle.

(Second Embodiment)
In the present embodiment, as shown in FIG. 10, the receiver 14 is disposed and fixed adjacent to the integrated valve 13, and the other configurations are the same as those in the first embodiment.

  As described above, by arranging and integrating the integrated valve 13 and the receiver 14 adjacent to the side surface of the outdoor heat exchanger 18, it is possible to improve these vehicle mounting properties.

(Third embodiment)
In the present embodiment, as shown in FIG. 11, with respect to the refrigeration cycle apparatus 10 of the first and second embodiments, a bypass passage 23 that bypasses the second outdoor heat exchange unit 17 and flows the refrigerant, and the bypass passage A bypass opening / closing valve 24 for opening and closing the opening 23 is added. Other configurations are the same as those in the first and second embodiments.

  In 1st, 2nd embodiment, the 1st, 2nd outdoor heat exchange parts 16 and 17 are functioned as a heat absorber by heating mode or 1st dehumidification heating mode. However, depending on the structure of the second outdoor heat exchange unit 17, the pressure loss of the refrigerant when passing through the second outdoor heat exchange unit 17 becomes high, so that it is more efficient to bypass the second outdoor heat exchange unit 17 in terms of performance. May be advantageous.

  Therefore, in the present embodiment, the refrigerant that flows out from the third outlet B3 flows around the second outdoor heat exchanger 17 by opening the bypass on-off valve 24 in the heating mode or the first dehumidifying heating mode. To.

  On the other hand, in the cooling mode, the bypass on-off valve 24 is closed so that the refrigerant flowing out from the third outlet B3 passes through the second outdoor heat exchanger 17 as in the first and second embodiments. To do.

(Fourth embodiment)
In the present embodiment, the integrated valve 13 of the first embodiment is divided into two, thereby bypassing the second outdoor heat exchanger 17 in the heating mode and the first dehumidifying heating mode, as in the third embodiment. A refrigerant is passed through the bypass passage.

  Specifically, as shown in FIG. 12, the refrigeration cycle apparatus 10 includes an integrated valve 13 and a downstream side switching valve 26 arranged on the downstream side of the refrigerant flow of the integrated valve 13 as order changing means. .

  The integrated valve 13 of the present embodiment is obtained by omitting the second three-way valve 133 and adding a fourth outlet B4 to the integrated valve 13 of the first embodiment.

  Specifically, the integrated valve 13 includes a first body 131 having first to third inlets A1 to A3 and first to fourth outlets B1 to B4. The first to third inlets A1 to A3 and the first and second outlets B1 and B2 of the present embodiment are the same as those of the first embodiment.

  Inside the first body 131, the third outlet B3 communicates with the second inlet A2, and the fourth outlet B4 communicates with the third inlet A3.

  The third outlet B3 is connected to the refrigerant inlet side of the second outdoor heat exchange unit 17, and the refrigerant flows out from the third outlet B3 toward the refrigerant inlet side of the second outdoor heat exchange unit 17. The fourth outlet B4 is connected to a bypass passage 25 that bypasses the second outdoor heat exchanger 17 and flows the refrigerant, and the refrigerant flows out from the fourth outlet B4 toward the bypass passage 25.

  The downstream switching valve 26 includes a second body 261 having a fourth inlet A4, a fifth inlet A5, and a fifth outlet B5. The second body 261 is separate from the first body 131 and is spaced apart from the first body 131. The fourth inlet A4 communicates with the third outlet B3 of the integrated valve 13 via the second outdoor heat exchange unit 17. The fifth inlet A5 is communicated with the fourth outlet B4 of the integrated valve 13 via the bypass passage 25. The fifth outlet B5 is a refrigerant outlet that allows the refrigerant flowing in from one of the fourth and fifth inlets A4 and A5 to flow out.

  The downstream side switching valve 26 is provided with a second three-way valve 133 in the second body 261 for communicating one of the fourth and fifth inlets A4 and A5 with the fifth outlet B5. The second three-way valve 133 is the same as the second three-way valve 133 described in the first embodiment, and operates in the same manner as in the first embodiment.

  In the present embodiment, the third check valve 91 of the second three-way valve 133 is provided between the fourth inlet A4 and the fifth outlet B5, and the fourth check valve 92 of the second three-way valve 133 is The fifth inflow port A5 and the fifth outflow port B5 are provided. For this reason, the third and fourth check valves 91 and 92 are configured such that when the refrigerant pressure at the fourth inlet A4 is higher than the refrigerant pressure at the fifth inlet A5, the fourth inlet A4 and the fifth outlet B5 The fifth inlet A5 and the fifth outlet B5 are communicated with each other. On the other hand, when the refrigerant pressure at the fifth inlet A5 is higher than the refrigerant pressure at the fourth inlet A4, the third and fourth check valves 91 and 92 are connected between the fifth inlet A5 and the fifth outlet B5. The gap is blocked, and the fourth inlet A4 and the fifth outlet B5 are communicated.

  With such a configuration, in the heating mode and the first dehumidifying heating mode, the solenoid valve 50 is energized in the heating mode and the first dehumidifying heating mode, so that the refrigerant flowing out from the fourth outlet B4 is exchanged in the second outdoor heat. It flows around the part 17.

  On the other hand, in the cooling mode, similarly to the first embodiment, the refrigerant that has flowed out from the third outlet B3 passes through the second outdoor heat exchanger 17 because the solenoid valve 50 is in a non-energized state.

  Also according to the present embodiment, the effects (1), (2), (4) to (7) of the first embodiment are exhibited.

  Further, according to the present embodiment, the order changing means is constituted by two switching devices of the integrated valve 13 and the downstream side switching valve 26, so that the order changing means is constituted by three or more switching devices. The cycle configuration can be simplified.

(Fifth embodiment)
In the present embodiment, the configuration of the integrated valve 13 is changed with respect to the first embodiment. Other configurations are the same as those in the first embodiment.

  As shown in FIG. 13, the integrated valve 13 of the present embodiment is provided with a first four-way valve 134 and a second four-way valve 135 inside a body 131. A general structure can be adopted as the first four-way valve 134 and the second four-way valve 135.

  In this way, the first and second communication states shown in FIG. 13 can be switched by combining the two four-way valves 134 and 135 and switching the communication state of the two four-way valves 134 and 135. The combination of the inflow port and the outflow port that communicate with each other in the first and second communication states is the same as that in the first embodiment.

  Also according to the present embodiment, the effects (1) to (3) and (5) to (7) of the first embodiment are exhibited.

(Sixth embodiment)
In this embodiment, a slide-type six-way valve 200 shown in FIGS. 14 and 15 is employed instead of the integrated valve 13 described in the first embodiment. The six-way valve 200 is the same as that described in Japanese Patent No. 3983896. Other configurations are the same as those in the first embodiment.

  The six-way valve 200 includes a main body 201 having first to third inlets A1 to A3 and first to third outlets B1 to B3. Connection pipes are connected to the first to third inlets A1 to A3 and the first to third outlets B1 to B3, respectively.

  A valve seat 202 and a slide part 203 are accommodated in the main body 201. The slide unit 203 includes a pair of disk-shaped valves 204, a slide member 205 that connects the pair of disk-shaped valves 204, and a slide valve 206 attached to the slide member 205.

  Although not shown, the valve seat 202 is formed with valve ports communicating with the second and third inlets A2 and A3 and the first to third outlets B1 to B3. A communication path that connects two adjacent valve ports is formed.

  The six-way valve 200 includes a pilot valve 210 connected to the body 201 via first to third pressure equalizing pipes 207, 208, and 209. In the pilot valve 210, a plunger needle 212 and a needle 213 are accommodated in a body 211 of the pilot valve 210, and these move in the axial direction when the electromagnetic coil 214 is turned on / off.

  One end of first to third pressure equalizing pipes 207, 208, and 209 is connected to the body 211 of the pilot valve 210, and the first and second pressure equalizing pipes 207 are moved by the axial movement of the flanger needle 212 and the needle 213. , 208 or the second and third pressure equalizing pipes 208, 209 are in communication with each other. The other end of the first pressure equalizing pipe 207 is communicated with one of the left and right spaces 221 of the disc-shaped valve 204 of the main body 201, and the other end of the third pressure equalizing pipe 209 is connected to the disc-shaped valve 204 of the main body 201. It communicates with the other 222 of the left and right spaces. The other end of the second pressure equalizing pipe 208 communicates with the third outlet B3.

  In the six-way valve 200, the pilot valve 210 controls the communication state of the pressure equalizing pipes 207 to 209, whereby a pressure difference is generated in the left and right spaces 221 and 222 of the disc-like valve 204 of the body body 201. The slide part 203 moves in the axial direction. At this time, the slide valve 206 moves together with the slide portion 203, so that the first communication state shown in FIG. 14 and the second communication state shown in FIG. 15 are switched. The combination of the inflow port and the outflow port that communicate with each other in the first and second communication states is the same as that in the first embodiment.

  Also according to the present embodiment, the effects (1) to (3) and (5) to (7) of the first embodiment are exhibited.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be appropriately modified within the scope described in the claims as follows.

  (1) In the first embodiment, the second three-way valve 133 of the integrated valve 13 is a non-electric type, but may be an electric type such as the first three-way valve 132. Similarly, the second three-way valve 133 of the fourth embodiment may be electrically operated.

  (2) In the fifth embodiment, the first four-way valve 134 and the second four-way valve 135 are provided in one body 131, and the first four-way valve 134 and the second four-way valve 135 are integrated. The first four-way valve 134 and the second four-way valve 135 may be separated. In this case, the order changing means is constituted by two devices.

  (3) In each above-mentioned embodiment, although the 1st, 2nd outdoor heat exchange parts 16 and 17 were constituted by one outdoor heat exchanger 18, the 1st and 2nd outdoor heat exchange parts 16 and 17 were changed. You may comprise with a separate heat exchanger.

  (4) In each of the above-described embodiments, the air passage of the indoor condenser 12 is blocked by the air mix door 34 so that the indoor condenser 12 does not exhibit the heat dissipation function in the cooling mode. Alternatively, the refrigerant may be caused to flow around the indoor condenser 12. That is, the refrigeration cycle apparatus 10 includes a bypass passage through which the refrigerant bypasses the indoor condenser 12 and an opening / closing means for opening / closing the bypass passage, and the opening / closing means opens the bypass passage in the cooling mode. A refrigerant may be allowed to flow through the bypass passage. In this case, the opening / closing means for opening and closing the bypass passage constitutes the refrigerant circuit switching means.

  (5) In each of the embodiments described above, the first expansion valve 15 is fully opened in order to prevent the first expansion valve 15 from depressurizing during the cooling mode. Instead, the first expansion valve 15 is The refrigerant may flow around by detour. That is, the refrigeration cycle apparatus 10 includes a bypass passage through which the refrigerant bypasses the first expansion valve 15 and the opening and closing means for opening and closing the bypass passage, and the opening and closing means opens the bypass passage in the cooling mode. A refrigerant may be allowed to flow through the bypass passage. In this case, the opening / closing means for opening and closing the bypass passage constitutes the refrigerant circuit switching means.

  (6) In each embodiment described above, the case where the operation mode is selected by the selection switch has been described. However, the control device 40 may automatically select the operation mode.

  (7) In each embodiment described above, the operation mode includes the cooling mode, the heating mode, and the first and second dehumidifying and heating modes. However, even if the first and second dehumidifying and heating modes are not provided. good.

  (8) In each of the above-described embodiments, the example in which the refrigeration cycle apparatus 10 of the present invention is applied to the vehicle air conditioner 1 for an electric vehicle has been described. However, the present invention is not limited to this. For example, the refrigeration cycle apparatus 10 of the present invention may be applied to an air conditioner for a vehicle such as a hybrid vehicle that obtains a driving force for traveling from an engine (internal combustion engine) and a traveling electric motor. Moreover, you may apply the refrigerating-cycle apparatus 10 of this invention to a stationary air conditioner etc.

  (9) The above-described embodiments are not irrelevant to each other, and can be appropriately combined unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 10 Refrigeration cycle apparatus 11 Compressor 12 Indoor condenser (heat radiator)
13 Integrated valve (order change means)
14 Receiver 15 First expansion valve (first decompression means)
16 1st outdoor heat exchange part 17 2nd outdoor heat exchange part 19 2nd expansion valve (2nd pressure reduction means)
20 Indoor evaporator (evaporator)
23 Bypass passage 25 Bypass passage

Claims (5)

A refrigeration cycle apparatus applied to an air conditioner that performs a cooling mode for cooling air blown into an air-conditioning target space and a heating mode for heating the blown air,
A compressor (11) for compressing and discharging the refrigerant;
A heat radiator (12) for exchanging heat between the refrigerant discharged from the compressor (11) and the blown air to dissipate the refrigerant;
A receiver (14) that is disposed downstream of the radiator with respect to the refrigerant flow, separates the gas-liquid of the refrigerant, and flows out the liquid-phase refrigerant,
A first outdoor heat exchange section (16) that is disposed downstream of the radiator with respect to the refrigerant flow and exchanges heat between the refrigerant and the outside air;
A second outdoor heat exchange section (17) that is disposed downstream of the first outdoor heat exchange section and the receiver and that exchanges heat between the refrigerant and the outside air;
Order changing means (13, 132, 133, 200) for changing the order in which the refrigerant flows in the first outdoor heat exchanger and the receiver on the upstream side of the refrigerant flow from the second outdoor heat exchanger,
An evaporator (20) that is disposed on the upstream side of the blower air flow from the radiator, heat-exchanges the refrigerant and the blown air, and evaporates the refrigerant;
First decompression means (15) for decompressing the refrigerant flowing into the first outdoor heat exchange section;
Second decompression means (19) for decompressing the refrigerant flowing into the evaporator,
In the heating mode, the order changing means sets the receiver first in the heating mode and the first outdoor heat exchange unit in the rear, and in the cooling mode, the first outdoor heat exchange unit first and the receiver. After
In the heating mode, a bypass passage that bypasses the compressor → the radiator → the receiver → the first pressure reducing unit → the first outdoor heat exchange unit → the second outdoor heat exchange unit or the second outdoor heat exchange unit ( 23, 25) are switched to a refrigerant circuit through which the refrigerant flows,
In the cooling mode, the compressor, the first outdoor heat exchange unit, the receiver, the second outdoor heat exchange unit, the second decompression unit, and the evaporator can be switched to a refrigerant circuit through which the refrigerant flows. A refrigeration cycle apparatus characterized by comprising: The air conditioner performs a dehumidifying heating mode in which the blown air is cooled and dehumidified, and the dehumidified blown air is heated.
Both of the first and second pressure reducing means are constituted by a variable throttle mechanism capable of changing the throttle opening,
In the first dehumidifying and heating mode, the order changing means sets the receiver to flow first in the first dehumidifying and heating mode, and after the first outdoor heat exchanging unit, and in the second dehumidifying and heating mode, the first outdoor heat exchanging unit. First, the receiver behind,
In the first dehumidifying and heating mode, bypass the compressor → the radiator → the receiver → the first pressure reducing unit → the first outdoor heat exchange unit → the second outdoor heat exchange unit or the second outdoor heat exchange unit. It is switched to a refrigerant circuit through which refrigerant flows in the order of bypass passage → second pressure reducing means → evaporator.
During the second dehumidifying heating mode, the compressor → the radiator → the first pressure reducing means → the first outdoor heat exchange unit → the receiver → the second outdoor heat exchange unit → the second pressure reducing means → the evaporator. 2. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is configured to be able to be switched to a refrigerant circuit through which refrigerant flows in order. The order changing means includes a first inlet (A1) into which the refrigerant discharged from the compressor flows, a first outlet (B1) from which the refrigerant flows out toward the refrigerant inlet of the receiver, The second inflow port (A2) into which the refrigerant flows, the second outflow port (B2) from which the refrigerant flows out toward the refrigerant inlet side of the first outdoor heat exchange unit, and the refrigerant after flowing out of the first outdoor heat exchange unit A single body (130) having a third inflow port (A3) to flow in and a third outflow port (B3) from which the refrigerant flows out toward the refrigerant inlet side of the second outdoor heat exchange section;
Inside the body, the first inlet (A1) and the first outlet (B1) communicate with each other, the second inlet (A2) and the second outlet (B2) communicate with each other, A first communication state in which the third inlet (A3) and the third outlet (B3) communicate with each other, and the first inlet (A1) and the second outlet (B2) communicate with each other; The third inflow port (A3) and the first outflow port (B1) communicate with each other, and the second inflow port (A2) and the third outflow port (B3) communicate with each other. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is configured to be switchable. The order changing means includes
An electric first three-way valve (132) provided in the body and communicating between the first inlet (A1) and one of the first and second outlets (B1, B2);
A first check valve (83) provided inside the body and between the first outlet (B1) and the third inlet (A3);
A second check valve (85) provided inside the body and between the second outlet (B2) and the second inlet (A2);
A second three-way valve (133) that is provided inside the body and communicates with one of the second and third inlets (A2, A3) and the third outlet (B3);
The first check valve communicates the first outlet with the third inlet when the refrigerant pressure at the third inlet is higher than the refrigerant pressure at the first outlet. When the refrigerant pressure at the outlet is higher than the refrigerant pressure at the third inlet, the gap between the first outlet and the third inlet is shut off,
The second check valve causes the second outlet and the second inlet to communicate with each other when the refrigerant pressure at the second inlet is higher than the refrigerant pressure at the second outlet. When the refrigerant pressure at the outlet is higher than the refrigerant pressure at the second inlet, the gap between the second outlet and the second inlet is shut off,
The second three-way valve includes a third check valve (91) provided between the second inlet (A2) and the third outlet (B3), the third inlet (A3), A fourth check valve (92) provided between the third outlet (B3) and mechanically interlocking with the third check valve;
When the refrigerant pressure at the second inlet (A2) is higher than the refrigerant pressure at the third inlet (A3), the third and fourth check valves are connected to the second inlet (A2) and the The third outlet (B3) is blocked and the third inlet (A3) and the third outlet (B3) are communicated, and the refrigerant pressure at the third inlet (A3) is When the refrigerant pressure is higher than the second inlet (A2), the third inlet (A3) and the third outlet (B3) are blocked, and the second inlet (A2) and the The refrigeration cycle apparatus according to claim 3, wherein the third outlet (B3) is in communication. The order changing means includes
The first inlet (A1) into which the refrigerant discharged from the compressor flows, the first outlet (B1) from which the refrigerant flows out toward the refrigerant inlet of the receiver, and the second into which the refrigerant flows out from the receiver. An inflow port (A2), a second outflow port (B2) through which the refrigerant flows out toward the refrigerant inlet side of the first outdoor heat exchange unit, and a third inflow port through which the refrigerant after flowing out of the first outdoor heat exchange unit flows (A3), a third outlet (B3) through which the refrigerant flows out toward the refrigerant inlet side of the second outdoor heat exchange section, and a fourth outlet (B4) through which the refrigerant flows out toward the bypass passage (25). ) A first body (131) having
A fourth inflow port (A4) communicating with the third outflow port (B3) via the second outdoor heat exchanger, and a fifth inflow port communicating with the fourth outflow port (B4) via the bypass passage. (A5) and a fifth outlet (B5) through which the refrigerant flowing in from one of the fourth and fifth inlets (A4, A5) flows out, and is disposed apart from the first body. 2 bodies (261),
An electrically driven first three-way valve (132) provided in the first body and communicating between the first inlet (A1) and one of the first and second outlets (B1, B2); ,
A first check valve (83) provided inside the first body and between the first outlet (B1) and the third inlet (A3);
A second check valve (85) provided in the first body and between the second outlet (B2) and the second inlet (A2);
A second three-way valve (133) provided inside the second body and communicating one of the fourth and fifth inlets (A4, A5) with the fifth outlet (B5);
The first check valve communicates the first outlet with the third inlet when the refrigerant pressure at the third inlet is higher than the refrigerant pressure at the first outlet. When the refrigerant pressure at the outlet is higher than the refrigerant pressure at the third inlet, the gap between the first outlet and the third inlet is shut off,
The second check valve causes the second outlet and the second inlet to communicate with each other when the refrigerant pressure at the second inlet is higher than the refrigerant pressure at the second outlet. When the refrigerant pressure at the outlet is higher than the refrigerant pressure at the second inlet, the gap between the second outlet and the second inlet is shut off,
The second three-way valve includes a third check valve (91) provided between the fourth inlet (A4) and the fifth outlet (B5), and the fifth inlet (A5). A fourth check valve (92) provided between the fifth outlet (B5) and mechanically interlocking with the third check valve;
The third check valve and the fourth check valve are connected to the fourth inlet (A4) when the refrigerant pressure at the fourth inlet (A4) is higher than the refrigerant pressure at the fifth inlet (A5). The fifth outlet (B5) is blocked, and the fifth inlet (A5) and the fifth outlet (B5) are communicated with each other. The refrigerant pressure at the fifth inlet (A5) is When the refrigerant pressure is higher than the fourth inlet (A4), the fifth inlet (A5) and the fifth outlet (B5) are blocked, and the fourth inlet (A4) and the The refrigeration cycle apparatus according to claim 1 or 2, wherein the fifth outlet (B5) communicates with the refrigeration cycle apparatus.

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