WO2020071097A1 - Refrigeration cycle device - Google Patents

Refrigeration cycle device

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Publication number
WO2020071097A1
WO2020071097A1 PCT/JP2019/036255 JP2019036255W WO2020071097A1 WO 2020071097 A1 WO2020071097 A1 WO 2020071097A1 JP 2019036255 W JP2019036255 W JP 2019036255W WO 2020071097 A1 WO2020071097 A1 WO 2020071097A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
unit
cooling
heat exchange
pressure
Prior art date
Application number
PCT/JP2019/036255
Other languages
French (fr)
Japanese (ja)
Inventor
伊藤　誠司
寛幸 小林
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2020071097A1 publication Critical patent/WO2020071097A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series

Definitions

  • the present disclosure relates to a refrigeration cycle device including a liquid storage unit.
  • Patent Document 1 discloses a refrigeration cycle apparatus including an accumulator as a liquid storage unit.
  • the accumulator is a low-pressure storage unit that separates gas-liquid refrigerant flowing out of the evaporator and stores the separated low-pressure liquid-phase refrigerant.
  • the cooling capacity of the evaporator is obtained by integrating the enthalpy difference ⁇ ie obtained by subtracting the enthalpy of the refrigerant on the inlet side of the evaporator from the enthalpy of the refrigerant on the outlet side of the evaporator, and the flow rate (mass flow rate) of the refrigerant flowing through the evaporator. It can be defined by a value or the like. Therefore, in order to improve the cooling capacity of the evaporator, it is effective to increase the enthalpy difference ⁇ ie.
  • the accumulator is connected to the refrigerant outlet side of the evaporator, so that the outlet side refrigerant of the evaporator approaches the saturated gas-phase refrigerant. Therefore, it is difficult to increase the enthalpy difference ⁇ ie by increasing the enthalpy of the refrigerant on the outlet side of the evaporator.
  • a refrigeration cycle apparatus including a liquid storage unit capable of sufficiently improving the cooling capacity of an evaporator.
  • a refrigeration cycle device includes a compressor, an outdoor heat exchanger, a decompression unit, an evaporator, and a low-pressure side liquid storage unit.
  • the compressor compresses and discharges the refrigerant.
  • the outdoor heat exchanger exchanges heat between the refrigerant discharged from the compressor and the outside air.
  • the pressure reducing unit reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger.
  • the evaporator evaporates the refrigerant flowing out of the decompression unit to cool the cooling target fluid.
  • the low-pressure side liquid storage part can separate the gas-liquid of the refrigerant flowing out of the evaporator and store the separated low-pressure liquid-phase refrigerant.
  • the outdoor heat exchanger has a first heat exchange unit, a high-pressure liquid storage unit, and a second heat exchange unit.
  • the first heat exchange unit exchanges heat between the discharged refrigerant and the outside air.
  • the high-pressure side liquid storage section can separate the gas-liquid of the refrigerant flowing out of the first heat exchange section and store the separated high-pressure liquid-phase refrigerant.
  • the second heat exchange unit exchanges heat between the refrigerant flowing out of the high-pressure side liquid storage unit and the outside air.
  • the throttle opening of the pressure reducing section is controlled so that the low-pressure liquid-phase refrigerant is stored in the low-pressure side liquid storage section.
  • the throttle opening of the pressure reducing section is controlled so that the high-pressure liquid-phase refrigerant is stored in the high-pressure side liquid storage section.
  • a refrigeration cycle in which the excess refrigerant of the cycle is stored as the low-pressure liquid-phase refrigerant in the low-pressure side liquid storage section can be configured.
  • a refrigeration cycle in which the excess refrigerant of the cycle is stored in the high-pressure side liquid storage portion as the high-pressure liquid-phase refrigerant can be configured.
  • the high-pressure liquid-phase refrigerant is stored in the high-pressure side liquid storage part, so that the refrigerant flowing out of the outdoor heat exchanger can be cooled without unnecessarily increasing the refrigerant condensation pressure in the outdoor heat exchanger.
  • the degree of cooling can be increased. That is, the enthalpy of the refrigerant on the inlet side of the evaporator can be reduced without unnecessarily increasing the refrigerant condensation pressure in the outdoor heat exchanger.
  • the excess refrigerant of the cycle is stored in the high-pressure side liquid storage section, the low-pressure gas-phase refrigerant having a degree of superheat can flow into the low-pressure side liquid storage section. Therefore, the enthalpy of the refrigerant on the outlet side of the evaporator can be increased.
  • the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side of the evaporator from the enthalpy of the refrigerant on the outlet side of the evaporator can be increased as compared with the first cooling mode, thereby improving the cooling capacity. it can. That is, according to the refrigeration cycle apparatus of one embodiment of the present disclosure, it is possible to provide a refrigeration cycle apparatus including a liquid storage unit capable of sufficiently improving the cooling capacity of the evaporator.
  • 1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. It is a typical sectional view of the outdoor heat exchanger of a 1st embodiment. It is a typical sectional view of the accumulator of a 1st embodiment. It is a block diagram which shows the electric control part of the vehicle air conditioner of 1st Embodiment. It is a flowchart which shows the control processing at the time of the cooling mode of 1st Embodiment. It is explanatory drawing which represented typically the state inside the outdoor heat exchanger at the time of the 1st cooling mode of 1st Embodiment.
  • FIG. 4 is an explanatory diagram illustrating a relationship between a throttle opening degree of the expansion valve for cooling according to the first embodiment and a state of a refrigerant.
  • FIG. 3 is a Mollier chart showing a change in a state of a refrigerant in a cooling mode according to the first embodiment. It is a typical sectional view of the outdoor heat exchanger of a 2nd embodiment.
  • the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1.
  • the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40, and the like, as shown in the overall configuration diagram of FIG.
  • the refrigeration cycle apparatus 10 has a function of cooling the blast air blown into the vehicle compartment and a high-temperature side heat medium circulating through the high-temperature side heat medium circuit 40 in the vehicle air conditioner 1 in order to perform air conditioning of the vehicle interior. Heat. Therefore, the fluid to be cooled in the refrigeration cycle device 10 is blast air.
  • the refrigeration cycle apparatus 10 is further configured to be able to switch between a refrigerant circuit in a cooling mode, a refrigerant circuit in a series dehumidifying and heating mode, a refrigerant circuit in a parallel dehumidifying and heating mode, and a refrigerant circuit in a heating mode.
  • the cooling mode is an operation mode in which the air in the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment.
  • the in-line dehumidification and heating mode is an operation mode in which the cooled and dehumidified blast air is reheated and blown out into the vehicle interior to perform dehumidification and heating in the vehicle interior.
  • the parallel dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blast air is reheated with a higher heating capacity than the serial dehumidifying and heating mode and is blown out into the vehicle interior to perform dehumidification and heating in the vehicle interior.
  • the heating mode is an operation mode for heating the vehicle interior by heating the blown air and blowing the air into the vehicle interior.
  • the refrigeration cycle apparatus 10 can execute the operation of the first cooling mode and the second cooling mode as the cooling mode.
  • the first cooling mode is a first cooling mode for cooling the blast air with a normal cooling capacity.
  • the second cooling mode is a second cooling mode for cooling the blown air with a higher cooling capacity than the first cooling mode.
  • the refrigeration cycle apparatus 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant, and is a vapor compression type in which the pressure of the refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a subcritical refrigeration cycle. Further, the refrigerant contains refrigeration oil for lubricating the compressor 11. Part of the refrigerating machine oil circulates through the cycle together with the refrigerant.
  • HFO-based refrigerant specifically, R1234yf
  • the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10.
  • the compressor 11 is arranged in a vehicle hood.
  • the compressor 11 is an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor.
  • the rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 described later.
  • the inlet of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the outlet of the compressor 11.
  • the water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature heat medium circulating in the high-temperature heat medium circuit 40 flows.
  • the water-refrigerant heat exchanger 12 is a heating heat exchanger that heats the high-temperature heat medium by exchanging heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage.
  • the outlet of the coolant passage of the water-refrigerant heat exchanger 12 is connected to the inlet of a first three-way joint 13a having three inflow ports that communicate with each other.
  • a three-way joint one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
  • the refrigeration cycle device 10 includes a second three-way joint 13b to a fourth three-way joint 13d.
  • the basic configuration of the second to fourth three-way joints 13b to 13d is the same as that of the first three-way joint 13a.
  • first three-way joint 13a to the fourth three-way joint 13d use one of the three inlets and outlets as an inlet, and use two of them as outlets, a branching part for branching the flow of the refrigerant is provided. Become. When two of the three inlets and outlets are used as inlets and one is used as an outlet, it serves as a merging portion for merging the flows of the refrigerant.
  • An inlet of the heating expansion valve 14a is connected to one of the outlets of the first three-way joint 13a.
  • One of the inlets of the second three-way joint 13b is connected to the other outlet of the first three-way joint 13a via a bypass passage 22a.
  • An on-off valve 15a for dehumidification is arranged in the bypass passage 22a.
  • the dehumidifying on-off valve 15a is an electromagnetic valve that opens and closes the bypass passage 22a. Further, the refrigeration cycle device 10 includes a heating on-off valve 15b as described later. The basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.
  • the on-off valve 15a for dehumidification and the on-off valve 15b for heating can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage. Therefore, the on-off valve 15a for dehumidification and the on-off valve 15b for heating are refrigerant circuit switching units that switch the refrigerant circuit of the cycle. The operations of the dehumidifying on-off valve 15a and the heating on-off valve 15b are controlled by a control voltage output from the control device 60.
  • the heating expansion valve 14a depressurizes the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 at least in a heating mode in which the vehicle interior is heated, and the flow rate (mass flow rate) of the refrigerant flowing downstream.
  • the heating expansion valve 14a is an electric variable throttle mechanism that includes a valve body configured to change the opening degree of the throttle and an electric actuator that changes the opening degree of the valve body.
  • the refrigeration cycle device 10 includes a cooling expansion valve 14b, as described later.
  • the basic configuration of the cooling expansion valve 14b is the same as that of the heating expansion valve 14a.
  • the heating expansion valve 14a and the cooling expansion valve 14b have a fully open function that functions as a mere refrigerant passage without exerting a flow rate adjusting action and a refrigerant pressure reducing action by fully opening the valve opening degree, and a full valve opening degree. It has a fully closed function of closing the refrigerant passage by closing.
  • the heating expansion valve 14a and the cooling expansion valve 14b can switch the refrigerant circuit in each operation mode by the fully open function and the fully closed function. Therefore, the heating expansion valve 14a and the cooling expansion valve 14b also have a function as a refrigerant circuit switching unit.
  • the operation of the heating expansion valve 14a and the cooling expansion valve 14b is controlled by a control signal (control pulse) output from the control device 60.
  • the refrigerant inflow port 162d side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a.
  • the outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by a cooling fan (not shown).
  • the outdoor heat exchanger 16 is arranged on the front side inside the vehicle hood. For this reason, when the vehicle is traveling, traveling wind can be applied to the outdoor heat exchanger 16.
  • the outdoor heat exchanger 16 of the present embodiment has a so-called tank-and-tube type heat exchanger structure.
  • the outdoor heat exchanger 16 includes a plurality of tubes 161, a pair of tanks 162 and 163, a corrugated fin 164, a modulator 165, and the like. Each of these constituent members is formed of the same kind of metal (in this embodiment, an aluminum alloy) having excellent heat conductivity.
  • the components of the outdoor heat exchanger 16 are integrated by brazing.
  • the plurality of tubes 161 are tubular members through which a refrigerant flows.
  • the tube 161 is a flat tube having a flat cross section.
  • the tube 161 is formed in a shape extending in the horizontal direction.
  • Each of the tubes 161 is vertically stacked at regular intervals so that the flat surfaces (so-called flat surfaces) of the outer surfaces are parallel to each other.
  • forty tubes 161 are stacked and arranged.
  • the corrugated fin 164 is a heat exchange fin that is disposed in an air passage formed between the adjacent tubes 161 and that promotes heat exchange between the refrigerant and the outside air.
  • FIG. 2 for clarification of illustration, only a part of the tube 161 and the corrugated fin 164 are shown, but the tube 161 and the corrugated fin 164 are arranged over the entire area of the heat exchange unit. .
  • the pair of tanks 162 and 163 are respectively connected to both ends of the tube 161. Inside the pair of tanks 162 and 163, a distribution space for distributing the refrigerant to the plurality of tubes 161 or a collecting space for collecting the refrigerant flowing out of the plurality of tubes 161 is formed.
  • the plurality of tubes 161 are divided into a plurality of (two in the present embodiment) paths.
  • the path in the tank-and-tube type heat exchanger means that the refrigerant in the same distribution space formed in one tank is directed in the same direction toward the same collective space formed in the other tank. It can be defined as a refrigerant flow path formed by a group of tubes flowing to the flow path.
  • the separator 162a is disposed at the center in the vertical direction of one of the tanks 162. For this reason, the internal space of one tank 162 is partitioned into two spaces having substantially the same volume in the vertical direction. Further, a separator 163a is arranged at the center in the vertical direction of the other tank 163. For this reason, the internal space of the other tank 163 is partitioned into two spaces having substantially the same volume in the vertical direction.
  • a refrigerant inflow port 162d through which the refrigerant flowing out of the heating expansion valve 14a flows is connected to a portion forming a space below the one tank 162. Therefore, the lower space in one tank 162 supplies the refrigerant to a plurality of (specifically, 20) tubes 161 connected to a portion of the one tank 162 that forms the lower space. It becomes the first distribution space 162b for distribution.
  • the space below the other tank 163 collects the refrigerant flowing out from a plurality of (specifically, 20) tubes 161 connected to a portion forming the space below the other tank 163. It becomes the first set space 163b to be made. Then, a first path is formed by a group of tubes through which the refrigerant flows from the first distribution space 162b to the first collection space 163b.
  • a refrigerant outlet port 162e that allows the refrigerant to flow toward the inlet side of the third three-way joint 13c is connected to a portion forming a space above the one tank 162. Therefore, the space above one tank 162 collects the refrigerant flowing out from a plurality of (specifically, 20) tubes 161 connected to a portion of the one tank 162 that forms the space above. The second set space 162c is obtained.
  • the space above the other tank 163 distributes the refrigerant to a plurality of (specifically, 20) tubes 161 connected to a portion forming the space above the other tank 163.
  • pass is formed by the tube group which flows a refrigerant
  • a coolant outlet 163d for allowing the coolant to flow out of the first collecting space 163b is formed in a portion of the other tank 163 where the first collecting space 163b is formed.
  • the refrigerant outlet 163d is arranged on the uppermost side of a portion of the other tank 163 where the first collecting space 163b is formed.
  • the refrigerant outlet 163d is connected to the refrigerant inlet 165a side of the modulator section 165.
  • the modulator 165 separates the gas-liquid of the high-pressure refrigerant that has exchanged heat with the outside air when flowing through the first path, and stores the separated high-pressure liquid-phase refrigerant as surplus refrigerant in the cycle. It is a side liquid storage part.
  • the modulator section 165 is formed in a bottomed cylindrical shape whose central axis extends in the stacking direction of the plurality of tubes 161 (that is, in the up-down direction).
  • the refrigerant inlet 165a of the modulator section 165 is disposed on the lowermost side of the modulator section 165.
  • the refrigerant outlet 165b of the modulator 165 is connected to the refrigerant inlet 163e formed in the other tank 163.
  • the refrigerant inlet 163e is formed in a portion of the other tank 163 that forms the second distribution space 163c. Further, the refrigerant inlet 163e is positioned on the lower side so that the refrigerant flowing from the modulator section 165 into the second distribution space 163c has a velocity component from the lower side to the upper side.
  • the heat exchange section 16a is configured.
  • the plurality of tubes 161 constituting the second path constitute a second heat exchange section 16b for exchanging heat between the refrigerant flowing out of the modulator section 165 and the outside air.
  • the first heat exchange unit 16a is disposed below the second heat exchange unit 16b in the vertical direction. Further, the number of tubes 161 constituting the first pass is the same as the number of tubes 161 constituting the second pass. Therefore, the heat exchange area for exchanging heat between the refrigerant and the outside air in the first heat exchange section 16a is equal to the heat exchange area for exchanging heat between the refrigerant and the outside air in the second heat exchange section 16b.
  • the refrigerant outlet 163d is arranged on the uppermost side of the first heat exchange part 16a means that the refrigerant outlet 163d is opened only at the uppermost part in the vertical direction of the member constituting the first heat exchange part 16a. It is not limited to the meaning that it is.
  • the refrigerant outlet 163d is opened so as to include the uppermost part in the vertical direction or a position slightly lower than the uppermost part in the vertical direction of the member constituting the first heat exchange unit 16a, and is substantially opened at the uppermost part. It is a meaning including.
  • the refrigerant inlet 165a of the modulator part 165 is arranged at the lowermost side of the modulator part 165 is limited to the meaning that the refrigerant inlet 165a is opened only at the lowermost part of the modulator part 165 in the vertical direction. Not done. This means that the refrigerant inlet 165a is opened so as to include the lowermost portion of the modulator portion 165 in the vertical direction or a position slightly lower than the lowermost portion in the vertical direction, and substantially opens at the lowermost portion.
  • the inflow port side of the third three-way joint 13c is connected to the refrigerant outflow port 162e of the outdoor heat exchanger 16.
  • One of the outlets of the third three-way joint 13c is connected to one of the inlets of the fourth three-way joint 13d via a heating passage 22b.
  • a heating opening / closing valve 15b that opens and closes the refrigerant passage is arranged in the heating passage 22b.
  • the other inflow side of the second three-way joint 13b is connected to the other outflow port of the third three-way joint 13c.
  • a check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c to the second three-way joint 13b, and prohibits the refrigerant from flowing from the second three-way joint 13b to the third three-way joint 13c.
  • the inlet of the cooling expansion valve 14b is connected to the outlet of the second three-way joint 13b.
  • the cooling expansion valve 14b is a pressure reducing unit that reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing downstream at least in the cooling mode.
  • the refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14b.
  • the indoor evaporator 18 is arranged in an air-conditioning case 31 of an indoor air-conditioning unit 30 described later.
  • the indoor evaporator 18 blows air by exchanging heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14b and the blast air blown from the blower 32 to evaporate the low-pressure refrigerant and exert an endothermic effect on the low-pressure refrigerant.
  • This is a cooling heat exchanger that cools air.
  • the refrigerant outlet of the indoor evaporator 18 is connected to the inlet side of the evaporation pressure regulating valve 20.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 18.
  • the evaporating pressure adjusting valve 20 is configured by a mechanical variable throttle mechanism that increases the valve opening as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a frost formation suppression temperature (1 ° C. in the present embodiment) capable of suppressing frost formation on the indoor evaporator 18.
  • the other inlet side of the fourth three-way joint 13d is connected to the outlet of the evaporation pressure regulating valve 20.
  • the refrigerant outlet 212a side of the accumulator 21 is connected to the outlet of the fourth three-way joint 13d.
  • the accumulator 21 is a low-pressure storage unit that separates gas-liquid refrigerant flowing out of the indoor evaporator 18 in a cooling mode or the like and stores the separated low-pressure liquid-phase refrigerant as surplus refrigerant in the cycle.
  • the suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet 213b of the accumulator 21.
  • the accumulator 21 has a refrigerant container 211, an inlet pipe 212, an outlet pipe 213, and the like.
  • the refrigerant container 211 is made of metal (in this embodiment, aluminum) formed in a bottomed cylindrical shape.
  • the refrigerant container 211 is arranged so that its central axis extends in the vertical direction.
  • a storage space for separating gas-liquid of the refrigerant and storing the separated liquid-phase refrigerant is formed inside the refrigerant container 211.
  • the inlet pipe 212 is a piping member formed of the same metal as the refrigerant container 211.
  • the inlet-side pipe 212 is formed in a shape extending in the up-down direction.
  • One end of the inlet-side pipe 212 is disposed above the refrigerant container 211 and forms a refrigerant inlet 212a through which the refrigerant flowing out of the fourth three-way joint 13d flows.
  • the other end of the inlet-side pipe 212 is disposed inside the refrigerant container 211 and forms a refrigerant outlet 212b.
  • the outlet-side pipe 213 is a piping member formed of the same metal as the refrigerant container 211.
  • the outlet side pipe 213 is formed in a shape having a U-shaped curved portion.
  • One end of the outlet pipe 213 is arranged above the outside of the refrigerant container 211 to form a gas-phase refrigerant outlet 213b that allows the gas-phase refrigerant to flow toward the suction port of the compressor 11.
  • the other end of the outlet-side pipe 213 is disposed inside the refrigerant container 211 and forms a gas-phase refrigerant inlet 213a through which the gas-phase refrigerant separated inside the refrigerant container 211 flows.
  • the gas-phase refrigerant inlet 213 a is above the liquid surface and further above the refrigerant outlet 212 b of the inlet pipe 212. Are located in Therefore, the liquid-phase refrigerant does not flow into the outlet-side pipe 213 from the gas-phase refrigerant inlet 213a.
  • the curved portion of the outlet-side pipe 213 is disposed below the liquid surface.
  • An oil return hole 213c is formed at the lowermost portion of the curved portion.
  • the oil return hole 213c is a hole formed for sucking the liquid-phase refrigerant in which the refrigerating machine oil is dissolved and sucking the liquid-phase refrigerant into the compressor 11 when the liquid-phase refrigerant is stored in the accumulator 21.
  • the high-temperature-side heat medium circuit 40 is a heat medium circulation circuit that circulates the high-temperature-side heat medium.
  • the high-temperature side heat medium ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid, or the like, an antifreeze, or the like can be used.
  • the high-temperature heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat medium pump 41, a heater core 42, and the like.
  • the high-temperature heat medium pump 41 is a water pump for pumping the high-temperature heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.
  • the outlet of the water passage of the water-refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42.
  • the heater core 42 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 18.
  • the heater core 42 is arranged inside the air conditioning case 31 of the indoor air conditioning unit 30.
  • the heat medium outlet of the heater core 42 is connected to the suction side of the high-temperature side heat medium pump 41.
  • each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. I have.
  • the indoor air-conditioning unit 30 is for blowing blast air adjusted to an appropriate temperature for air-conditioning the vehicle interior to an appropriate location in the vehicle interior.
  • the indoor air-conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the forefront of the vehicle interior.
  • the indoor air-conditioning unit 30 has a blower 32, an indoor evaporator 18, a heater core 42, and the like housed in an air-conditioning case 31 that forms an air passage for blowing air.
  • the air-conditioning case 31 has a certain degree of elasticity and is formed of a resin (for example, polypropylene) having excellent strength.
  • An inside / outside air switching device 33 is disposed on the most upstream side of the airflow of the air conditioning case 31.
  • the inside / outside air switching device 33 switches and introduces inside air (vehicle interior air) and outside air (vehicle outside air) into the air conditioning case 31.
  • the operation of the electric actuator for driving the inside / outside air switching device 33 is controlled by a control signal output from the control device 60.
  • a blower 32 is disposed downstream of the inside / outside air switching device 33 in the blown air flow.
  • the blower 32 blows the air taken in through the inside / outside air switching device 33 toward the vehicle interior.
  • the blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor.
  • the rotation speed (that is, the blowing capacity) of the blower 32 is controlled by the control voltage output from the control device 60.
  • the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 18 is arranged on the upstream side of the flow of the blown air from the heater core 42.
  • a cool air bypass passage 35 is provided in the air-conditioning case 31 to allow the air blown through the indoor evaporator 18 to flow around the heater core 42. Further, an air mix door 34 is arranged on the downstream side of the air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the air flow of the heater core 42.
  • the air mix door 34 adjusts a flow rate ratio of a flow rate of the blown air passing through the heater core 42 and a flow rate of the blown air passing through the cool air bypass passage 35 among the blown air after passing through the indoor evaporator 18. Department.
  • the operation of the electric actuator for driving the air mix door 34 is controlled by a control signal output from the control device 60.
  • the mixing space is disposed downstream of the air flow of the heater core 42 and the cool air bypass passage 35 in the air conditioning case 31.
  • the mixing space is a space for mixing the blast air heated by the heater core 42 and the blast air that has not passed through the cool air bypass passage 35 and is not heated. Further, an opening hole for blowing out the blown air mixed and temperature-adjusted in the mixing space into the vehicle compartment is disposed downstream of the airflow of the air-conditioning case 31.
  • the face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment.
  • the foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air flow ratio of the air flow passing through the heater core 42 and the air flow passing through the cool air bypass passage 35 by the air mixing door 34. Then, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle interior is adjusted.
  • Face doors, foot doors, and defroster doors are arranged on the upstream side of the airflow from the face opening, the foot opening, and the defroster opening.
  • the face door, the foot door, and the defroster door are opening / closing units that open and close corresponding opening holes according to the operation mode.
  • the control device 60 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits. Then, various calculations and processes are performed based on the air conditioning control program stored in the ROM, and the operations of the various control target devices 11, 14a, 14b, 15a, 15b, 32, 41, etc. connected to the output side are performed. Control.
  • an inside air temperature sensor 61 On the input side of the control device 60, as shown in the block diagram of FIG. 4, an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, first to fourth refrigerant temperature sensors 64a to 64d, and evaporation.
  • the control unit 60 receives detection signals from these sensor groups.
  • the inside air temperature sensor 61 is an inside air temperature detection unit that detects the vehicle interior temperature (inside air temperature) Tr.
  • the outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam.
  • the solar radiation sensor 63 is a solar radiation amount detecting unit that detects a solar radiation amount Ts irradiated into the vehicle interior.
  • the first refrigerant temperature sensor 64a is a discharged refrigerant temperature detection unit that detects the temperature T1 of the refrigerant discharged from the compressor 11.
  • the second refrigerant temperature sensor 64b is a second refrigerant temperature detector that detects the temperature T2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects the temperature T3 of the refrigerant flowing out of the outdoor heat exchanger 16.
  • the fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detector that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18.
  • the evaporator temperature sensor 64f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18.
  • the evaporator temperature sensor 64f of this embodiment specifically detects the temperature of the heat exchange fins of the indoor evaporator 18.
  • the first refrigerant pressure sensor 65a is a first refrigerant pressure detector that detects the pressure P1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the second refrigerant pressure sensor 65b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the indoor evaporator 18.
  • the high-temperature heat medium temperature sensor 66a is a high-temperature heat medium temperature detection unit that detects the high-temperature heat medium temperature TWH, which is the temperature of the high-temperature heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12.
  • the air-conditioning air temperature sensor 69 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.
  • an operation panel 70 arranged near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches provided on the operation panel 70 An operation signal is input.
  • Specific examples of various operation switches provided on the operation panel 70 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, a blowout mode switching switch, and the like.
  • the automatic switch is an automatic control operation setting unit that sets or cancels the automatic control operation of the vehicle air conditioner 1.
  • the air conditioner switch is a cooling request unit that requests the indoor evaporator 18 to cool the blown air.
  • the air volume setting switch is an air volume setting unit for manually setting the air volume of the blower 32.
  • the temperature setting switch is a target temperature setting unit that sets a target temperature Tset in the vehicle compartment.
  • the blowout mode is a blowout mode switching setting unit for manually setting the blowout mode.
  • the control device 60 of the present embodiment has an integrated control unit for controlling various control target devices connected to the output side. Therefore, the configuration (hardware and software) that controls the operation of each control target device constitutes a control unit that controls the operation of each control target device.
  • the configuration that controls the refrigerant discharge capacity of the compressor 11 constitutes the discharge capacity control unit 60a.
  • the configuration for controlling the operation of the cooling expansion valve 14b forms the pressure reducing control unit 60b.
  • the vehicle air conditioner 1 of the present embodiment can perform cooling, dehumidifying heating, and heating of the vehicle interior. Further, the refrigeration cycle apparatus 10 switches the operation among a cooling mode, a series dehumidifying and heating mode, a parallel dehumidifying and heating mode, and a heating mode for air conditioning in the vehicle compartment.
  • the switching of each operation mode of the refrigeration cycle device 10 is performed by executing an air conditioning control program.
  • the air conditioning control program is executed when the automatic switch of the operation panel 70 is turned on (ON) and the automatic control operation is set.
  • a target outlet temperature TAO which is a target temperature of the outlet air to be blown into the vehicle interior
  • the target outlet temperature TAO is calculated by the following equation F1.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ As + C (F1)
  • Tset is a target temperature in the vehicle interior (vehicle interior setting temperature) set by the temperature setting switch
  • Tr is the internal air temperature detected by the internal air temperature sensor 61
  • Tam is the external air temperature detected by the external air temperature sensor 62
  • Ts Is the amount of solar radiation detected by the solar radiation sensor 63.
  • Kset, Kr, Kam, and Ks are control gains
  • C is a correction constant.
  • the target outlet temperature TAO is equal to or higher than the cooling reference temperature ⁇
  • the outside air temperature Tam is higher than the predetermined dehumidifying heating reference temperature ⁇ .
  • the operation mode is switched to the in-line dehumidification heating mode.
  • the operation mode is switched to the parallel dehumidification heating mode.
  • the cooling mode is mainly executed when the outside air temperature is relatively high, such as in summer.
  • the in-line dehumidification heating mode is mainly performed in the spring or autumn.
  • the parallel dehumidifying and heating mode is mainly executed when it is necessary to heat the blown air with a higher heating capacity than in the series dehumidifying and heating mode, such as early spring or late autumn.
  • the heating mode is mainly executed at a low outside air temperature in winter. The operation in each operation mode will be described below.
  • the switching between the first cooling mode and the second cooling mode is performed by executing the control flow shown in FIG.
  • the control flow shown in FIG. 5 is executed as a subroutine of the main routine of the air conditioning control program.
  • the control flow shown in FIG. 5 is executed at predetermined intervals when the cooling mode is selected in the main routine. Details of the control flow in FIG. 5 will be described later.
  • the control device 60 causes the heating expansion valve 14a to be in a fully open state and the cooling expansion valve 14b to be in a throttled state in which a decompression effect is exerted. Further, the control device 60 closes the dehumidifying on-off valve 15a and closes the heating on-off valve 15b.
  • the discharge port of the compressor 11, the water-refrigerant heat exchanger 12 (the heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, and the cooling expansion valve 14b A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the indoor evaporator 18, the evaporating pressure regulating valve 20, the accumulator 21, and the suction port of the compressor 11 is configured.
  • control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and outputs the determined control signals and the like to various control target devices.
  • control device 60 determines a control signal for adjusting the rotation speed Nc of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 64f approaches the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined based on the target outlet temperature TAO with reference to a cooling mode control map stored in the control device 60 in advance.
  • the target evaporator temperature TEO is determined to increase as the target outlet temperature TAO increases. Further, the target evaporator temperature TEO is determined to a value within a range (specifically, 1 ° C. or more) in which frost formation on the indoor evaporator 18 can be suppressed.
  • the control device 60 determines the control voltage to be output to the high-temperature side heat transfer medium pump 41 so as to exhibit a predetermined hydraulic pumping capacity for the cooling mode.
  • control device 60 controls the output to the electric actuator for the air mixing door based on the target blowing temperature TAO, the evaporator temperature Tefin, and the high-temperature heat medium temperature TWH detected by the high-temperature heat medium temperature sensor 66a. Determine the signal. This control signal is determined such that the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.
  • a refrigeration cycle in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a condenser and the indoor evaporator 18 functions as an evaporator is configured. Therefore, in the cooling mode, the inside of the vehicle compartment can be cooled by blowing the air cooled by the indoor evaporator 18 to the heater core 42 and blowing it out into the vehicle compartment.
  • step S10 it is determined whether or not the evaporator temperature Tefin has reached the target evaporator temperature TEO.
  • step S10 If it is determined in step S10 that the evaporator temperature Tefin has reached the target evaporator temperature TEO, the process proceeds to step S30, and the control of the first cooling mode shown in steps S30 to S50 is performed. If it is determined in step S10 that the evaporator temperature Tefin is not at the target evaporator temperature TEO, that is, if the evaporator temperature Tefin is higher than the target evaporator temperature TEO, the process proceeds to step S20. .
  • step S20 it is determined whether or not the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax.
  • the maximum rotation speed NcMax a maximum rotation speed determined from the durability performance of the compressor 11 or a maximum rotation speed determined for noise suppression or the like in accordance with operating conditions can be adopted.
  • step S20 If it is determined in step S20 that the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the process proceeds to step S100, and the operation in the second cooling mode shown in steps S100 to S140 is performed.
  • step S20 when it is determined that the rotation speed Nc of the compressor 11 has not reached the maximum rotation speed NcMax, that is, it is determined that the rotation speed Nc of the compressor 11 has not reached the maximum rotation speed NcMax. In this case, the process proceeds to step S30, and the operation in the first cooling mode is performed.
  • a target supercooling degree SCO1 for the first cooling mode is determined as a target value of the supercooling degree SC of the refrigerant flowing out of the outdoor heat exchanger 16 and flowing into the cooling expansion valve 14b, and step S40 is performed. Proceed to.
  • the target degree of supercooling SCO1 is determined with reference to a control map shown in the control characteristic diagram of step S30 in FIG. In this control map, the target degree of supercooling SCO1 is determined based on the outside temperature Tam so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • step S40 the change amount ⁇ EVC1 of the throttle opening of the cooling expansion valve 14b is determined so that the subcooling degree SC approaches the target subcooling degree SCO1, and the process proceeds to step S50.
  • the degree of supercooling SC is calculated using the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.
  • step S50 the amount of change ⁇ EVC in the throttle opening of the cooling expansion valve 14b is determined, and the process proceeds to step S60.
  • step S50 the change amount ⁇ EVC1 determined in step S40 is adopted as the change amount ⁇ EVC.
  • step S60 the change amount ⁇ EVC determined in step S70 is added to the previous throttle opening EVCn-1 of the cooling expansion valve 14b, and the current throttle opening EVCn is determined. Then, the control signal to be output to the cooling expansion valve 14b is determined so that the current throttle opening EVCn is obtained, and the process returns to the main routine.
  • a target supercooling degree SCO2 for the second cooling mode is determined as a target value of the supercooling degree SC, and the process proceeds to step S110.
  • the target degree of supercooling SCO2 is determined with reference to a control map shown in the control characteristic diagram of step S100 in FIG. In this control map, the target supercooling degree SCO2 is determined so as to be a value obtained by adding a predetermined amount (10 ° C. in the present embodiment) to the target supercooling degree SCO1 determined in step S30.
  • step S110 the amount of change ⁇ EVC1 in the throttle opening of the cooling expansion valve 14b is determined so that the subcooling degree SC approaches the target subcooling degree SCO2, and the process proceeds to step S120.
  • the target superheat degree SHO2 for the second cooling mode is determined as the target value of the superheat degree SH of the refrigerant on the outlet side of the indoor evaporator 18, and the process proceeds to Step S130.
  • the target superheat degree SHO2 is determined to be 10 ° C.
  • step S130 the amount of change ⁇ EVC2 in the throttle opening of the cooling expansion valve 14b is determined so that the superheat degree SH approaches the target superheat degree SHO2, and the process proceeds to step S140.
  • step S140 the change amount ⁇ EVC of the throttle opening of the cooling expansion valve 14b is determined, and the process proceeds to step S60.
  • step S140 the larger value of the change amount ⁇ EVC1 determined in step S110 and the change amount ⁇ EVC2 determined in step S130 is adopted as the change amount ⁇ EVC.
  • the target supercooling degree SCO2 determined in step S100 is set to be a sufficiently high value. More specifically, even if the throttle opening of the cooling expansion valve 14b is determined so that the actual superheat degree SH becomes the target superheat degree SHO2, the actual supercooling degree SC does not reach the target supercooling degree SCO2. Is set to a high value.
  • step S110 the variation ⁇ EVC1 determined in step S110 becomes a negative value in order to decrease the throttle opening of the cooling expansion valve 14b, and tends to be smaller than the variation ⁇ EVC2 determined in step S130. Therefore, in step S70 of the second cooling mode, the change amount ⁇ EVC2 is often adopted as the change amount ⁇ EVC.
  • steps S30 and S100 are target supercooling degree determination units that determine the target supercooling degrees SCO1 and SCO2 of the refrigerant flowing into the cooling expansion valve 14b.
  • Step S120 is a target superheat degree determination unit that determines the target superheat degree SHO2 of the refrigerant on the outlet side of the indoor evaporator 18.
  • steps S10 and S20 it is assumed that the condition for determining that the cooling capacity of the blown air in the indoor evaporator 18 is insufficient is satisfied. That is, it is assumed that the cooling capacity shortage condition is satisfied. More specifically, when the evaporator temperature Tefin has not reached the target evaporator temperature TEO and the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the cooling capacity shortage condition has been satisfied. And
  • FIGS. 6 to 8 schematically show the distribution of the liquid-phase refrigerant in the outdoor heat exchanger 16 in each operation mode, and the region where the liquid-phase refrigerant is distributed is schematically shown by hatching.
  • I have.
  • the throttle openings of the cooling expansion valve 14b in the states shown in FIGS. 6 to 8 are indicated by (A) to (C), respectively.
  • a change in the state of the refrigerant in the first cooling mode is indicated by a broken line
  • a change in the state of the refrigerant in the second cooling mode is indicated by a thick solid line.
  • the throttle opening of the cooling expansion valve 14b is controlled such that the supercooling degree SC approaches the target supercooling degree SCO1.
  • This throttle opening is indicated by the throttle opening (A) in FIG.
  • a region on the upstream side of the refrigerant flow of the first heat exchange unit 16a and the second heat exchange unit 16b of the outdoor heat exchanger 16 is a condensing unit that condenses the refrigerant.
  • a region on the downstream side of the refrigerant flow of the second heat exchange unit 16b is a subcooling unit that supercools the liquid-phase refrigerant. Therefore, the excess refrigerant of the cycle is stored in the accumulator 21 as shown by the liquid level H in the accumulator 21 in FIG.
  • the compressor 11 sends the relatively high dryness gas-liquid two-phase containing the liquid-phase refrigerant in which the refrigerating machine oil is dissolved, from the accumulator 21.
  • the refrigerant (point a1 in FIG. 10) is sucked and compressed.
  • the refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 16 and exchanges heat with the outside air to radiate heat (points b1 to c1 in FIG. 10).
  • the supercooling degree SC of the refrigerant (point c1 in FIG. 10) flowing out of the outdoor heat exchanger 16 approaches the target supercooling degree SCO1.
  • the refrigerant flowing out of the outdoor heat exchanger 16 is decompressed by the cooling expansion valve 14b (point c1 to point d1 in FIG. 10).
  • the refrigerant decompressed by the cooling expansion valve 14b absorbs heat from the blown air in the indoor evaporator 18 and evaporates (from point d1 to point a1 in FIG. 10). Thereby, the blown air is cooled.
  • the refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 21 and is separated into gas and liquid.
  • the blast air is cooled so that the COP of the cycle becomes a maximum value.
  • the target supercooling degree SCO2 determined to be higher than the target supercooling degree SCO1 is adopted as the target value of the supercooling degree SC. You. For this reason, in order to increase the degree of supercooling SC from the first cooling mode, the throttle opening of the cooling expansion valve 14b decreases. In FIG. 9, the throttle opening (A) decreases to the throttle opening (B).
  • the first heat exchange section 16a of the outdoor heat exchanger 16 becomes a condenser section. Further, the entire area of the second heat exchange section 16b is filled with the high-pressure liquid-phase refrigerant to become a supercooling section.
  • the surplus refrigerant stored in the accumulator 21 is smaller than in the first cooling mode. That is, the liquid level H decreases. Further, the refrigerant condensation pressure in the outdoor heat exchanger 16 increases. Furthermore, since the target degree of supercooling SCO2 is set to a value sufficiently higher than the target degree of supercooling SCO1, the actual degree of supercooling SC has not reached the target degree of supercooling SCO2.
  • the throttle opening of the cooling expansion valve 14b further decreases.
  • the throttle opening (B) decreases to the throttle opening (C).
  • the inside of the modulator 165 is also filled with the high-pressure liquid-phase refrigerant. That is, the surplus refrigerant of the cycle stored in the accumulator 21 moves into the modulator section 165.
  • the superheat degree SH of the refrigerant in the accumulator 21 and the refrigerant on the outlet side of the indoor evaporator 18 increases to the target superheat degree SHO2 (specifically, 10 ° C.).
  • the compressor 11 sucks the gaseous refrigerant having the degree of superheat (point a2 in FIG. 10) from the accumulator 21 and compresses it, as indicated by the thick solid line in the Mollier diagram in FIG. I do.
  • the refrigerant discharged from the compressor 11 exchanges heat with the outside air and radiates heat in the outdoor heat exchanger 16 (point b2 to point c2 in FIG. 10). Then, the excess refrigerant of the cycle becomes high-pressure liquid-phase refrigerant and is stored in the modulator section 165.
  • the refrigerant flowing out of the outdoor heat exchanger 16 is decompressed by the cooling expansion valve 14b (from point c2 to point d2 in FIG. 10).
  • the refrigerant decompressed by the cooling expansion valve 14b absorbs heat from the blown air in the indoor evaporator 18 and evaporates (from point d2 to point a2 in FIG. 10). Thereby, the blown air is cooled.
  • the degree of superheat SH of the refrigerant on the outlet side of the indoor evaporator 18 approaches the target degree of superheat SHO2.
  • the superheated refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 21.
  • the enthalpy difference ⁇ ie2 obtained by subtracting the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 from the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 is equal to that in the first cooling mode. Is larger than the enthalpy difference ⁇ ie1. That is, the refrigeration cycle device 10 in the second cooling mode can cool the blown air with a higher cooling capacity than in the first cooling mode.
  • (B) In-line dehumidification and heating mode In the in-series dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to the throttled state and sets the cooling expansion valve 14b to the throttled state. Further, the control device 60 closes the dehumidifying on-off valve 15a and closes the heating on-off valve 15b.
  • the compressor 11 in the serial dehumidification heating mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporation
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the device 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • control device 60 similarly to the cooling mode, the control device 60 appropriately determines control signals and the like output to various control target devices connected to the output side, and sends the determined control signals and the like to the various control target devices. Output.
  • control device 60 transmits a control signal output to the heating expansion valve 14a and the cooling expansion valve 14b such that the blast air temperature TAV detected by the conditioned air temperature sensor 69 approaches the target outlet temperature TAO. decide. Therefore, in the series dehumidification heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
  • control device 60 controls the control signal so as to decrease the throttle opening of the heating expansion valve 14a and increase the throttle opening of the cooling expansion valve 14b as the target outlet temperature TAO increases. To determine.
  • a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a condenser and the indoor evaporator 18 functions as an evaporator is configured.
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is reduced with the rise of the target outlet temperature TAO, and the outdoor heat exchange is performed.
  • the heat radiation amount of the refrigerant in the vessel 16 can be reduced.
  • the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air in the heater core 42 can be improved.
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is reduced with an increase in the target outlet temperature TAO, and the outdoor heat exchange is performed.
  • the amount of heat absorbed by the refrigerant in the vessel 16 can be increased.
  • the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air in the heater core 42 can be improved.
  • the air that has been cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed. Further, by adjusting the throttle openings of the heating expansion valve 14a and the cooling expansion valve 14b, the amount of refrigerant radiated in the water-refrigerant heat exchanger 12 is adjusted, and the heating capacity of the blower air in the heater core 42 is adjusted. can do.
  • (C) Parallel dehumidification and heating mode In the parallel dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to a throttled state and sets the cooling expansion valve 14b to a throttled state. Further, the control device 60 opens the dehumidifying on-off valve 15a and opens the heating on-off valve 15b.
  • the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b (heating on-off valve 15b), A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the accumulator 21 and the compressor 11 is configured.
  • the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a (dehumidifying on-off valve 15a), the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 in this order.
  • a vapor compression refrigeration cycle in which the refrigerant circulates is configured. That is, a refrigeration cycle in which the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to the refrigerant flow is configured.
  • control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and outputs the determined control signals and the like to various control target devices.
  • control device 60 determines a control signal for controlling the rotation speed Nc of the compressor 11 such that the pressure P1 detected by the first refrigerant pressure sensor 65a approaches the target condensing pressure PDO.
  • this control map it is determined that the target condensing pressure PDO increases as the target outlet temperature TAO increases.
  • control device 60 determines a control signal to be output to heating expansion valve 14a and cooling expansion valve 14b such that COP approaches the maximum value. Therefore, in the parallel dehumidification heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
  • the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed.
  • the evaporation temperature of the refrigerant in the outdoor heat exchanger 16 can be made lower than the evaporation temperature of the refrigerant in the indoor evaporator 18 without causing frost on the indoor evaporator 18 by the action of the evaporation pressure adjusting valve 20. it can.
  • the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased more than in the in-line dehumidifying and heating mode, and the heating capacity of the blown air can be increased.
  • (D) Heating Mode In the heating mode, the control device 60 sets the heating expansion valve 14a to the throttled state and sets the cooling expansion valve 14b to the fully closed state. Further, the control device 60 closes the dehumidifying on-off valve 15a and opens the heating on-off valve 15b.
  • control device 60 similarly to the parallel dehumidifying and heating mode, the control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and determines the determined control signals and the like for various control targets. Output to device.
  • control device 60 determines a control signal to be output to the heating expansion valve 14a such that the COP approaches the local maximum value, as in the first cooling mode. Therefore, in the heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
  • a refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 16 functions as an evaporator. Therefore, in the heating mode, the inside of the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment.
  • the operation of various operation modes can be performed by switching the refrigerant circuit.
  • the vehicle air conditioner 1 comfortable air conditioning in the vehicle compartment can be realized.
  • the refrigeration cycle device 10 of the present embodiment includes an accumulator 21 which is a low-pressure side liquid storage unit. Therefore, even if the heat exchanger functioning as a condenser changes according to the operation mode, the surplus refrigerant can be reliably stored in the accumulator 21.
  • the outlet refrigerant of the indoor evaporator 18 approaches the saturated gas-phase refrigerant, so that the enthalpy difference ⁇ ie is increased by increasing the enthalpy of the outlet refrigerant of the indoor evaporator 18. It is difficult.
  • the refrigerant drawn into the compressor 11 is a gas-liquid two-phase refrigerant having a high degree of dryness.
  • the refrigerant on the outlet side of the indoor evaporator 18 becomes a gas-liquid two-phase refrigerant having a lower enthalpy than the saturated gas-phase refrigerant, and it is difficult to further increase the enthalpy difference ⁇ ie.
  • Means for increasing the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 16 in the first cooling mode and reducing the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 to increase the enthalpy difference ⁇ ie may be considered.
  • the first cooling mode in which the excess refrigerant is stored in the accumulator 21 can be switched to the second cooling mode in which the excess refrigerant is stored in the modulator section 165.
  • the refrigerant flowing out of the outdoor heat exchanger 16 does not needlessly increase the refrigerant condensation pressure in the outdoor heat exchanger 16.
  • the degree of supercooling can be increased. That is, the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 can be reduced without unnecessarily increasing the refrigerant condensing pressure in the outdoor heat exchanger 16.
  • the surplus refrigerant of the cycle is stored in the modulator unit 165, the low-pressure gas-phase refrigerant having a degree of superheat can flow into the accumulator 21. Therefore, the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 can be increased.
  • the enthalpy difference ⁇ ie can be expanded more than in the first cooling mode, and the cooling capacity of the indoor evaporator 18 can be improved. That is, according to the refrigeration cycle device 10 of the present embodiment, the cooling capacity of the indoor evaporator 18 can be sufficiently improved.
  • the target degree of supercooling is increased. According to this, when the cooling capacity of the blown air in the indoor evaporator 18 is insufficient, it is possible to surely shift from the first cooling mode to the second cooling mode and improve the cooling capacity.
  • the target degree of superheat is increased when shifting to the second cooling mode. According to this, when the mode shifts to the second cooling mode, the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 can be reduced, so that the cooling capacity can be further improved.
  • the heat exchange area of the second heat exchange unit 16b is filled so that the second heat exchange unit 16b is filled with the high-pressure liquid-phase refrigerant. Is set. According to this, in the second cooling mode, the entire area of the second heat exchange section 16b can be used as a subcooling section, and the excess refrigerant flowing out of the outdoor heat exchanger 16 and flowing into the cooling expansion valve 14b can be used.
  • the cooling degree SC can be made closer to the target supercooling degree SCO2.
  • the physique of the outdoor heat exchanger 16 is set to be equal to that of an outdoor heat exchanger (so-called condenser) of a general refrigeration cycle device applied to a vehicle air conditioner.
  • the heat exchange area of the first heat exchange section 16a is set to be equal to the heat exchange area of the second heat exchange section 16b. According to this, it has been confirmed that the subcooling degree SC can be reliably increased in the second cooling mode to approach the target supercooling degree SCO2.
  • the refrigerant outlet 163d of the first heat exchange unit 16a is arranged on the uppermost side of the first heat exchange unit 16a. According to this, it is possible to prevent the volume of the modulator section 165 from unnecessarily expanding.
  • the refrigerant inlet 165a of the modulator section 165 is arranged at the lowermost side of the modulator section 165. According to this, when flowing into the modulator section 165 flowing out of the first heat exchange section 16a, it is difficult to form a region in which the refrigerant flows and stagnates, and the refrigerant melts into the liquid-phase refrigerant on the bottom side inside the modulator section 165. The stagnation of the refrigerating machine oil can be suppressed.
  • the first heat exchange unit 16a is disposed below the second heat exchange unit 16b.
  • the refrigerant flowing from the inner space of the modulator section 165 into the second distribution space 163c of the other tank 163 has a velocity component from the lower side to the upper side.
  • the refrigerant flowing into the second distribution space 163c is unevenly distributed below the second distribution space 163c by the action of gravity. Can be suppressed. Therefore, a uniform flow rate of the refrigerant can be distributed to each of the tubes 161 constituting the second path, and the refrigerant can be uniformly evaporated in the second heat exchange unit 16b.
  • a refrigerant inflow port 162d is connected to a portion forming a space above the one tank 162.
  • a refrigerant outflow port 162e is connected to a portion forming a space below the one tank 162.
  • the first distribution space 162b is formed above the one tank 162. Further, a second collecting space 162c is formed below one tank 162. Further, a first collecting space 163b is formed above the other tank 163. Further, a second distribution space 163c is formed below the other tank 163.
  • the flow direction of the refrigerant is reversed with respect to the outdoor heat exchanger 16 of the first embodiment.
  • the heat exchange area of the first heat exchange section 16a is equal to the heat exchange area of the second heat exchange section 16b. Therefore, also in the present embodiment, the heat exchange area of the second heat exchange unit 16b is set so that the second heat exchange unit 16b is filled with the high-pressure liquid-phase refrigerant in the second cooling mode. .
  • the example in which the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1 has been described, but the application of the refrigeration cycle device 10 is not limited thereto.
  • the present invention is not limited to vehicles, and may be applied to stationary air conditioners, refrigeration devices, and the like.
  • Each configuration of the refrigeration cycle device is not limited to the configuration disclosed in the above embodiment.
  • an electric compressor is employed as the compressor 11
  • an engine-driven compressor may be employed.
  • a variable displacement compressor configured to adjust the refrigerant discharge capacity by changing the discharge capacity may be adopted.
  • R1234yf is adopted as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a mixed refrigerant obtained by mixing a plurality of types of these refrigerants may be employed.
  • the refrigeration cycle apparatus 10 that can be switched to a plurality of operation modes has been described.
  • the switching of the operation mode of the refrigeration cycle apparatus 10 is not limited to this. At least, if the switching between the first cooling mode and the second cooling mode can be executed, the cooling capacity exhibited by the indoor evaporator 18 can be sufficiently improved.
  • the heating unit constituted by the components of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is employed, but the heating unit is not limited to this.
  • an indoor condenser that directly exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air may be adopted, and the indoor condenser may be arranged in the air-conditioning case 31 like the heater core 42.
  • the cooling capacity shortage condition when the evaporator temperature Tefin has reached the target evaporator temperature TEO and the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the cooling capacity shortage condition has been satisfied.
  • the cooling capacity shortage condition is not limited to this.
  • the blast air temperature TAV detected by the conditioned air temperature sensor 69 when the blast air temperature TAV detected by the conditioned air temperature sensor 69 is higher than the target outlet temperature TAO, it may be determined that the cooling capacity shortage condition has been satisfied.

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Abstract

The purpose of the present invention is to provide a refrigeration cycle device comprising a fluid storage unit capable of sufficiently improving the cooling capacity of an evaporator. The refrigeration cycle device comprises a compressor (11), an outdoor heat exchanger (16), a decompression unit (14b), an evaporator (18), and a low pressure-side fluid storage unit (21). The outdoor heat exchanger (16) has a first heat exchange unit (16a), a high pressure-side fluid storage unit (165), and a second heat exchange unit (16b). During a first cooling mode in which fluid to be cooled is cooled in the evaporator (18), the aperture of the decompression unit (14b) is controlled such that a low-pressure liquid-phase reagent is stored inside the low pressure-side fluid storage unit (21). During a second cooling mode in which fluid to be cooled is cooled in the evaporator (18) at a higher cooling capacity than in the first cooling mode, the aperture of the decompression unit (14b) is controlled such that a high-pressure liquid-phase reagent is stored inside the high pressure-side fluid storage unit (165).

Description

冷凍サイクル装置Refrigeration cycle device 関連出願の相互参照Cross-reference of related applications
　本出願は、２０１８年１０月５日に出願された日本特許出願番号２０１８－１８９６９６号に基づくもので、ここにその記載内容を援用する。 This application is based on Japanese Patent Application No. 2018-189696, filed on October 5, 2018, the contents of which are incorporated herein by reference.
　本開示は、貯液部を備える冷凍サイクル装置に関する。 The present disclosure relates to a refrigeration cycle device including a liquid storage unit.
　従来、貯液部を備える冷凍サイクル装置が知られている。貯液部は、サイクル内で余剰となっている余剰冷媒を液相冷媒として貯える。例えば、特許文献１には、貯液部としてアキュムレータを備える冷凍サイクル装置が開示されている。アキュムレータは、蒸発器から流出した冷媒の気液を分離して、分離された低圧液相冷媒を貯える低圧側貯液部である。 Conventionally, a refrigeration cycle device including a liquid storage unit is known. The liquid storage section stores excess refrigerant that has become excessive in the cycle as a liquid-phase refrigerant. For example, Patent Document 1 discloses a refrigeration cycle apparatus including an accumulator as a liquid storage unit. The accumulator is a low-pressure storage unit that separates gas-liquid refrigerant flowing out of the evaporator and stores the separated low-pressure liquid-phase refrigerant.
特開２０１２－２２５６３７号公報JP 2012-225637 A
　アキュムレータを備える冷凍サイクル装置では、特許文献１のように、運転モードに応じて凝縮器として機能する熱交換器が変化しても、アキュムレータに余剰冷媒を確実に貯えることができる。 冷凍 In a refrigeration cycle device including an accumulator, as in Patent Document 1, even if the heat exchanger functioning as a condenser changes according to the operation mode, the excess refrigerant can be reliably stored in the accumulator.
　しかしながら、アキュムレータを備える冷凍サイクル装置では、蒸発器にて発揮される送風空気の冷却能力を向上させにくい。その理由は、アキュムレータを備える冷凍サイクル装置では、蒸発器の出口側冷媒のエンタルピから蒸発器の入口側冷媒のエンタルピを減算したエンタルピ差Δｉｅを拡大させにくいからである。 However, in the refrigeration cycle device including the accumulator, it is difficult to improve the cooling capacity of the blown air exerted by the evaporator. The reason is that, in the refrigeration cycle device including the accumulator, it is difficult to increase the enthalpy difference Δie obtained by subtracting the enthalpy of the refrigerant on the inlet side of the evaporator from the enthalpy of the refrigerant on the outlet side of the evaporator.
　ここで、蒸発器における冷却能力は、蒸発器の出口側冷媒のエンタルピから蒸発器の入口側冷媒のエンタルピを減算したエンタルピ差Δｉｅと、蒸発器を流通する冷媒の流量（質量流量）との積算値等で定義することができる。従って、蒸発器における冷却能力を向上させるためには、エンタルピ差Δｉｅを拡大させることが有効である。 Here, the cooling capacity of the evaporator is obtained by integrating the enthalpy difference Δie obtained by subtracting the enthalpy of the refrigerant on the inlet side of the evaporator from the enthalpy of the refrigerant on the outlet side of the evaporator, and the flow rate (mass flow rate) of the refrigerant flowing through the evaporator. It can be defined by a value or the like. Therefore, in order to improve the cooling capacity of the evaporator, it is effective to increase the enthalpy difference Δie.
　ところが、アキュムレータを備える冷凍サイクル装置では、アキュムレータが蒸発器の冷媒出口側に接続されるので、蒸発器の出口側冷媒が飽和気相冷媒に近づいてしまう。従って、蒸発器の出口側冷媒のエンタルピを増加させることによって、エンタルピ差Δｉｅを拡大させることは難しい。 However, in the refrigeration cycle device including the accumulator, the accumulator is connected to the refrigerant outlet side of the evaporator, so that the outlet side refrigerant of the evaporator approaches the saturated gas-phase refrigerant. Therefore, it is difficult to increase the enthalpy difference Δie by increasing the enthalpy of the refrigerant on the outlet side of the evaporator.
　これに対して、凝縮器として機能する熱交換器から流出する冷媒の過冷却度を増加させて、蒸発器の入口側冷媒のエンタルピを低減させる手段が考えられる。 に 対 し て On the other hand, a method of increasing the degree of supercooling of the refrigerant flowing out of the heat exchanger functioning as a condenser to reduce the enthalpy of the refrigerant on the inlet side of the evaporator can be considered.
　ところが、凝縮器として機能する熱交換器から流出する冷媒の過冷却度を増加させると、この熱交換器における冷媒凝縮圧力が上昇してしまうので、サイクル構成機器の耐久寿命に悪影響を与えてしまうおそれがある。そのため、蒸発器の入口側のエンタルピを低減させることによって、エンタルピ差Δｉｅを拡大させることには限界がある。 However, if the degree of supercooling of the refrigerant flowing out of the heat exchanger functioning as a condenser is increased, the refrigerant condensing pressure in the heat exchanger increases, which adversely affects the durability life of the cycle components. There is a risk. Therefore, there is a limit in increasing the enthalpy difference Δie by reducing the enthalpy on the inlet side of the evaporator.
　従って、アキュムレータを備える冷凍サイクル装置では、蒸発器における冷却能力を向上させにくい。 Therefore, in the refrigeration cycle device including the accumulator, it is difficult to improve the cooling capacity of the evaporator.
　本開示は、上記点に鑑み、蒸発器における冷却能力を充分に向上させることが可能な貯液部を備える冷凍サイクル装置を提供することを目的とする。 In view of the above, it is an object of the present disclosure to provide a refrigeration cycle apparatus including a liquid storage unit capable of sufficiently improving the cooling capacity of an evaporator.
　本開示の一態様の冷凍サイクル装置は、圧縮機と、室外熱交換器と、減圧部と、蒸発器と、低圧側貯液部と、を備える。 冷凍 A refrigeration cycle device according to one embodiment of the present disclosure includes a compressor, an outdoor heat exchanger, a decompression unit, an evaporator, and a low-pressure side liquid storage unit.
　圧縮機は、冷媒を圧縮して吐出する。室外熱交換器は、圧縮機から吐出された吐出冷媒と外気とを熱交換させる。減圧部は、室外熱交換器から流出した冷媒を減圧させる。蒸発器は、減圧部から流出した冷媒を蒸発させて冷却対象流体を冷却する。低圧側貯液部は、蒸発器から流出した冷媒の気液を分離して、分離された低圧液相冷媒を貯えることができる。 The compressor compresses and discharges the refrigerant. The outdoor heat exchanger exchanges heat between the refrigerant discharged from the compressor and the outside air. The pressure reducing unit reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger. The evaporator evaporates the refrigerant flowing out of the decompression unit to cool the cooling target fluid. The low-pressure side liquid storage part can separate the gas-liquid of the refrigerant flowing out of the evaporator and store the separated low-pressure liquid-phase refrigerant.
　室外熱交換器は、第１熱交換部、高圧側貯液部、および第２熱交換部を有している。第１熱交換部は、吐出冷媒と外気とを熱交換させる。高圧側貯液部は、第１熱交換部から流出した冷媒の気液を分離して、分離された高圧液相冷媒を貯えることができる。第２熱交換部は、高圧側貯液部から流出した冷媒と外気とを熱交換させる。 外 The outdoor heat exchanger has a first heat exchange unit, a high-pressure liquid storage unit, and a second heat exchange unit. The first heat exchange unit exchanges heat between the discharged refrigerant and the outside air. The high-pressure side liquid storage section can separate the gas-liquid of the refrigerant flowing out of the first heat exchange section and store the separated high-pressure liquid-phase refrigerant. The second heat exchange unit exchanges heat between the refrigerant flowing out of the high-pressure side liquid storage unit and the outside air.
　蒸発器にて冷却対象流体を冷却する第１冷却モード時には、低圧側貯液部内に低圧液相冷媒が貯えられるように減圧部の絞り開度が制御される。 (4) In the first cooling mode in which the cooling target fluid is cooled by the evaporator, the throttle opening of the pressure reducing section is controlled so that the low-pressure liquid-phase refrigerant is stored in the low-pressure side liquid storage section.
　蒸発器にて第１冷却モードよりも高い冷却能力で冷却対象流体を冷却する第２冷却モード時には、高圧側貯液部内に高圧液相冷媒が貯えられるように減圧部の絞り開度が制御される。 In the second cooling mode in which the evaporator cools the cooling target fluid with a higher cooling capacity than in the first cooling mode, the throttle opening of the pressure reducing section is controlled so that the high-pressure liquid-phase refrigerant is stored in the high-pressure side liquid storage section. You.
　これによれば、第１冷却モード時には、サイクルの余剰冷媒を低圧液相冷媒として、低圧側貯液部内に貯える冷凍サイクルを構成することができる。また、第２冷却モード時には、サイクルの余剰冷媒を高圧液相冷媒として、高圧側貯液部内に貯える冷凍サイクルを構成することができる。 According to this, in the first cooling mode, a refrigeration cycle in which the excess refrigerant of the cycle is stored as the low-pressure liquid-phase refrigerant in the low-pressure side liquid storage section can be configured. Further, in the second cooling mode, a refrigeration cycle in which the excess refrigerant of the cycle is stored in the high-pressure side liquid storage portion as the high-pressure liquid-phase refrigerant can be configured.
　この第２冷却モードでは、高圧側貯液部内に高圧液相冷媒を貯えるので、室外熱交換器における冷媒凝縮圧力を不必要に上昇させてしまうことなく、室外熱交換器から流出する冷媒の過冷却度を増加させることができる。すなわち、室外熱交換器における冷媒凝縮圧力を不必要に上昇させてしまうことなく、蒸発器の入口側冷媒のエンタルピを低減させることができる。 In the second cooling mode, the high-pressure liquid-phase refrigerant is stored in the high-pressure side liquid storage part, so that the refrigerant flowing out of the outdoor heat exchanger can be cooled without unnecessarily increasing the refrigerant condensation pressure in the outdoor heat exchanger. The degree of cooling can be increased. That is, the enthalpy of the refrigerant on the inlet side of the evaporator can be reduced without unnecessarily increasing the refrigerant condensation pressure in the outdoor heat exchanger.
　さらに、サイクルの余剰冷媒が高圧側貯液部内に貯えられているので、低圧側貯液部へ過熱度を有する低圧気相冷媒を流入させることができる。従って、蒸発器の出口側冷媒のエンタルピを増加させることもできる。 Further, since the excess refrigerant of the cycle is stored in the high-pressure side liquid storage section, the low-pressure gas-phase refrigerant having a degree of superheat can flow into the low-pressure side liquid storage section. Therefore, the enthalpy of the refrigerant on the outlet side of the evaporator can be increased.
　その結果、第２冷却モードでは、第１冷却モードよりも、蒸発器の出口側冷媒のエンタルピから蒸発器の入口側冷媒のエンタルピを減算したエンタルピ差を拡大させて、冷却能力を向上させることができる。すなわち、本開示の一態様の冷凍サイクル装置によれば、蒸発器における冷却能力を充分に向上させることが可能な貯液部を備える冷凍サイクル装置を提供することができる。 As a result, in the second cooling mode, the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side of the evaporator from the enthalpy of the refrigerant on the outlet side of the evaporator can be increased as compared with the first cooling mode, thereby improving the cooling capacity. it can. That is, according to the refrigeration cycle apparatus of one embodiment of the present disclosure, it is possible to provide a refrigeration cycle apparatus including a liquid storage unit capable of sufficiently improving the cooling capacity of the evaporator.
第１実施形態の車両用空調装置の全体構成図である。1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. 第１実施形態の室外熱交換器の模式的な断面図である。It is a typical sectional view of the outdoor heat exchanger of a 1st embodiment. 第１実施形態のアキュムレータの模式的な断面図である。It is a typical sectional view of the accumulator of a 1st embodiment. 第１実施形態の車両用空調装置の電気制御部を示すブロック図である。It is a block diagram which shows the electric control part of the vehicle air conditioner of 1st Embodiment. 第１実施形態の冷房モード時の制御処理を示すフローチャートである。It is a flowchart which shows the control processing at the time of the cooling mode of 1st Embodiment. 第１実施形態の第１冷房モード時の室外熱交換器の内部の状態を模式的に表した説明図である。It is explanatory drawing which represented typically the state inside the outdoor heat exchanger at the time of the 1st cooling mode of 1st Embodiment. 第１実施形態の第１冷房モードから第２冷房モードへ移行する過程の室外熱交換器の内部の状態を模式的に表した説明図である。It is explanatory drawing which represented typically the internal state of the outdoor heat exchanger in the process of shifting to the 2nd cooling mode from the 1st cooling mode of 1st Embodiment. 第１実施形態の第２冷房モード時の室外熱交換器の内部の状態を模式的に表した説明図である。It is explanatory drawing which represented typically the state inside the outdoor heat exchanger at the time of the 2nd cooling mode of 1st Embodiment. 第１実施形態の冷房用膨張弁の絞り開度と冷媒の状態との関係を説明する説明図である。FIG. 4 is an explanatory diagram illustrating a relationship between a throttle opening degree of the expansion valve for cooling according to the first embodiment and a state of a refrigerant. 第１実施形態の冷房モード時の冷媒の状態の変化を示すモリエル線図である。FIG. 3 is a Mollier chart showing a change in a state of a refrigerant in a cooling mode according to the first embodiment. 第２実施形態の室外熱交換器の模式的な断面図である。It is a typical sectional view of the outdoor heat exchanger of a 2nd embodiment.
　以下に、図面を参照しながら本開示を実施するための複数の形態を説明する。各実施形態において先行する実施形態で説明した事項に対応する部分には同一の参照符号を付して重複する説明を省略する場合がある。各実施形態において構成の一部のみを説明している場合は、構成の他の部分については先行して説明した他の実施形態を適用することができる。各実施形態で具体的に組合せが可能であることを明示している部分同士の組合せばかりではなく、特に組合せに支障が生じなければ、明示してなくとも実施形態同士を部分的に組み合せることも可能である。 Hereinafter, a plurality of embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, portions corresponding to the items described in the preceding embodiment are denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each embodiment, the other embodiments described earlier can be applied to other parts of the configuration. Not only the combination of the parts that clearly indicate that a combination is possible in each embodiment, but also the embodiments may be partially combined without being specified unless there is any particular problem with the combination. Is also possible.
　（第１実施形態）
　図１～図１０を用いて、本開示の第１実施形態を説明する。本実施形態では、本開示に係る冷凍サイクル装置１０を車両用空調装置１に適用している。車両用空調装置１は、図１の全体構成図に示すように、冷凍サイクル装置１０、室内空調ユニット３０、高温側熱媒体回路４０等を備えている。 (1st Embodiment)
A first embodiment of the present disclosure will be described with reference to FIGS. In the present embodiment, the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1. The vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40, and the like, as shown in the overall configuration diagram of FIG.
　冷凍サイクル装置１０は、車両用空調装置１において、車室内の空調を行うために、車室内へ送風される送風空気を冷却する機能、および高温側熱媒体回路４０を循環する高温側熱媒体を加熱する。従って、冷凍サイクル装置１０における冷却対象流体は、送風空気である。 The refrigeration cycle apparatus 10 has a function of cooling the blast air blown into the vehicle compartment and a high-temperature side heat medium circulating through the high-temperature side heat medium circuit 40 in the vehicle air conditioner 1 in order to perform air conditioning of the vehicle interior. Heat. Therefore, the fluid to be cooled in the refrigeration cycle device 10 is blast air.
　さらに、冷凍サイクル装置１０は、冷房モードの冷媒回路、直列除湿暖房モードの冷媒回路、並列除湿暖房モードの冷媒回路、および暖房モードの冷媒回路を切り替え可能に構成されている。 The refrigeration cycle apparatus 10 is further configured to be able to switch between a refrigerant circuit in a cooling mode, a refrigerant circuit in a series dehumidifying and heating mode, a refrigerant circuit in a parallel dehumidifying and heating mode, and a refrigerant circuit in a heating mode.
　ここで、冷房モードは、送風空気を冷却して車室内へ吹き出すことによって車室内の冷房を行う運転モードである。直列除湿暖房モードは、冷却されて除湿された送風空気を再加熱して車室内へ吹き出すことによって車室内の除湿暖房を行う運転モードである。並列除湿暖房モードは、冷却されて除湿された送風空気を直列除湿暖房モードよりも高い加熱能力で再加熱して車室内へ吹き出すことによって車室内の除湿暖房を行う運転モードである。暖房モードは、送風空気を加熱して車室内へ吹き出すことによって車室内の暖房を行う運転モードである。 冷 Here, the cooling mode is an operation mode in which the air in the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment. The in-line dehumidification and heating mode is an operation mode in which the cooled and dehumidified blast air is reheated and blown out into the vehicle interior to perform dehumidification and heating in the vehicle interior. The parallel dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blast air is reheated with a higher heating capacity than the serial dehumidifying and heating mode and is blown out into the vehicle interior to perform dehumidification and heating in the vehicle interior. The heating mode is an operation mode for heating the vehicle interior by heating the blown air and blowing the air into the vehicle interior.
　これに加えて、冷凍サイクル装置１０は、冷房モードとして、第１冷房モードおよび第２冷房モードの運転を実行することができる。第１冷房モードは、通常の冷却能力で送風空気を冷却する第１冷却モードである。第２冷房モードは、第１冷房モードよりも高い冷却能力で送風空気を冷却する第２冷却モードである。 に In addition, the refrigeration cycle apparatus 10 can execute the operation of the first cooling mode and the second cooling mode as the cooling mode. The first cooling mode is a first cooling mode for cooling the blast air with a normal cooling capacity. The second cooling mode is a second cooling mode for cooling the blown air with a higher cooling capacity than the first cooling mode.
　また、冷凍サイクル装置１０では、冷媒としてＨＦＯ系冷媒（具体的には、Ｒ１２３４ｙｆ）を採用しており、圧縮機１１から吐出された吐出冷媒の圧力が冷媒の臨界圧力を超えない蒸気圧縮式の亜臨界冷凍サイクルを構成している。さらに、冷媒には、圧縮機１１を潤滑するための冷凍機油が混入されている。冷凍機油の一部は、冷媒とともにサイクルを循環している。 Further, the refrigeration cycle apparatus 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant, and is a vapor compression type in which the pressure of the refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a subcritical refrigeration cycle. Further, the refrigerant contains refrigeration oil for lubricating the compressor 11. Part of the refrigerating machine oil circulates through the cycle together with the refrigerant.
　冷凍サイクル装置１０の構成機器のうち、圧縮機１１は、冷凍サイクル装置１０において冷媒を吸入し、圧縮して吐出する。圧縮機１１は、車両ボンネット内に配置されている。圧縮機１１は、吐出容量が固定された固定容量型の圧縮機構を電動モータにて回転駆動する電動圧縮機である。圧縮機１１は、後述する制御装置６０から出力される制御信号によって、回転数（すなわち、冷媒吐出能力）が制御される。 圧 縮 Among the components of the refrigeration cycle device 10, the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10. The compressor 11 is arranged in a vehicle hood. The compressor 11 is an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor. The rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 described later.
　圧縮機１１の吐出口には、水－冷媒熱交換器１２の冷媒通路の入口側が接続されている。水－冷媒熱交換器１２は、圧縮機１１から吐出された高圧冷媒を流通させる冷媒通路と、高温側熱媒体回路４０を循環する高温側熱媒体を流通させる水通路とを有している。水－冷媒熱交換器１２は、冷媒通路を流通する高圧冷媒と、水通路を流通する高温側熱媒体とを熱交換させて、高温側熱媒体を加熱する加熱用熱交換器である。 The inlet of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the outlet of the compressor 11. The water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature heat medium circulating in the high-temperature heat medium circuit 40 flows. The water-refrigerant heat exchanger 12 is a heating heat exchanger that heats the high-temperature heat medium by exchanging heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage.
　水－冷媒熱交換器１２の冷媒通路の出口には、互いに連通する３つの流入出口を有する第１三方継手１３ａの流入口側が接続されている。このような三方継手としては、複数の配管を接合して形成されたものや、金属ブロックや樹脂ブロックに複数の冷媒通路を設けることによって形成されたものを採用することができる。 The outlet of the coolant passage of the water-refrigerant heat exchanger 12 is connected to the inlet of a first three-way joint 13a having three inflow ports that communicate with each other. As such a three-way joint, one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
　さらに、冷凍サイクル装置１０は、後述するように、第２三方継手１３ｂ～第４三方継手１３ｄを備えている。これらの第２三方継手１３ｂ～第４三方継手１３ｄの基本的構成は、第１三方継手１３ａと同様である。 冷凍 Furthermore, as described later, the refrigeration cycle device 10 includes a second three-way joint 13b to a fourth three-way joint 13d. The basic configuration of the second to fourth three-way joints 13b to 13d is the same as that of the first three-way joint 13a.
　これらの第１三方継手１３ａ～第４三方継手１３ｄは、３つの流入出口のうち１つを流入口として用い、２つを流出口として用いた際には、冷媒の流れを分岐する分岐部となる。また、３つの流入出口のうち２つを流入口として用い、１つを流出口として用いた際には、冷媒の流れを合流させる合流部となる。 When the first three-way joint 13a to the fourth three-way joint 13d use one of the three inlets and outlets as an inlet, and use two of them as outlets, a branching part for branching the flow of the refrigerant is provided. Become. When two of the three inlets and outlets are used as inlets and one is used as an outlet, it serves as a merging portion for merging the flows of the refrigerant.
　第１三方継手１３ａの一方の流出口には、暖房用膨張弁１４ａの入口側が接続されている。第１三方継手１３ａの他方の流出口には、バイパス通路２２ａを介して、第２三方継手１３ｂの一方の流入口側が接続されている。バイパス通路２２ａには、除湿用開閉弁１５ａが配置されている。 入口 An inlet of the heating expansion valve 14a is connected to one of the outlets of the first three-way joint 13a. One of the inlets of the second three-way joint 13b is connected to the other outlet of the first three-way joint 13a via a bypass passage 22a. An on-off valve 15a for dehumidification is arranged in the bypass passage 22a.
　除湿用開閉弁１５ａは、バイパス通路２２ａを開閉する電磁弁である。さらに、冷凍サイクル装置１０は、後述するように、暖房用開閉弁１５ｂを備えている。暖房用開閉弁１５ｂの基本的構成は、除湿用開閉弁１５ａと同様である。 開 閉 The dehumidifying on-off valve 15a is an electromagnetic valve that opens and closes the bypass passage 22a. Further, the refrigeration cycle device 10 includes a heating on-off valve 15b as described later. The basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.
　除湿用開閉弁１５ａおよび暖房用開閉弁１５ｂは、冷媒通路を開閉することで、各運転モードの冷媒回路を切り替えることができる。従って、除湿用開閉弁１５ａおよび暖房用開閉弁１５ｂは、サイクルの冷媒回路を切り替える冷媒回路切替部である。除湿用開閉弁１５ａおよび暖房用開閉弁１５ｂは、制御装置６０から出力される制御電圧によって、その作動が制御される。 (4) The on-off valve 15a for dehumidification and the on-off valve 15b for heating can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage. Therefore, the on-off valve 15a for dehumidification and the on-off valve 15b for heating are refrigerant circuit switching units that switch the refrigerant circuit of the cycle. The operations of the dehumidifying on-off valve 15a and the heating on-off valve 15b are controlled by a control voltage output from the control device 60.
　暖房用膨張弁１４ａは、少なくとも車室内の暖房を行う暖房モード時に、水－冷媒熱交換器１２の冷媒通路から流出した高圧冷媒を減圧させるとともに、下流側へ流出させる冷媒の流量（質量流量）を調整する。暖房用膨張弁１４ａは、絞り開度を変更可能に構成された弁体と、この弁体の開度を変化させる電動アクチュエータとを有して構成される電気式の可変絞り機構である。 The heating expansion valve 14a depressurizes the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 at least in a heating mode in which the vehicle interior is heated, and the flow rate (mass flow rate) of the refrigerant flowing downstream. To adjust. The heating expansion valve 14a is an electric variable throttle mechanism that includes a valve body configured to change the opening degree of the throttle and an electric actuator that changes the opening degree of the valve body.
　さらに、冷凍サイクル装置１０は、後述するように、冷房用膨張弁１４ｂを備えている。冷房用膨張弁１４ｂの基本的構成は、暖房用膨張弁１４ａと同様である。暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂは、弁開度を全開にすることで流量調整作用および冷媒減圧作用を殆ど発揮することなく単なる冷媒通路として機能する全開機能、および弁開度を全閉にすることで冷媒通路を閉塞する全閉機能を有している。 冷凍 Furthermore, the refrigeration cycle device 10 includes a cooling expansion valve 14b, as described later. The basic configuration of the cooling expansion valve 14b is the same as that of the heating expansion valve 14a. The heating expansion valve 14a and the cooling expansion valve 14b have a fully open function that functions as a mere refrigerant passage without exerting a flow rate adjusting action and a refrigerant pressure reducing action by fully opening the valve opening degree, and a full valve opening degree. It has a fully closed function of closing the refrigerant passage by closing.
　そして、この全開機能および全閉機能によって、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂは、各運転モードの冷媒回路を切り替えることができる。従って、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂは、冷媒回路切替部としての機能も兼ね備えている。暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂは、制御装置６０から出力される制御信号（制御パルス）によって、その作動が制御される。 The heating expansion valve 14a and the cooling expansion valve 14b can switch the refrigerant circuit in each operation mode by the fully open function and the fully closed function. Therefore, the heating expansion valve 14a and the cooling expansion valve 14b also have a function as a refrigerant circuit switching unit. The operation of the heating expansion valve 14a and the cooling expansion valve 14b is controlled by a control signal (control pulse) output from the control device 60.
　暖房用膨張弁１４ａの出口には、室外熱交換器１６の冷媒流入ポート１６２ｄ側が接続されている。室外熱交換器１６は、暖房用膨張弁１４ａから流出した冷媒と図示しない冷却ファンにより送風された外気とを熱交換させる熱交換器である。室外熱交換器１６は、車両ボンネット内の前方側に配置されている。このため、車両走行時には、室外熱交換器１６に走行風を当てることができる。 出口 The refrigerant inflow port 162d side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is arranged on the front side inside the vehicle hood. For this reason, when the vehicle is traveling, traveling wind can be applied to the outdoor heat exchanger 16.
　ここで、図２を用いて、室外熱交換器１６の詳細構成について説明する。なお、図２における上下の各矢印は、室外熱交換器１６を車両に搭載した状態における上下の各方向を示している。このことは、他の図面においても同様である。本実施形態の室外熱交換器１６は、いわゆるタンクアンドチューブ型の熱交換器構造のものである。 Here, the detailed configuration of the outdoor heat exchanger 16 will be described with reference to FIG. Note that the upper and lower arrows in FIG. 2 indicate the upper and lower directions when the outdoor heat exchanger 16 is mounted on the vehicle. This is the same in other drawings. The outdoor heat exchanger 16 of the present embodiment has a so-called tank-and-tube type heat exchanger structure.
　室外熱交換器１６は、複数のチューブ１６１、一対のタンク１６２、１６３、コルゲートフィン１６４、モジュレータ部１６５等を有している。これらの各構成部材は、いずれも伝熱性に優れる同種の金属（本実施形態では、アルミニウム合金）で形成されている。室外熱交換器１６の各構成部材は、ろう付け接合により一体化されている。 The outdoor heat exchanger 16 includes a plurality of tubes 161, a pair of tanks 162 and 163, a corrugated fin 164, a modulator 165, and the like. Each of these constituent members is formed of the same kind of metal (in this embodiment, an aluminum alloy) having excellent heat conductivity. The components of the outdoor heat exchanger 16 are integrated by brazing.
　複数のチューブ１６１は、内部に冷媒が流通する管状部材である。チューブ１６１は、断面形状が扁平形状に形成された扁平チューブである。チューブ１６１は、水平方向に延びる形状に形成されている。それぞれのチューブ１６１は、外表面の平坦面（いわゆる、扁平面）同士が互いに平行となるように、一定の間隔を開けて上下方向に積層配置されている。本実施形態の室外熱交換器１６では、具体的に、４０本のチューブ１６１が積層配置されている。 The plurality of tubes 161 are tubular members through which a refrigerant flows. The tube 161 is a flat tube having a flat cross section. The tube 161 is formed in a shape extending in the horizontal direction. Each of the tubes 161 is vertically stacked at regular intervals so that the flat surfaces (so-called flat surfaces) of the outer surfaces are parallel to each other. In the outdoor heat exchanger 16 of the present embodiment, specifically, forty tubes 161 are stacked and arranged.
　これにより、隣り合うチューブ１６１同士の間には、外気が流通する空気通路が形成される。そして、チューブ１６１を流通する冷媒と空気通路を流通する外気の熱交換が可能となっている。つまり、室外熱交換器１６では、複数のチューブ１６１が積層配置されることによって、冷媒と外気とを熱交換させる熱交換部が形成されている。 Thereby, an air passage through which outside air flows is formed between the adjacent tubes 161. Then, heat exchange between the refrigerant flowing through the tube 161 and the outside air flowing through the air passage is possible. That is, in the outdoor heat exchanger 16, a heat exchange unit that exchanges heat between the refrigerant and the outside air is formed by stacking the plurality of tubes 161.
　コルゲートフィン１６４は、隣り合うチューブ１６１同士の間に形成された空気通路に配置されて、冷媒と外気との熱交換を促進する熱交換フィンである。なお、図２では、図示の明確化のため、チューブ１６１およびコルゲートフィン１６４の一部のみを図示しているが、チューブ１６１およびコルゲートフィン１６４は、熱交換部の全域に亘って配置されている。 The corrugated fin 164 is a heat exchange fin that is disposed in an air passage formed between the adjacent tubes 161 and that promotes heat exchange between the refrigerant and the outside air. In addition, in FIG. 2, for clarification of illustration, only a part of the tube 161 and the corrugated fin 164 are shown, but the tube 161 and the corrugated fin 164 are arranged over the entire area of the heat exchange unit. .
　一対のタンク１６２、１６３は、それぞれチューブ１６１の両端部に接続されている。一対のタンク１６２、１６３の内部には、複数のチューブ１６１に対して冷媒を分配するための分配空間、あるいは、複数のチューブ１６１から流出した冷媒を集合させるための集合空間が形成されている。 The pair of tanks 162 and 163 are respectively connected to both ends of the tube 161. Inside the pair of tanks 162 and 163, a distribution space for distributing the refrigerant to the plurality of tubes 161 or a collecting space for collecting the refrigerant flowing out of the plurality of tubes 161 is formed.
　タンク１６２、１６３の内部には、それぞれ内部空間を区画するセパレータ１６２ａ、１６３ａが配置されている。これにより、複数のチューブ１６１は、複数（本実施形態では、２つ）のパスに分けられている。ここで、タンクアンドチューブ型の熱交換器におけるパスとは、一方のタンク内に形成された同一の分配空間内の冷媒を他方のタンク内に形成された同一の集合空間へ向けて同一の方向へ流すチューブ群によって形成される冷媒流路と定義することができる。 セ パ レ ー タ Separators 162a and 163a that partition the internal space are disposed inside the tanks 162 and 163, respectively. Thereby, the plurality of tubes 161 are divided into a plurality of (two in the present embodiment) paths. Here, the path in the tank-and-tube type heat exchanger means that the refrigerant in the same distribution space formed in one tank is directed in the same direction toward the same collective space formed in the other tank. It can be defined as a refrigerant flow path formed by a group of tubes flowing to the flow path.
　本実施形態では、一方のタンク１６２の上下方向中央部にセパレータ１６２ａが配置されている。このため、一方のタンク１６２の内部空間は上下方向に略同等の容積の２つの空間に仕切られている。また、他方のタンク１６３の上下方向中央部にセパレータ１６３ａが配置されている。このため、他方のタンク１６３の内部空間は上下方向に略同等の容積の２つの空間に仕切られている。 In the present embodiment, the separator 162a is disposed at the center in the vertical direction of one of the tanks 162. For this reason, the internal space of one tank 162 is partitioned into two spaces having substantially the same volume in the vertical direction. Further, a separator 163a is arranged at the center in the vertical direction of the other tank 163. For this reason, the internal space of the other tank 163 is partitioned into two spaces having substantially the same volume in the vertical direction.
　一方のタンク１６２の下方側の空間を形成する部位には、暖房用膨張弁１４ａ側から流出した冷媒を流入させる冷媒流入ポート１６２ｄが接続されている。従って、一方のタンク１６２内の下方側の空間は、一方のタンク１６２のうち下方側の空間を形成する部位に接続された複数（具体的には、２０本）のチューブ１６１に対して冷媒を分配する第１分配空間１６２ｂとなる。 冷媒 A refrigerant inflow port 162d through which the refrigerant flowing out of the heating expansion valve 14a flows is connected to a portion forming a space below the one tank 162. Therefore, the lower space in one tank 162 supplies the refrigerant to a plurality of (specifically, 20) tubes 161 connected to a portion of the one tank 162 that forms the lower space. It becomes the first distribution space 162b for distribution.
　さらに、他方のタンク１６３の下方側の空間は、他方のタンク１６３のうち下方側の空間を形成する部位に接続された複数（具体的には、２０本）のチューブ１６１から流出した冷媒を集合させる第１集合空間１６３ｂとなる。そして、第１分配空間１６２ｂから第１集合空間１６３ｂへ向けて冷媒を流すチューブ群によって、第１パスが形成される。 Further, the space below the other tank 163 collects the refrigerant flowing out from a plurality of (specifically, 20) tubes 161 connected to a portion forming the space below the other tank 163. It becomes the first set space 163b to be made. Then, a first path is formed by a group of tubes through which the refrigerant flows from the first distribution space 162b to the first collection space 163b.
　また、一方のタンク１６２の上方側の空間を形成する部位には、第３三方継手１３ｃの流入口側へ冷媒を流出させる冷媒流出ポート１６２ｅが接続されている。従って、一方のタンク１６２の上方側の空間は、一方のタンク１６２のうち上方側の空間を形成する部位に接続された複数（具体的には、２０本）のチューブ１６１から流出した冷媒を集合させる第２集合空間１６２ｃとなる。 冷媒 A refrigerant outlet port 162e that allows the refrigerant to flow toward the inlet side of the third three-way joint 13c is connected to a portion forming a space above the one tank 162. Therefore, the space above one tank 162 collects the refrigerant flowing out from a plurality of (specifically, 20) tubes 161 connected to a portion of the one tank 162 that forms the space above. The second set space 162c is obtained.
　さらに、他方のタンク１６３の上方側の空間は、他方のタンク１６３のうち上方側の空間を形成する部位に接続された複数（具体的には、２０本）のチューブ１６１に対して冷媒を分配する第２分配空間１６３ｃとなる。そして、第２分配空間１６３ｃから第２集合空間１６２ｃへ向けて冷媒を流すチューブ群によって、第２パスが形成される。 Further, the space above the other tank 163 distributes the refrigerant to a plurality of (specifically, 20) tubes 161 connected to a portion forming the space above the other tank 163. The second distribution space 163c. And a 2nd path | pass is formed by the tube group which flows a refrigerant | coolant from the 2nd distribution space 163c to the 2nd collective space 162c.
　また、他方のタンク１６３のうち第１集合空間１６３ｂが形成される部位には、第１集合空間１６３ｂから冷媒を流出させる冷媒出口１６３ｄが形成されている。冷媒出口１６３ｄは、他方のタンク１６３のうち第１集合空間１６３ｂが形成される部位の最上方側に配置されている。この冷媒出口１６３ｄには、モジュレータ部１６５の冷媒入口１６５ａ側が接続されている。 冷媒 A coolant outlet 163d for allowing the coolant to flow out of the first collecting space 163b is formed in a portion of the other tank 163 where the first collecting space 163b is formed. The refrigerant outlet 163d is arranged on the uppermost side of a portion of the other tank 163 where the first collecting space 163b is formed. The refrigerant outlet 163d is connected to the refrigerant inlet 165a side of the modulator section 165.
　モジュレータ部１６５は、第２冷房モード時に、第１パスを流通する際に外気と熱交換した高圧冷媒の気液を分離して、分離された高圧液相冷媒をサイクル内の余剰冷媒として貯える高圧側貯液部である。モジュレータ部１６５は、中心軸が複数のチューブ１６１の積層方向（すなわち、上下方向）に延びる有底筒状に形成されている。モジュレータ部１６５の冷媒入口１６５ａは、モジュレータ部１６５の最下方側に配置されている。 In the second cooling mode, the modulator 165 separates the gas-liquid of the high-pressure refrigerant that has exchanged heat with the outside air when flowing through the first path, and stores the separated high-pressure liquid-phase refrigerant as surplus refrigerant in the cycle. It is a side liquid storage part. The modulator section 165 is formed in a bottomed cylindrical shape whose central axis extends in the stacking direction of the plurality of tubes 161 (that is, in the up-down direction). The refrigerant inlet 165a of the modulator section 165 is disposed on the lowermost side of the modulator section 165.
　モジュレータ部１６５の冷媒出口１６５ｂには、他方のタンク１６３に形成された冷媒入口１６３ｅ側が接続されている。冷媒入口１６３ｅは、他方のタンク１６３のうち第２分配空間１６３ｃを形成する部位に形成されている。さらに、冷媒入口１６３ｅは、モジュレータ部１６５から第２分配空間１６３ｃへ流入した冷媒が、下方側から上方側へ向かう速度成分を有するように下方側に位置付けられている。 The refrigerant outlet 165b of the modulator 165 is connected to the refrigerant inlet 163e formed in the other tank 163. The refrigerant inlet 163e is formed in a portion of the other tank 163 that forms the second distribution space 163c. Further, the refrigerant inlet 163e is positioned on the lower side so that the refrigerant flowing from the modulator section 165 into the second distribution space 163c has a velocity component from the lower side to the upper side.
　以上の説明から明かなように、本実施形態の室外熱交換器１６では、第１パスを構成する複数のチューブ１６１によって、暖房用膨張弁１４ａから流出した冷媒と外気とを熱交換させる第１熱交換部１６ａが構成されている。さらに、第２パスを構成する複数のチューブ１６１によって、モジュレータ部１６５から流出した冷媒と外気とを熱交換させる第２熱交換部１６ｂが構成されている。 As is clear from the above description, in the outdoor heat exchanger 16 of the present embodiment, the first tube in which the refrigerant flowing out of the heating expansion valve 14a exchanges heat with the outside air by the plurality of tubes 161 constituting the first path. The heat exchange section 16a is configured. Further, the plurality of tubes 161 constituting the second path constitute a second heat exchange section 16b for exchanging heat between the refrigerant flowing out of the modulator section 165 and the outside air.
　第１熱交換部１６ａは、第２熱交換部１６ｂよりも上下方向下方側に配置されている。また、第１パスを構成するチューブ１６１の本数と第２パスを構成するチューブ１６１の本数が同じになっている。従って、第１熱交換部１６ａにて冷媒と外気とを熱交換させる熱交換面積と第２熱交換部１６ｂにて冷媒と外気とを熱交換させる熱交換面積が同等となっている。 The first heat exchange unit 16a is disposed below the second heat exchange unit 16b in the vertical direction. Further, the number of tubes 161 constituting the first pass is the same as the number of tubes 161 constituting the second pass. Therefore, the heat exchange area for exchanging heat between the refrigerant and the outside air in the first heat exchange section 16a is equal to the heat exchange area for exchanging heat between the refrigerant and the outside air in the second heat exchange section 16b.
　このように、第２熱交換部１６ｂの熱交換面積が設定されているのは、第２冷房モード時に、第２熱交換部１６ｂを高圧液相冷媒で満たすためである。換言すると、第２熱交換部１６ｂの熱交換面積は、第２冷却モード時に、第２熱交換部１６ｂが高圧液相冷媒で満たされるように設定されている。
また、他方のタンク１６３の冷媒出口１６３ｄは、第１集合空間１６３ｂが形成される部位の最上方側に配置されている。つまり、冷媒出口１６３ｄは、第１熱交換部１６ａの最上方側に配置されている。 The reason why the heat exchange area of the second heat exchange unit 16b is set in this way is to fill the second heat exchange unit 16b with the high-pressure liquid-phase refrigerant in the second cooling mode. In other words, the heat exchange area of the second heat exchange unit 16b is set so that the second heat exchange unit 16b is filled with the high-pressure liquid-phase refrigerant in the second cooling mode.
In addition, the refrigerant outlet 163d of the other tank 163 is disposed on the uppermost side of a portion where the first collecting space 163b is formed. That is, the refrigerant outlet 163d is arranged on the uppermost side of the first heat exchange unit 16a.
　ここで、冷媒出口１６３ｄが、第１熱交換部１６ａの最上方側に配置されているとは、冷媒出口１６３ｄが、第１熱交換部１６ａを構成する部材の上下方向最上部のみで開口しているという意味に限定されない。冷媒出口１６３ｄが、第１熱交換部１６ａを構成する部材の上下方向最上部あるいは上下方向最上部よりも僅かに低い位置を含むように開口して、実質的に最上部で開口していることを含む意味である。 Here, that the refrigerant outlet 163d is arranged on the uppermost side of the first heat exchange part 16a means that the refrigerant outlet 163d is opened only at the uppermost part in the vertical direction of the member constituting the first heat exchange part 16a. It is not limited to the meaning that it is. The refrigerant outlet 163d is opened so as to include the uppermost part in the vertical direction or a position slightly lower than the uppermost part in the vertical direction of the member constituting the first heat exchange unit 16a, and is substantially opened at the uppermost part. It is a meaning including.
　同様に、モジュレータ部１６５の冷媒入口１６５ａが、モジュレータ部１６５の最下方側に配置されているとは、冷媒入口１６５ａが、モジュレータ部１６５の上下方向最下部のみで開口しているという意味に限定されない。冷媒入口１６５ａが、モジュレータ部１６５の上下方向最下部あるいは上下方向最下部よりも僅かに位置を含むように開口して、実質的に最下部で開口していることを含む意味である。 Similarly, that the refrigerant inlet 165a of the modulator part 165 is arranged at the lowermost side of the modulator part 165 is limited to the meaning that the refrigerant inlet 165a is opened only at the lowermost part of the modulator part 165 in the vertical direction. Not done. This means that the refrigerant inlet 165a is opened so as to include the lowermost portion of the modulator portion 165 in the vertical direction or a position slightly lower than the lowermost portion in the vertical direction, and substantially opens at the lowermost portion.
　室外熱交換器１６の冷媒流出ポート１６２ｅには、図１に示すように、第３三方継手１３ｃの流入口側が接続されている。第３三方継手１３ｃの一方の流出口には、暖房用通路２２ｂを介して、第４三方継手１３ｄの一方の流入口側が接続されている。暖房用通路２２ｂには、この冷媒通路を開閉する暖房用開閉弁１５ｂが配置されている。 (1) As shown in FIG. 1, the inflow port side of the third three-way joint 13c is connected to the refrigerant outflow port 162e of the outdoor heat exchanger 16. One of the outlets of the third three-way joint 13c is connected to one of the inlets of the fourth three-way joint 13d via a heating passage 22b. A heating opening / closing valve 15b that opens and closes the refrigerant passage is arranged in the heating passage 22b.
　第３三方継手１３ｃの他方の流出口には、第２三方継手１３ｂの他方の流入口側が接続されている。第３三方継手１３ｃの他方の流出口側と第２三方継手１３ｂの他方の流入口側とを接続する冷媒通路には、逆止弁１７が配置されている。逆止弁１７は、第３三方継手１３ｃ側から第２三方継手１３ｂ側へ冷媒が流れることを許容し、第２三方継手１３ｂ側から第３三方継手１３ｃ側へ冷媒が流れることを禁止する。 他方 The other inflow side of the second three-way joint 13b is connected to the other outflow port of the third three-way joint 13c. A check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c to the second three-way joint 13b, and prohibits the refrigerant from flowing from the second three-way joint 13b to the third three-way joint 13c.
　第２三方継手１３ｂの流出口には、冷房用膨張弁１４ｂの入口側が接続されている。冷房用膨張弁１４ｂは、少なくとも冷房モード時に、室外熱交換器１６から流出した冷媒を減圧させるとともに、下流側へ流出させる冷媒の流量を調整する減圧部である。 流 The inlet of the cooling expansion valve 14b is connected to the outlet of the second three-way joint 13b. The cooling expansion valve 14b is a pressure reducing unit that reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing downstream at least in the cooling mode.
　冷房用膨張弁１４ｂの出口には、室内蒸発器１８の冷媒入口側が接続されている。室内蒸発器１８は、後述する室内空調ユニット３０の空調ケース３１内に配置されている。室内蒸発器１８は、冷房用膨張弁１４ｂにて減圧された低圧冷媒と送風機３２から送風された送風空気とを熱交換させて低圧冷媒を蒸発させ、低圧冷媒に吸熱作用を発揮させることによって送風空気を冷却する冷却用熱交換器である。 冷媒 The refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14b. The indoor evaporator 18 is arranged in an air-conditioning case 31 of an indoor air-conditioning unit 30 described later. The indoor evaporator 18 blows air by exchanging heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14b and the blast air blown from the blower 32 to evaporate the low-pressure refrigerant and exert an endothermic effect on the low-pressure refrigerant. This is a cooling heat exchanger that cools air.
　室内蒸発器１８の冷媒出口には、蒸発圧力調整弁２０の入口側が接続されている。蒸発圧力調整弁２０は、室内蒸発器１８の着霜を抑制するために、室内蒸発器１８における冷媒蒸発圧力を、予め定めた基準圧力以上に維持する。蒸発圧力調整弁２０は、室内蒸発器１８の出口側冷媒の圧力の上昇に伴って、弁開度を増加させる機械式の可変絞り機構で構成されている。 冷媒 The refrigerant outlet of the indoor evaporator 18 is connected to the inlet side of the evaporation pressure regulating valve 20. The evaporation pressure regulating valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 18. The evaporating pressure adjusting valve 20 is configured by a mechanical variable throttle mechanism that increases the valve opening as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases.
　これにより、蒸発圧力調整弁２０は、室内蒸発器１８における冷媒蒸発温度を、室内蒸発器１８の着霜を抑制可能な着霜抑制温度（本実施形態では、１℃）以上に維持している。蒸発圧力調整弁２０の出口には、第４三方継手１３ｄの他方の流入口側が接続されている。第４三方継手１３ｄの流出口には、アキュムレータ２１の冷媒入口２１２ａ側が接続されている。 As a result, the evaporation pressure regulating valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a frost formation suppression temperature (1 ° C. in the present embodiment) capable of suppressing frost formation on the indoor evaporator 18. . The other inlet side of the fourth three-way joint 13d is connected to the outlet of the evaporation pressure regulating valve 20. The refrigerant outlet 212a side of the accumulator 21 is connected to the outlet of the fourth three-way joint 13d.
　アキュムレータ２１は、冷房モード時等に、室内蒸発器１８から流出した冷媒の気液を分離して、分離された低圧液相冷媒をサイクル内の余剰冷媒として貯える低圧側貯液部である。アキュムレータ２１の気相冷媒出口２１３ｂには、圧縮機１１の吸入口側が接続されている。 The accumulator 21 is a low-pressure storage unit that separates gas-liquid refrigerant flowing out of the indoor evaporator 18 in a cooling mode or the like and stores the separated low-pressure liquid-phase refrigerant as surplus refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet 213b of the accumulator 21.
　ここで、図３を用いて、アキュムレータ２１の詳細構成について説明する。アキュムレータ２１は、冷媒容器２１１、入口側パイプ２１２、出口側パイプ２１３等を有している。 Here, the detailed configuration of the accumulator 21 will be described with reference to FIG. The accumulator 21 has a refrigerant container 211, an inlet pipe 212, an outlet pipe 213, and the like.
　冷媒容器２１１は、有底円筒状に形成された金属製（本実施形態では、アルミニウム製）のものである。冷媒容器２１１は、その中心軸が上下方向に延びるように配置されている。冷媒容器２１１の内部には、冷媒の気液を分離して、分離された液相冷媒を貯える貯留空間が形成されている。 The refrigerant container 211 is made of metal (in this embodiment, aluminum) formed in a bottomed cylindrical shape. The refrigerant container 211 is arranged so that its central axis extends in the vertical direction. Inside the refrigerant container 211, a storage space for separating gas-liquid of the refrigerant and storing the separated liquid-phase refrigerant is formed.
　入口側パイプ２１２は、冷媒容器２１１と同じ金属で形成された配管部材である。入口側パイプ２１２は、上下方向に延びる形状に形成されている。入口側パイプ２１２の一方の端部は、冷媒容器２１１の外部の上方側に配置されて、第４三方継手１３ｄから流出した冷媒を流入させる冷媒入口２１２ａを形成している。入口側パイプ２１２の他方の端部は、冷媒容器２１１の内部に配置されて、冷媒出口２１２ｂを形成している。 The inlet pipe 212 is a piping member formed of the same metal as the refrigerant container 211. The inlet-side pipe 212 is formed in a shape extending in the up-down direction. One end of the inlet-side pipe 212 is disposed above the refrigerant container 211 and forms a refrigerant inlet 212a through which the refrigerant flowing out of the fourth three-way joint 13d flows. The other end of the inlet-side pipe 212 is disposed inside the refrigerant container 211 and forms a refrigerant outlet 212b.
　出口側パイプ２１３は、冷媒容器２１１と同じ金属で形成された配管部材である。出口側パイプ２１３は、Ｕ字状に湾曲した湾曲部を有する形状に形成されている。出口側パイプ２１３の一方の端部は、冷媒容器２１１の外部の上方側に配置されて、圧縮機１１の吸入口側へ気相冷媒を流出させる気相冷媒出口２１３ｂを形成している。出口側パイプ２１３の他方の端部は、冷媒容器２１１の内部に配置されて、冷媒容器２１１の内部で分離された気相冷媒を流入させる気相冷媒入口２１３ａを形成している。 The outlet-side pipe 213 is a piping member formed of the same metal as the refrigerant container 211. The outlet side pipe 213 is formed in a shape having a U-shaped curved portion. One end of the outlet pipe 213 is arranged above the outside of the refrigerant container 211 to form a gas-phase refrigerant outlet 213b that allows the gas-phase refrigerant to flow toward the suction port of the compressor 11. The other end of the outlet-side pipe 213 is disposed inside the refrigerant container 211 and forms a gas-phase refrigerant inlet 213a through which the gas-phase refrigerant separated inside the refrigerant container 211 flows.
　より詳細には、気相冷媒入口２１３ａは、アキュムレータ２１内に液相冷媒が貯えられた際に、液面よりも上方側であって、さらに、入口側パイプ２１２の冷媒出口２１２ｂよりも上方側に配置されている。従って、気相冷媒入口２１３ａから出口側パイプ２１３へ液相冷媒が流入してしまうことはない。 More specifically, when the liquid-phase refrigerant is stored in the accumulator 21, the gas-phase refrigerant inlet 213 a is above the liquid surface and further above the refrigerant outlet 212 b of the inlet pipe 212. Are located in Therefore, the liquid-phase refrigerant does not flow into the outlet-side pipe 213 from the gas-phase refrigerant inlet 213a.
　さらに、出口側パイプ２１３の湾曲部は、アキュムレータ２１内に液相冷媒が貯えられた際に、液面よりも下方側に配置されている。湾曲部の最下部には、オイル戻し穴２１３ｃが形成されている。オイル戻し穴２１３ｃは、アキュムレータ２１内に液相冷媒が貯えられた際に、冷凍機油が溶け込んだ液相冷媒を吸い込んで、圧縮機１１へ吸入させるために形成された穴である。 {Circle around (2)} When the liquid-phase refrigerant is stored in the accumulator 21, the curved portion of the outlet-side pipe 213 is disposed below the liquid surface. An oil return hole 213c is formed at the lowermost portion of the curved portion. The oil return hole 213c is a hole formed for sucking the liquid-phase refrigerant in which the refrigerating machine oil is dissolved and sucking the liquid-phase refrigerant into the compressor 11 when the liquid-phase refrigerant is stored in the accumulator 21.
　次に、高温側熱媒体回路４０について説明する。高温側熱媒体回路４０は、高温側熱媒体を循環させる熱媒体循環回路である。高温側熱媒体としては、エチレングリコール、ジメチルポリシロキサン、あるいはナノ流体等を含む溶液、不凍液等を採用することができる。高温側熱媒体回路４０には、水－冷媒熱交換器１２の水通路、高温側熱媒体ポンプ４１、ヒータコア４２等が配置されている。 Next, the high-temperature side heat medium circuit 40 will be described. The high-temperature-side heat medium circuit 40 is a heat medium circulation circuit that circulates the high-temperature-side heat medium. As the high-temperature side heat medium, ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid, or the like, an antifreeze, or the like can be used. The high-temperature heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat medium pump 41, a heater core 42, and the like.
　高温側熱媒体ポンプ４１は、高温側熱媒体を水－冷媒熱交換器１２の水通路の入口側へ圧送する水ポンプである。高温側熱媒体ポンプ４１は、制御装置６０から出力される制御電圧によって、回転数（すなわち、圧送能力）が制御される電動ポンプである。 The high-temperature heat medium pump 41 is a water pump for pumping the high-temperature heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12. The high-temperature-side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.
　水－冷媒熱交換器１２の水通路の出口には、ヒータコア４２の熱媒体入口側が接続されている。ヒータコア４２は、水－冷媒熱交換器１２にて加熱された高温側熱媒体と室内蒸発器１８を通過した送風空気とを熱交換させて、送風空気を加熱する熱交換器である。ヒータコア４２は、室内空調ユニット３０の空調ケース３１内に配置されている。ヒータコア４２の熱媒体出口には、高温側熱媒体ポンプ４１の吸入口側が接続されている。 熱 The outlet of the water passage of the water-refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42. The heater core 42 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 18. The heater core 42 is arranged inside the air conditioning case 31 of the indoor air conditioning unit 30. The heat medium outlet of the heater core 42 is connected to the suction side of the high-temperature side heat medium pump 41.
　つまり、本実施形態では、水－冷媒熱交換器１２および高温側熱媒体回路４０の各構成機器によって、圧縮機１１から吐出された冷媒を熱源として、送風空気を加熱する加熱部が構成されている。 In other words, in the present embodiment, each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. I have.
　次に、室内空調ユニット３０について説明する。室内空調ユニット３０は、車室内の空調のために適切な温度に調整された送風空気を車室内の適切な箇所へ吹き出すためのものである。室内空調ユニット３０は、車室内最前部の計器盤（インストルメントパネル）の内側に配置されている。 Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is for blowing blast air adjusted to an appropriate temperature for air-conditioning the vehicle interior to an appropriate location in the vehicle interior. The indoor air-conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the forefront of the vehicle interior.
　室内空調ユニット３０は、図１に示すように、送風空気の空気通路を形成する空調ケース３１内に、送風機３２、室内蒸発器１８、ヒータコア４２等を収容したものである。空調ケース３１は、ある程度の弾性を有し、強度的にも優れた樹脂（例えば、ポリプロピレン）にて成形されている。 (1) As shown in FIG. 1, the indoor air-conditioning unit 30 has a blower 32, an indoor evaporator 18, a heater core 42, and the like housed in an air-conditioning case 31 that forms an air passage for blowing air. The air-conditioning case 31 has a certain degree of elasticity and is formed of a resin (for example, polypropylene) having excellent strength.
　空調ケース３１の送風空気流れ最上流側には、内外気切替装置３３が配置されている。内外気切替装置３３は、空調ケース３１内へ内気（車室内空気）と外気（車室外空気）とを切替導入する。内外気切替装置３３の駆動用の電動アクチュエータは、制御装置６０から出力される制御信号によって、その作動が制御される。 内 An inside / outside air switching device 33 is disposed on the most upstream side of the airflow of the air conditioning case 31. The inside / outside air switching device 33 switches and introduces inside air (vehicle interior air) and outside air (vehicle outside air) into the air conditioning case 31. The operation of the electric actuator for driving the inside / outside air switching device 33 is controlled by a control signal output from the control device 60.
　内外気切替装置３３の送風空気流れ下流側には、送風機３２が配置されている。送風機３２は、内外気切替装置３３を介して吸入した空気を車室内へ向けて送風する。送風機３２は、遠心多翼ファンを電動モータにて駆動する電動送風機である。送風機３２は、制御装置６０から出力される制御電圧によって、回転数（すなわち、送風能力）が制御される。 A blower 32 is disposed downstream of the inside / outside air switching device 33 in the blown air flow. The blower 32 blows the air taken in through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (that is, the blowing capacity) of the blower 32 is controlled by the control voltage output from the control device 60.
　送風機３２の送風空気流れ下流側には、室内蒸発器１８、ヒータコア４２が、送風空気流れに対して、この順に配置されている。つまり、室内蒸発器１８は、ヒータコア４２よりも、送風空気流れ上流側に配置されている。 室内 On the downstream side of the blown air flow of the blower 32, the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 18 is arranged on the upstream side of the flow of the blown air from the heater core 42.
　空調ケース３１内には、室内蒸発器１８通過後の送風空気を、ヒータコア４２を迂回させて流す冷風バイパス通路３５が設けられている。さらに、空調ケース３１内の室内蒸発器１８の送風空気流れ下流側であって、かつ、ヒータコア４２の送風空気流れ上流側には、エアミックスドア３４が配置されている。 冷 A cool air bypass passage 35 is provided in the air-conditioning case 31 to allow the air blown through the indoor evaporator 18 to flow around the heater core 42. Further, an air mix door 34 is arranged on the downstream side of the air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the air flow of the heater core 42.
　エアミックスドア３４は、室内蒸発器１８通過後の送風空気のうち、ヒータコア４２側を通過する送風空気の風量と冷風バイパス通路３５を通過させる送風空気の風量との風量割合を調整する風量割合調整部である。エアミックスドア３４の駆動用の電動アクチュエータは、制御装置６０から出力される制御信号によって、その作動が制御される。 The air mix door 34 adjusts a flow rate ratio of a flow rate of the blown air passing through the heater core 42 and a flow rate of the blown air passing through the cool air bypass passage 35 among the blown air after passing through the indoor evaporator 18. Department. The operation of the electric actuator for driving the air mix door 34 is controlled by a control signal output from the control device 60.
　空調ケース３１内のヒータコア４２および冷風バイパス通路３５の送風空気流れ下流側には、混合空間が配置されている。混合空間は、ヒータコア４２にて加熱された送風空気と冷風バイパス通路３５を通過して加熱されていない送風空気とを混合させる空間である。さらに、空調ケース３１の送風空気流れ下流部には、混合空間にて混合されて温度調整された送風空気を、車室内へ吹き出すための開口穴が配置されている。 {Circle around (4)} The mixing space is disposed downstream of the air flow of the heater core 42 and the cool air bypass passage 35 in the air conditioning case 31. The mixing space is a space for mixing the blast air heated by the heater core 42 and the blast air that has not passed through the cool air bypass passage 35 and is not heated. Further, an opening hole for blowing out the blown air mixed and temperature-adjusted in the mixing space into the vehicle compartment is disposed downstream of the airflow of the air-conditioning case 31.
　開口穴としては、フェイス開口穴、フット開口穴、およびデフロスタ開口穴（いずれも図示せず）が設けられている。フェイス開口穴は、車室内の乗員の上半身に向けて空調風を吹き出すための開口穴である。フット開口穴は、乗員の足元に向けて空調風を吹き出すための開口穴である。デフロスタ開口穴は、車両前面窓ガラス内側面に向けて空調風を吹き出すための開口穴である。 As the opening holes, a face opening hole, a foot opening hole, and a defroster opening hole (all not shown) are provided. The face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment. The foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.
　従って、エアミックスドア３４が、ヒータコア４２を通過させる風量と冷風バイパス通路３５を通過させる風量との風量割合を調整することによって、混合空間にて混合される空調風の温度が調整される。そして、各吹出口から車室内へ吹き出される送風空気（空調風）の温度が調整される。 Therefore, the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air flow ratio of the air flow passing through the heater core 42 and the air flow passing through the cool air bypass passage 35 by the air mixing door 34. Then, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle interior is adjusted.
　また、フェイス開口穴、フット開口穴、およびデフロスタ開口穴の送風空気流れ上流側には、フェイスドア、フットドア、およびデフロスタドア（いずれも図示せず）が配置されている。フェイスドア、フットドア、およびデフロスタドアは、運転モードに応じて対応する開口穴を開閉する開閉部である。 フ ェ イ ス Face doors, foot doors, and defroster doors (all not shown) are arranged on the upstream side of the airflow from the face opening, the foot opening, and the defroster opening. The face door, the foot door, and the defroster door are opening / closing units that open and close corresponding opening holes according to the operation mode.
　これらのドアは、リンク機構等を介して、共通する駆動用の電動アクチュエータに連結されて連動して回転操作される。これらのドアの駆動用の電動アクチュエータは、制御装置６０から出力される制御信号によって、その作動が制御される。 ド ア These doors are connected to a common driving electric actuator via a link mechanism or the like, and are rotated in conjunction therewith. The operation of these electric actuators for driving the doors is controlled by a control signal output from the control device 60.
　次に、本実施形態の電気制御部の概要について説明する。制御装置６０は、ＣＰＵ、ＲＯＭおよびＲＡＭ等を含む周知のマイクロコンピュータとその周辺回路から構成されている。そして、そのＲＯＭ内に記憶された空調制御プログラムに基づいて各種演算、処理を行い、その出力側に接続された各種制御対象機器１１、１４ａ、１４ｂ、１５ａ、１５ｂ、３２、４１等の作動を制御する。 Next, an outline of the electric control unit of the present embodiment will be described. The control device 60 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits. Then, various calculations and processes are performed based on the air conditioning control program stored in the ROM, and the operations of the various control target devices 11, 14a, 14b, 15a, 15b, 32, 41, etc. connected to the output side are performed. Control.
　また、制御装置６０の入力側には、図４のブロック図に示すように、内気温センサ６１、外気温センサ６２、日射センサ６３、第１冷媒温度センサ６４ａ～第４冷媒温度センサ６４ｄ、蒸発器温度センサ６４ｆ、第１冷媒圧力センサ６５ａ、第２冷媒圧力センサ６５ｂ、高温側熱媒体温度センサ６６ａ、空調風温度センサ６９等が接続されている。そして、制御装置６０には、これらのセンサ群の検出信号が入力される。 On the input side of the control device 60, as shown in the block diagram of FIG. 4, an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, first to fourth refrigerant temperature sensors 64a to 64d, and evaporation. A heater temperature sensor 64f, a first refrigerant pressure sensor 65a, a second refrigerant pressure sensor 65b, a high-temperature heat medium temperature sensor 66a, an air-conditioning air temperature sensor 69, and the like are connected. The control unit 60 receives detection signals from these sensor groups.
　内気温センサ６１は、車室内温度（内気温）Ｔｒを検出する内気温検出部である。外気温センサ６２は、車室外温度（外気温）Ｔａｍを検出する外気温検出部である。日射センサ６３は、車室内へ照射される日射量Ｔｓを検出する日射量検出部である。 The inside air temperature sensor 61 is an inside air temperature detection unit that detects the vehicle interior temperature (inside air temperature) Tr. The outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam. The solar radiation sensor 63 is a solar radiation amount detecting unit that detects a solar radiation amount Ts irradiated into the vehicle interior.
　第１冷媒温度センサ６４ａは、圧縮機１１から吐出された冷媒の温度Ｔ１を検出する吐出冷媒温度検出部である。第２冷媒温度センサ６４ｂは、水－冷媒熱交換器１２の冷媒通路から流出した冷媒の温度Ｔ２を検出する第２冷媒温度検出部である。第３冷媒温度センサ６４ｃは、室外熱交換器１６から流出した冷媒の温度Ｔ３を検出する第３冷媒温度検出部である。第４冷媒温度センサ６４ｄは、室内蒸発器１８から流出した冷媒の温度Ｔ４を検出する第４冷媒温度検出部である。 The first refrigerant temperature sensor 64a is a discharged refrigerant temperature detection unit that detects the temperature T1 of the refrigerant discharged from the compressor 11. The second refrigerant temperature sensor 64b is a second refrigerant temperature detector that detects the temperature T2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. The third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects the temperature T3 of the refrigerant flowing out of the outdoor heat exchanger 16. The fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detector that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18.
　蒸発器温度センサ６４ｆは、室内蒸発器１８における冷媒蒸発温度（蒸発器温度）Ｔｅｆｉｎを検出する蒸発器温度検出部である。本実施形態の蒸発器温度センサ６４ｆは、具体的に、室内蒸発器１８の熱交換フィンの温度を検出している。 The evaporator temperature sensor 64f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. The evaporator temperature sensor 64f of this embodiment specifically detects the temperature of the heat exchange fins of the indoor evaporator 18.
　第１冷媒圧力センサ６５ａは、水－冷媒熱交換器１２の冷媒通路から流出した冷媒の圧力Ｐ１を検出する第１冷媒圧力検出部である。第２冷媒圧力センサ６５ｂは、室内蒸発器１８から流出した冷媒の圧力Ｐ２を検出する第２冷媒圧力検出部である。 The first refrigerant pressure sensor 65a is a first refrigerant pressure detector that detects the pressure P1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. The second refrigerant pressure sensor 65b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the indoor evaporator 18.
　高温側熱媒体温度センサ６６ａは、水－冷媒熱交換器１２の水通路から流出した高温側熱媒体の温度である高温側熱媒体温度ＴＷＨを検出する高温側熱媒体温度検出部である。空調風温度センサ６９は、混合空間から車室内へ送風される送風空気温度ＴＡＶを検出する空調風温度検出部である。 The high-temperature heat medium temperature sensor 66a is a high-temperature heat medium temperature detection unit that detects the high-temperature heat medium temperature TWH, which is the temperature of the high-temperature heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12. The air-conditioning air temperature sensor 69 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.
　さらに、制御装置６０の入力側には、図４に示すように、車室内前部の計器盤付近に配置された操作パネル７０が接続され、この操作パネル７０に設けられた各種操作スイッチからの操作信号が入力される。 Further, as shown in FIG. 4, an operation panel 70 arranged near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches provided on the operation panel 70 An operation signal is input.
　操作パネル７０に設けられた各種操作スイッチとしては、具体的に、オートスイッチ、エアコンスイッチ、風量設定スイッチ、温度設定スイッチ、吹出モード切替スイッチ等がある。 各種 Specific examples of various operation switches provided on the operation panel 70 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, a blowout mode switching switch, and the like.
　オートスイッチは、車両用空調装置１の自動制御運転を設定あるいは解除する自動制御運転設定部である。エアコンスイッチは、室内蒸発器１８で送風空気の冷却を行うことを要求する冷却要求部である。風量設定スイッチは、送風機３２の風量をマニュアル設定する風量設定部である。温度設定スイッチは、車室内の目標温度Ｔｓｅｔを設定する目標温度設定部である。吹出モードは、吹出モードをマニュアル設定する吹出モード切替設定部である。 The automatic switch is an automatic control operation setting unit that sets or cancels the automatic control operation of the vehicle air conditioner 1. The air conditioner switch is a cooling request unit that requests the indoor evaporator 18 to cool the blown air. The air volume setting switch is an air volume setting unit for manually setting the air volume of the blower 32. The temperature setting switch is a target temperature setting unit that sets a target temperature Tset in the vehicle compartment. The blowout mode is a blowout mode switching setting unit for manually setting the blowout mode.
　なお、本実施形態の制御装置６０は、その出力側に接続された各種制御対象機器を制御する制御部が一体に構成されたものである。従って、それぞれの制御対象機器の作動を制御する構成（ハードウェアおよびソフトウェア）が、それぞれの制御対象機器の作動を制御する制御部を構成している。 The control device 60 of the present embodiment has an integrated control unit for controlling various control target devices connected to the output side. Therefore, the configuration (hardware and software) that controls the operation of each control target device constitutes a control unit that controls the operation of each control target device.
　例えば、制御装置６０のうち、圧縮機１１の冷媒吐出能力（具体的には、圧縮機１１の回転数）を制御する構成は、吐出能力制御部６０ａを構成している。また、減圧部である冷房用膨張弁１４ｂの作動（具体的には、冷房用膨張弁１４ｂの絞り開度）を制御する構成は、減圧制御部６０ｂを構成している。 For example, of the control device 60, the configuration that controls the refrigerant discharge capacity of the compressor 11 (specifically, the number of revolutions of the compressor 11) constitutes the discharge capacity control unit 60a. The configuration for controlling the operation of the cooling expansion valve 14b (specifically, the throttle opening of the cooling expansion valve 14b), which is a pressure reducing unit, forms the pressure reducing control unit 60b.
　次に、上記構成における本実施形態の作動について説明する。前述の如く、本実施形態の車両用空調装置１は、車室内の冷房、除湿暖房、および暖房を行うことができる。さらに、冷凍サイクル装置１０は、車室内の空調のために、冷房モード、直列除湿暖房モード、並列除湿暖房モード、および暖房モードの運転を切り替える。 Next, the operation of the present embodiment in the above configuration will be described. As described above, the vehicle air conditioner 1 of the present embodiment can perform cooling, dehumidifying heating, and heating of the vehicle interior. Further, the refrigeration cycle apparatus 10 switches the operation among a cooling mode, a series dehumidifying and heating mode, a parallel dehumidifying and heating mode, and a heating mode for air conditioning in the vehicle compartment.
　冷凍サイクル装置１０の各運転モードの切り替えは、空調制御プログラムが実行されることによって行われる。空調制御プログラムは、操作パネル７０のオートスイッチが投入（ＯＮ）されて、自動制御運転が設定された際に実行される。 The switching of each operation mode of the refrigeration cycle device 10 is performed by executing an air conditioning control program. The air conditioning control program is executed when the automatic switch of the operation panel 70 is turned on (ON) and the automatic control operation is set.
　空調制御プログラムのメインルーチンでは、上述の空調制御用のセンサ群の検出信号および各種空調操作スイッチからの操作信号を読み込む。そして、読み込んだ検出信号および操作信号の値に基づいて、車室内へ吹き出す吹出空気の目標温度である目標吹出温度ＴＡＯを、以下数式Ｆ１に基づいて算出する。 メ イ ン In the main routine of the air conditioning control program, the detection signals of the above-described air conditioning control sensor group and operation signals from various air conditioning operation switches are read. Then, based on the values of the read detection signal and operation signal, a target outlet temperature TAO, which is a target temperature of the outlet air to be blown into the vehicle interior, is calculated based on the following equation F1.
　具体的には、目標吹出温度ＴＡＯは、以下数式Ｆ１によって算出される。ＴＡＯ＝Ｋｓｅｔ×Ｔｓｅｔ－Ｋｒ×Ｔｒ－Ｋａｍ×Ｔａｍ－Ｋｓ×Ａｓ＋Ｃ…（Ｆ１）
　なお、Ｔｓｅｔは温度設定スイッチによって設定された車室内の目標温度（車室内設定温度）、Ｔｒは内気温センサ６１によって検出された内気温、Ｔａｍは外気温センサ６２によって検出された外気温、Ｔｓは日射センサ６３によって検出された日射量である。Ｋｓｅｔ、Ｋｒ、Ｋａｍ、Ｋｓは制御ゲインであり、Ｃは補正用の定数である。 Specifically, the target outlet temperature TAO is calculated by the following equation F1. TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × As + C (F1)
In addition, Tset is a target temperature in the vehicle interior (vehicle interior setting temperature) set by the temperature setting switch, Tr is the internal air temperature detected by the internal air temperature sensor 61, Tam is the external air temperature detected by the external air temperature sensor 62, and Ts Is the amount of solar radiation detected by the solar radiation sensor 63. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.
　そして、操作パネル７０のエアコンスイッチが投入された状態で、目標吹出温度ＴＡＯが予め定めた冷房基準温度αよりも低くなっている場合には、運転モードが冷房モードに切り替えられる。 {Circle around (5)} When the target air outlet temperature TAO is lower than the predetermined cooling reference temperature α with the air conditioner switch on the operation panel 70 turned on, the operation mode is switched to the cooling mode.
　また、操作パネル７０のエアコンスイッチが投入された状態で、目標吹出温度ＴＡＯが冷房基準温度α以上になっており、かつ、外気温Ｔａｍが予め定めた除湿暖房基準温度βよりも高くなっている場合には、運転モードが直列除湿暖房モードに切り替えられる。 Further, with the air conditioner switch of the operation panel 70 turned on, the target outlet temperature TAO is equal to or higher than the cooling reference temperature α, and the outside air temperature Tam is higher than the predetermined dehumidifying heating reference temperature β. In this case, the operation mode is switched to the in-line dehumidification heating mode.
　また、操作パネル７０のエアコンスイッチが投入された状態で、目標吹出温度ＴＡＯが冷房基準温度α以上になっており、かつ、外気温Ｔａｍが除湿暖房基準温度β以下になっている場合には、運転モードが並列除湿暖房モードに切り替えられる。 When the target outlet temperature TAO is equal to or higher than the cooling reference temperature α and the outside air temperature Tam is equal to or lower than the dehumidifying heating reference temperature β in a state where the air conditioner switch of the operation panel 70 is turned on, The operation mode is switched to the parallel dehumidification heating mode.
　また、エアコンスイッチの冷房スイッチが投入されていない場合には、運転モードが暖房モードに切り替えられる。 運 転 If the cooling switch of the air conditioner switch is not turned on, the operation mode is switched to the heating mode.
　このため、冷房モードは、主に夏季のように比較的外気温が高い場合に実行される。直列除湿暖房モードは、主に春季あるいは秋季に実行される。並列除湿暖房モードは、主に早春季あるいは晩秋季のように直列除湿暖房モードよりも高い加熱能力で送風空気を加熱する必要のある場合に実行される。暖房モードは、主に冬季の低外気温時に実行される。以下に各運転モードにおける作動を説明する。 Therefore, the cooling mode is mainly executed when the outside air temperature is relatively high, such as in summer. The in-line dehumidification heating mode is mainly performed in the spring or autumn. The parallel dehumidifying and heating mode is mainly executed when it is necessary to heat the blown air with a higher heating capacity than in the series dehumidifying and heating mode, such as early spring or late autumn. The heating mode is mainly executed at a low outside air temperature in winter. The operation in each operation mode will be described below.
　（ａ）冷房モード
　本実施形態の冷凍サイクル装置１０では、前述の如く、冷房モードとして、第１冷房モードおよび第２冷房モードの２つの運転モードを実行することができる。 (A) Cooling Mode In the refrigeration cycle apparatus 10 of the present embodiment, as described above, two operation modes of the first cooling mode and the second cooling mode can be executed as the cooling mode.
　第１冷房モードと第２冷房モードとの切り替えは、図５に示す制御フローが実行されることによって行われる。図５に示す制御フローは、空調制御プログラムのメインルーチンのサブルーチンとして実行される。図５に示す制御フローは、メインルーチンにて、冷房モードが選択された際に、所定の周期毎に実行される。図５の制御フローの詳細については、後述する。 The switching between the first cooling mode and the second cooling mode is performed by executing the control flow shown in FIG. The control flow shown in FIG. 5 is executed as a subroutine of the main routine of the air conditioning control program. The control flow shown in FIG. 5 is executed at predetermined intervals when the cooling mode is selected in the main routine. Details of the control flow in FIG. 5 will be described later.
　まず、第１冷房モードおよび第２冷房モードに共通する冷房モードの基本的な作動について説明する。冷房モードでは、制御装置６０が、暖房用膨張弁１４ａを全開状態とし、冷房用膨張弁１４ｂを減圧作用を発揮する絞り状態とする。また、制御装置６０は、除湿用開閉弁１５ａを閉じ、暖房用開閉弁１５ｂを閉じる。 First, the basic operation of the cooling mode common to the first cooling mode and the second cooling mode will be described. In the cooling mode, the control device 60 causes the heating expansion valve 14a to be in a fully open state and the cooling expansion valve 14b to be in a throttled state in which a decompression effect is exerted. Further, the control device 60 closes the dehumidifying on-off valve 15a and closes the heating on-off valve 15b.
　従って、冷房モードの冷凍サイクル装置１０では、圧縮機１１の吐出口、水－冷媒熱交換器１２（、暖房用膨張弁１４ａ）、室外熱交換器１６、逆止弁１７、冷房用膨張弁１４ｂ、室内蒸発器１８、蒸発圧力調整弁２０、アキュムレータ２１、圧縮機１１の吸入口の順に冷媒が循環する蒸気圧縮式の冷凍サイクルが構成される。 Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12 (the heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, and the cooling expansion valve 14b A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the indoor evaporator 18, the evaporating pressure regulating valve 20, the accumulator 21, and the suction port of the compressor 11 is configured.
　このサイクル構成で、制御装置６０は、出力側に接続された各種制御対象機器へ出力される制御信号等を適宜決定し、決定された制御信号等を各種制御対象機器へ出力する。 In this cycle configuration, the control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and outputs the determined control signals and the like to various control target devices.
　例えば、制御装置６０は、蒸発器温度センサ６４ｆによって検出された蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯに近づくように、圧縮機１１の回転数Ｎｃを調整するための制御信号を決定する。目標蒸発器温度ＴＥＯは、目標吹出温度ＴＡＯに基づいて、予め制御装置６０に記憶された冷房モード用の制御マップを参照して決定される。 For example, the control device 60 determines a control signal for adjusting the rotation speed Nc of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 64f approaches the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target outlet temperature TAO with reference to a cooling mode control map stored in the control device 60 in advance.
　この制御マップでは、目標吹出温度ＴＡＯの上昇に伴って、目標蒸発器温度ＴＥＯが上昇するように決定される。さらに、目標蒸発器温度ＴＥＯは、室内蒸発器１８の着霜を抑制可能な範囲（具体的には、１℃以上）の値に決定される。 In this control map, the target evaporator temperature TEO is determined to increase as the target outlet temperature TAO increases. Further, the target evaporator temperature TEO is determined to a value within a range (specifically, 1 ° C. or more) in which frost formation on the indoor evaporator 18 can be suppressed.
　また、制御装置６０は、予め定めた冷房モード用の水圧送能力を発揮するように、高温側熱媒体ポンプ４１へ出力される制御電圧を決定する。 {Circle around (4)} The control device 60 determines the control voltage to be output to the high-temperature side heat transfer medium pump 41 so as to exhibit a predetermined hydraulic pumping capacity for the cooling mode.
　また、制御装置６０は、目標吹出温度ＴＡＯ、蒸発器温度Ｔｅｆｉｎ、高温側熱媒体温度センサ６６ａによって検出された高温側熱媒体温度ＴＷＨに基づいて、エアミックスドア用の電動アクチュエータへ出力される制御信号を決定する。この制御信号は、車室内へ吹き出される送風空気の温度が目標吹出温度ＴＡＯに近づくように決定される。 Further, the control device 60 controls the output to the electric actuator for the air mixing door based on the target blowing temperature TAO, the evaporator temperature Tefin, and the high-temperature heat medium temperature TWH detected by the high-temperature heat medium temperature sensor 66a. Determine the signal. This control signal is determined such that the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.
　このため、冷房モードの冷凍サイクル装置１０では、水－冷媒熱交換器１２および室外熱交換器１６を凝縮器として機能させ、室内蒸発器１８を蒸発器として機能させる冷凍サイクルが構成される。従って、冷房モードでは、室内蒸発器１８にて冷却された送風空気を、ヒータコア４２にて再加熱して車室内へ吹き出すことによって、車室内の冷房を行うことができる。 Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a condenser and the indoor evaporator 18 functions as an evaporator is configured. Therefore, in the cooling mode, the inside of the vehicle compartment can be cooled by blowing the air cooled by the indoor evaporator 18 to the heater core 42 and blowing it out into the vehicle compartment.
　次に、図５を用いて、第１冷房モードと第２冷房モードとの切り替えについて説明する。まず、ステップＳ１０では、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯに到達しているか否かが判定される。 Next, switching between the first cooling mode and the second cooling mode will be described with reference to FIG. First, in step S10, it is determined whether or not the evaporator temperature Tefin has reached the target evaporator temperature TEO.
　ステップＳ１０にて、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯになっていると判定された場合は、ステップＳ３０へ進み、ステップＳ３０～Ｓ５０に示される第１冷房モードの制御を行う。ステップＳ１０にて、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯになっていないと判定された場合、すなわち、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯよりも高くなっている場合は、ステップＳ２０へ進む。 If it is determined in step S10 that the evaporator temperature Tefin has reached the target evaporator temperature TEO, the process proceeds to step S30, and the control of the first cooling mode shown in steps S30 to S50 is performed. If it is determined in step S10 that the evaporator temperature Tefin is not at the target evaporator temperature TEO, that is, if the evaporator temperature Tefin is higher than the target evaporator temperature TEO, the process proceeds to step S20. .
　ステップＳ２０では、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘに到達しているか否かが判定される。最大回転数ＮｃＭａｘとしては、圧縮機１１の耐久性能から決定される最大回転数や、運転条件に応じて騒音抑制等のために決定される最大回転数を採用することができる。 In step S20, it is determined whether or not the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax. As the maximum rotation speed NcMax, a maximum rotation speed determined from the durability performance of the compressor 11 or a maximum rotation speed determined for noise suppression or the like in accordance with operating conditions can be adopted.
　ステップＳ２０にて、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘになっていると判定された場合は、ステップＳ１００へ進み、ステップＳ１００～Ｓ１４０に示される第２冷房モードでの運転を行う。ステップＳ２０にて、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘになっていないと判定された場合、すなわち、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘに到達していないと判定された場合は、ステップＳ３０へ進み、第１冷房モードでの運転を行う。 If it is determined in step S20 that the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the process proceeds to step S100, and the operation in the second cooling mode shown in steps S100 to S140 is performed. In step S20, when it is determined that the rotation speed Nc of the compressor 11 has not reached the maximum rotation speed NcMax, that is, it is determined that the rotation speed Nc of the compressor 11 has not reached the maximum rotation speed NcMax. In this case, the process proceeds to step S30, and the operation in the first cooling mode is performed.
　ステップＳ３０では、室外熱交換器１６から流出して冷房用膨張弁１４ｂへ流入する冷媒の過冷却度ＳＣの目標値として、第１冷房モード用の目標過冷却度ＳＣＯ１を決定して、ステップＳ４０へ進む。目標過冷却度ＳＣＯ１は、図５のステップＳ３０の制御特性図に示す制御マップを参照して決定される。この制御マップでは、外気温Ｔａｍに基づいて、サイクルの成績係数（ＣＯＰ）が極大値に近づくように、目標過冷却度ＳＣＯ１を決定する。 In step S30, a target supercooling degree SCO1 for the first cooling mode is determined as a target value of the supercooling degree SC of the refrigerant flowing out of the outdoor heat exchanger 16 and flowing into the cooling expansion valve 14b, and step S40 is performed. Proceed to. The target degree of supercooling SCO1 is determined with reference to a control map shown in the control characteristic diagram of step S30 in FIG. In this control map, the target degree of supercooling SCO1 is determined based on the outside temperature Tam so that the coefficient of performance (COP) of the cycle approaches the maximum value.
　ステップＳ４０では、過冷却度ＳＣが目標過冷却度ＳＣＯ１に近づくように、冷房用膨張弁１４ｂの絞り開度の変化量ΔＥＶＣ１を決定して、ステップＳ５０へ進む。過冷却度ＳＣは、第３冷媒温度センサ６４ｃによって検出された温度Ｔ３および第１冷媒圧力センサ６５ａによって検出された圧力Ｐ１を用いて算定される。 In step S40, the change amount ΔEVC1 of the throttle opening of the cooling expansion valve 14b is determined so that the subcooling degree SC approaches the target subcooling degree SCO1, and the process proceeds to step S50. The degree of supercooling SC is calculated using the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.
　ステップＳ５０では、冷房用膨張弁１４ｂの絞り開度の変化量ΔＥＶＣが決定されて、ステップＳ６０へ進む。ステップＳ５０では、変化量ΔＥＶＣとして、ステップＳ４０で決定された変化量ΔＥＶＣ１が採用される。 In step S50, the amount of change ΔEVC in the throttle opening of the cooling expansion valve 14b is determined, and the process proceeds to step S60. In step S50, the change amount ΔEVC1 determined in step S40 is adopted as the change amount ΔEVC.
　ステップＳ６０では、冷房用膨張弁１４ｂの前回の絞り開度ＥＶＣｎ－１にステップＳ７０で決定された変化量ΔＥＶＣが加算されて、今回の絞り開度ＥＶＣｎが決定される。そして、今回の絞り開度ＥＶＣｎとなるように、冷房用膨張弁１４ｂへ出力される制御信号が決定されて、メインルーチンへ戻る。 In step S60, the change amount ΔEVC determined in step S70 is added to the previous throttle opening EVCn-1 of the cooling expansion valve 14b, and the current throttle opening EVCn is determined. Then, the control signal to be output to the cooling expansion valve 14b is determined so that the current throttle opening EVCn is obtained, and the process returns to the main routine.
　一方、ステップＳ１００では、過冷却度ＳＣの目標値として、第２冷房モード用の目標過冷却度ＳＣＯ２を決定して、ステップＳ１１０へ進む。目標過冷却度ＳＣＯ２は、図５のステップＳ１００の制御特性図に示す制御マップを参照して決定される。この制御マップでは、ステップＳ３０で決定される目標過冷却度ＳＣＯ１に対して所定量（本実施形態では、１０℃）を加算した値となるように、目標過冷却度ＳＣＯ２を決定する。 On the other hand, in step S100, a target supercooling degree SCO2 for the second cooling mode is determined as a target value of the supercooling degree SC, and the process proceeds to step S110. The target degree of supercooling SCO2 is determined with reference to a control map shown in the control characteristic diagram of step S100 in FIG. In this control map, the target supercooling degree SCO2 is determined so as to be a value obtained by adding a predetermined amount (10 ° C. in the present embodiment) to the target supercooling degree SCO1 determined in step S30.
　ステップＳ１１０では、過冷却度ＳＣが目標過冷却度ＳＣＯ２に近づくように、冷房用膨張弁１４ｂの絞り開度の変化量ΔＥＶＣ１を決定して、ステップＳ１２０へ進む。 In step S110, the amount of change ΔEVC1 in the throttle opening of the cooling expansion valve 14b is determined so that the subcooling degree SC approaches the target subcooling degree SCO2, and the process proceeds to step S120.
　ステップＳ１２０では、室内蒸発器１８の出口側冷媒の過熱度ＳＨの目標値として、第２冷房モード用の目標過熱度ＳＨＯ２を決定して、ステップＳ１３０へ進む。本実施形態では、目標過熱度ＳＨＯ２を、１０℃に決定する。 In Step S120, the target superheat degree SHO2 for the second cooling mode is determined as the target value of the superheat degree SH of the refrigerant on the outlet side of the indoor evaporator 18, and the process proceeds to Step S130. In the present embodiment, the target superheat degree SHO2 is determined to be 10 ° C.
　ステップＳ１３０では、過熱度ＳＨが目標過熱度ＳＨＯ２に近づくように、冷房用膨張弁１４ｂの絞り開度の変化量ΔＥＶＣ２を決定して、ステップＳ１４０へ進む。ステップＳ１４０では、冷房用膨張弁１４ｂの絞り開度の変化量ΔＥＶＣが決定されて、ステップＳ６０へ進む。ステップＳ１４０では、変化量ΔＥＶＣとして、ステップＳ１１０で決定された変化量ΔＥＶＣ１およびステップＳ１３０で決定された変化量ΔＥＶＣ２のうち、大きい方の値が採用される。 In step S130, the amount of change ΔEVC2 in the throttle opening of the cooling expansion valve 14b is determined so that the superheat degree SH approaches the target superheat degree SHO2, and the process proceeds to step S140. In step S140, the change amount ΔEVC of the throttle opening of the cooling expansion valve 14b is determined, and the process proceeds to step S60. In step S140, the larger value of the change amount ΔEVC1 determined in step S110 and the change amount ΔEVC2 determined in step S130 is adopted as the change amount ΔEVC.
　ここで、ステップＳ１００で決定される目標過冷却度ＳＣＯ２は、充分に高い値となるように設定されている。より詳細には、実際の過熱度ＳＨが目標過熱度ＳＨＯ２となるように冷房用膨張弁１４ｂの絞り開度が決定されても、実際の過冷却度ＳＣが目標過冷却度ＳＣＯ２に到達しない程度に高い値となるように設定されている。 Here, the target supercooling degree SCO2 determined in step S100 is set to be a sufficiently high value. More specifically, even if the throttle opening of the cooling expansion valve 14b is determined so that the actual superheat degree SH becomes the target superheat degree SHO2, the actual supercooling degree SC does not reach the target supercooling degree SCO2. Is set to a high value.
　このため、ステップＳ１１０で決定された変化量ΔＥＶＣ１は、冷房用膨張弁１４ｂの絞り開度を低下させるために負の値となり、ステップＳ１３０で決定された変化量ΔＥＶＣ２よりも小さい値となりやすい。従って、第２冷却モードのステップＳ７０では、変化量ΔＥＶＣとして、変化量ΔＥＶＣ２が採用されることが多い。 Therefore, the variation ΔEVC1 determined in step S110 becomes a negative value in order to decrease the throttle opening of the cooling expansion valve 14b, and tends to be smaller than the variation ΔEVC2 determined in step S130. Therefore, in step S70 of the second cooling mode, the change amount ΔEVC2 is often adopted as the change amount ΔEVC.
　以上の説明から明かなように、ステップＳ３０、Ｓ１００は、冷房用膨張弁１４ｂへ流入する冷媒の目標過冷却度ＳＣＯ１、ＳＣＯ２を決定する目標過冷却度決定部である。また、ステップＳ１２０は、室内蒸発器１８の出口側冷媒の目標過熱度ＳＨＯ２を決定する目標過熱度決定部である。 As is clear from the above description, steps S30 and S100 are target supercooling degree determination units that determine the target supercooling degrees SCO1 and SCO2 of the refrigerant flowing into the cooling expansion valve 14b. Step S120 is a target superheat degree determination unit that determines the target superheat degree SHO2 of the refrigerant on the outlet side of the indoor evaporator 18.
　さらに、本実施形態では、ステップＳ１０、Ｓ２０に記載されているように、室内蒸発器１８における送風空気の冷却能力が不足していると判定される条件が成立したものとしている。すなわち、冷却能力不足条件が成立したものとしている。より詳細には、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯになっておらず、かつ、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘになっている際に、冷却能力不足条件が成立したものとしている。 Further, in the present embodiment, as described in steps S10 and S20, it is assumed that the condition for determining that the cooling capacity of the blown air in the indoor evaporator 18 is insufficient is satisfied. That is, it is assumed that the cooling capacity shortage condition is satisfied. More specifically, when the evaporator temperature Tefin has not reached the target evaporator temperature TEO and the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the cooling capacity shortage condition has been satisfied. And
　次に、図６～図１０を用いて、第１冷房モードおよび第２冷房モードの詳細作動について説明する。図６～図８は、各運転モード時における室外熱交換器１６内の液相冷媒の分布を模式的に表したものであり、液相冷媒が分布する領域を斜線ハッチングで模式的に示している。図９では、図６～図８に示す状態となる冷房用膨張弁１４ｂの絞り開度を、それぞれ（Ａ）～（Ｃ）で示している。図１０では、第１冷房モード時の冷媒の状態の変化を破線で示し、第２冷房モード時の冷媒の状態の変化を太実線で示している。 Next, the detailed operations of the first cooling mode and the second cooling mode will be described with reference to FIGS. 6 to 8 schematically show the distribution of the liquid-phase refrigerant in the outdoor heat exchanger 16 in each operation mode, and the region where the liquid-phase refrigerant is distributed is schematically shown by hatching. I have. In FIG. 9, the throttle openings of the cooling expansion valve 14b in the states shown in FIGS. 6 to 8 are indicated by (A) to (C), respectively. In FIG. 10, a change in the state of the refrigerant in the first cooling mode is indicated by a broken line, and a change in the state of the refrigerant in the second cooling mode is indicated by a thick solid line.
　まず、第１冷房モードでは、前述の如く、過冷却度ＳＣが目標過冷却度ＳＣＯ１に近づくように冷房用膨張弁１４ｂの絞り開度が制御される。この絞り開度は、図９では、絞り開度（Ａ）で示される。 First, in the first cooling mode, as described above, the throttle opening of the cooling expansion valve 14b is controlled such that the supercooling degree SC approaches the target supercooling degree SCO1. This throttle opening is indicated by the throttle opening (A) in FIG.
　第１冷房モードでは、図６に示すように、室外熱交換器１６の第１熱交換部１６ａ、および第２熱交換部１６ｂの冷媒流れ上流側の領域が、冷媒を凝縮させる凝縮部になる。さらに、第２熱交換部１６ｂの冷媒流れ下流側の領域が、液相冷媒を過冷却する過冷却部になる。このため、サイクルの余剰冷媒は、図９のアキュムレータ２１内の液面高さＨに示すように、アキュムレータ２１内に貯えられる。 In the first cooling mode, as shown in FIG. 6, a region on the upstream side of the refrigerant flow of the first heat exchange unit 16a and the second heat exchange unit 16b of the outdoor heat exchanger 16 is a condensing unit that condenses the refrigerant. . Furthermore, a region on the downstream side of the refrigerant flow of the second heat exchange unit 16b is a subcooling unit that supercools the liquid-phase refrigerant. Therefore, the excess refrigerant of the cycle is stored in the accumulator 21 as shown by the liquid level H in the accumulator 21 in FIG.
　従って、第１冷房モードでは、図１０のモリエル線図の破線で示すように、圧縮機１１が、アキュムレータ２１から、冷凍機油が溶け込んだ液相冷媒を含む比較的乾き度の高い気液二相冷媒（図１０のａ１点）を吸入して圧縮する。圧縮機１１から吐出された冷媒は、室外熱交換器１６へ流入し、外気と熱交換して放熱する（図１０のｂ１点からｃ１点）。この際、室外熱交換器１６から流出した冷媒（図１０のｃ１点）の過冷却度ＳＣは、目標過冷却度ＳＣＯ１に近づく。 Therefore, in the first cooling mode, as shown by the broken line in the Mollier diagram of FIG. 10, the compressor 11 sends the relatively high dryness gas-liquid two-phase containing the liquid-phase refrigerant in which the refrigerating machine oil is dissolved, from the accumulator 21. The refrigerant (point a1 in FIG. 10) is sucked and compressed. The refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 16 and exchanges heat with the outside air to radiate heat (points b1 to c1 in FIG. 10). At this time, the supercooling degree SC of the refrigerant (point c1 in FIG. 10) flowing out of the outdoor heat exchanger 16 approaches the target supercooling degree SCO1.
　室外熱交換器１６から流出した冷媒は、冷房用膨張弁１４ｂにて減圧される（図１０のｃ１点からｄ１点）。冷房用膨張弁１４ｂにて減圧された冷媒は、室内蒸発器１８にて送風空気から吸熱して蒸発する（図１０のｄ１点からａ１点）。これにより、送風空気が冷却される。室内蒸発器１８から流出した冷媒は、アキュムレータ２１へ流入して気液分離される。 冷媒 The refrigerant flowing out of the outdoor heat exchanger 16 is decompressed by the cooling expansion valve 14b (point c1 to point d1 in FIG. 10). The refrigerant decompressed by the cooling expansion valve 14b absorbs heat from the blown air in the indoor evaporator 18 and evaporates (from point d1 to point a1 in FIG. 10). Thereby, the blown air is cooled. The refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 21 and is separated into gas and liquid.
　これにより、第１冷房モードの冷凍サイクル装置１０では、サイクルのＣＯＰが極大値になるように、送風空気を冷却する。 Accordingly, in the refrigeration cycle apparatus 10 in the first cooling mode, the blast air is cooled so that the COP of the cycle becomes a maximum value.
　次に、冷却能力不足条件が成立して、第２冷房モードへ移行すると、過冷却度ＳＣの目標値として、目標過冷却度ＳＣＯ１よりも高い値に決定される目標過冷却度ＳＣＯ２が採用される。このため、第１冷房モードよりも過冷却度ＳＣを上昇させるために、冷房用膨張弁１４ｂの絞り開度が減少する。図９では、絞り開度（Ａ）から絞り開度（Ｂ）へ減少する。 Next, when the cooling capacity shortage condition is satisfied and the mode shifts to the second cooling mode, the target supercooling degree SCO2 determined to be higher than the target supercooling degree SCO1 is adopted as the target value of the supercooling degree SC. You. For this reason, in order to increase the degree of supercooling SC from the first cooling mode, the throttle opening of the cooling expansion valve 14b decreases. In FIG. 9, the throttle opening (A) decreases to the throttle opening (B).
　これにより、図７に示すように、室外熱交換器１６の第１熱交換部１６ａが凝縮部になる。さらに、第２熱交換部１６ｂの全域が高圧液相冷媒で満たされて過冷却部になる。 Thereby, as shown in FIG. 7, the first heat exchange section 16a of the outdoor heat exchanger 16 becomes a condenser section. Further, the entire area of the second heat exchange section 16b is filled with the high-pressure liquid-phase refrigerant to become a supercooling section.
　また、図９に示すように、第１冷房モードよりも、アキュムレータ２１内に貯えられた余剰冷媒が減少する。すなわち、液面高さＨが低下する。また、室外熱交換器１６における冷媒凝縮圧力が上昇する。さらに、目標過冷却度ＳＣＯ２は目標過冷却度ＳＣＯ１に対して充分に高い値に設定されているので、実際の過冷却度ＳＣは、目標過冷却度ＳＣＯ２に到達していない。 Also, as shown in FIG. 9, the surplus refrigerant stored in the accumulator 21 is smaller than in the first cooling mode. That is, the liquid level H decreases. Further, the refrigerant condensation pressure in the outdoor heat exchanger 16 increases. Furthermore, since the target degree of supercooling SCO2 is set to a value sufficiently higher than the target degree of supercooling SCO1, the actual degree of supercooling SC has not reached the target degree of supercooling SCO2.
　第２冷房モードでは、過冷却度ＳＣの目標値として、目標過冷却度ＳＣＯ２が採用されるだけでなく、室内蒸発器１８の出口側冷媒の過熱度ＳＨの目標値として、目標過熱度ＳＨＯ２（具体的には、１０℃）が採用される。このため、冷房用膨張弁１４ｂの絞り開度がさらに減少する。図９では、絞り開度（Ｂ）から絞り開度（Ｃ）へ減少する。 In the second cooling mode, not only the target supercooling degree SCO2 is adopted as the target value of the supercooling degree SC, but also the target superheat degree SHO2 ( Specifically, 10 ° C.) is employed. For this reason, the throttle opening of the cooling expansion valve 14b further decreases. In FIG. 9, the throttle opening (B) decreases to the throttle opening (C).
　これにより、図８の斜線ハッチングで示すように、モジュレータ部１６５内も高圧液相冷媒で満たされる。つまり、アキュムレータ２１内に貯えられていたサイクルの余剰冷媒が、モジュレータ部１６５内へ移動する。その結果、アキュムレータ２１内の冷媒および室内蒸発器１８の出口側冷媒の過熱度ＳＨが、目標過熱度ＳＨＯ２（具体的には、１０℃）へ上昇する。 Accordingly, as shown by hatching in FIG. 8, the inside of the modulator 165 is also filled with the high-pressure liquid-phase refrigerant. That is, the surplus refrigerant of the cycle stored in the accumulator 21 moves into the modulator section 165. As a result, the superheat degree SH of the refrigerant in the accumulator 21 and the refrigerant on the outlet side of the indoor evaporator 18 increases to the target superheat degree SHO2 (specifically, 10 ° C.).
　この際、アキュムレータ２１内に貯えられていたサイクルの余剰冷媒が、モジュレータ部１６５内へ移動しても、凝縮部となる第１熱交換部１６ａの熱交換面積は縮小しない。このため、第２冷房モードでは、冷房用膨張弁１４ｂの絞り開度が、絞り開度（Ｂ）より減少しても、室外熱交換器１６における冷媒凝縮圧力が上昇してしまうことはない。 At this time, even if the excess refrigerant of the cycle stored in the accumulator 21 moves into the modulator 165, the heat exchange area of the first heat exchange unit 16a serving as the condensation unit does not decrease. For this reason, in the second cooling mode, even if the throttle opening of the cooling expansion valve 14b is smaller than the throttle opening (B), the refrigerant condensation pressure in the outdoor heat exchanger 16 does not increase.
　従って、第２冷房モードでは、図１０のモリエル線図の太実線に示すように、圧縮機１１が、アキュムレータ２１から、過熱度を有する気相冷媒（図１０のａ２点）を吸入して圧縮する。圧縮機１１から吐出された冷媒は、室外熱交換器１６にて、外気と熱交換して放熱する（図１０のｂ２点からｃ２点）。そして、サイクルの余剰冷媒が高圧液相冷媒となってモジュレータ部１６５に貯えられる。 Therefore, in the second cooling mode, the compressor 11 sucks the gaseous refrigerant having the degree of superheat (point a2 in FIG. 10) from the accumulator 21 and compresses it, as indicated by the thick solid line in the Mollier diagram in FIG. I do. The refrigerant discharged from the compressor 11 exchanges heat with the outside air and radiates heat in the outdoor heat exchanger 16 (point b2 to point c2 in FIG. 10). Then, the excess refrigerant of the cycle becomes high-pressure liquid-phase refrigerant and is stored in the modulator section 165.
　室外熱交換器１６から流出した冷媒は、冷房用膨張弁１４ｂにて減圧される（図１０のｃ２点からｄ２点）。冷房用膨張弁１４ｂにて減圧された冷媒は、室内蒸発器１８にて送風空気から吸熱して蒸発する（図１０のｄ２点からａ２点）。これにより、送風空気が冷却される。この際、室内蒸発器１８の出口側冷媒の過熱度ＳＨは、目標過熱度ＳＨＯ２に近づく。室内蒸発器１８から流出した過熱度を有する冷媒は、アキュムレータ２１へ流入する。 冷媒 The refrigerant flowing out of the outdoor heat exchanger 16 is decompressed by the cooling expansion valve 14b (from point c2 to point d2 in FIG. 10). The refrigerant decompressed by the cooling expansion valve 14b absorbs heat from the blown air in the indoor evaporator 18 and evaporates (from point d2 to point a2 in FIG. 10). Thereby, the blown air is cooled. At this time, the degree of superheat SH of the refrigerant on the outlet side of the indoor evaporator 18 approaches the target degree of superheat SHO2. The superheated refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 21.
　このため、第２冷房モードでは、図１０に示すように、室内蒸発器１８の出口側冷媒のエンタルピから室内蒸発器１８の入口側冷媒のエンタルピを減算したエンタルピ差Δｉｅ２が、第１冷房モード時のエンタルピ差Δｉｅ１よりも増大する。つまり、第２冷房モードの冷凍サイクル装置１０では、第１冷房モードよりも高い冷却能力で、送風空気を冷却することができる。 Therefore, in the second cooling mode, as shown in FIG. 10, the enthalpy difference Δie2 obtained by subtracting the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 from the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 is equal to that in the first cooling mode. Is larger than the enthalpy difference Δie1. That is, the refrigeration cycle device 10 in the second cooling mode can cool the blown air with a higher cooling capacity than in the first cooling mode.
　（ｂ）直列除湿暖房モード
　直列除湿暖房モードでは、制御装置６０が、暖房用膨張弁１４ａを絞り状態とし、冷房用膨張弁１４ｂを絞り状態とする。また、制御装置６０は、除湿用開閉弁１５ａを閉じ、暖房用開閉弁１５ｂを閉じる。 (B) In-line dehumidification and heating mode In the in-series dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to the throttled state and sets the cooling expansion valve 14b to the throttled state. Further, the control device 60 closes the dehumidifying on-off valve 15a and closes the heating on-off valve 15b.
　従って、直列除湿暖房モードの冷凍サイクル装置１０では、圧縮機１１、水－冷媒熱交換器１２、暖房用膨張弁１４ａ、室外熱交換器１６、逆止弁１７、冷房用膨張弁１４ｂ、室内蒸発器１８、蒸発圧力調整弁２０、アキュムレータ２１、圧縮機１１の順に冷媒が循環する蒸気圧縮式の冷凍サイクルが構成される。 Therefore, in the refrigeration cycle apparatus 10 in the serial dehumidification heating mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporation A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the device 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
　このサイクル構成で、制御装置６０は、冷房モードと同様に、出力側に接続された各種制御対象機器へ出力される制御信号等を適宜決定し、決定された制御信号等を各種制御対象機器へ出力する。 In this cycle configuration, similarly to the cooling mode, the control device 60 appropriately determines control signals and the like output to various control target devices connected to the output side, and sends the determined control signals and the like to the various control target devices. Output.
　例えば、制御装置６０は、空調風温度センサ６９にて検出された送風空気温度ＴＡＶが、目標吹出温度ＴＡＯに近づくように、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂへ出力される制御信号を決定する。従って、直列除湿暖房モードでは、サイクルの余剰冷媒がアキュムレータ２１内に貯えられる。 For example, the control device 60 transmits a control signal output to the heating expansion valve 14a and the cooling expansion valve 14b such that the blast air temperature TAV detected by the conditioned air temperature sensor 69 approaches the target outlet temperature TAO. decide. Therefore, in the series dehumidification heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
　より具体的には、制御装置６０は、目標吹出温度ＴＡＯの上昇に伴って、暖房用膨張弁１４ａの絞り開度を減少させ、冷房用膨張弁１４ｂの絞り開度を増加させるように制御信号を決定する。 More specifically, the control device 60 controls the control signal so as to decrease the throttle opening of the heating expansion valve 14a and increase the throttle opening of the cooling expansion valve 14b as the target outlet temperature TAO increases. To determine.
　このため、直列除湿暖房モードの冷凍サイクル装置１０では、水－冷媒熱交換器１２を凝縮器として機能させ、室内蒸発器１８を蒸発器として機能させる冷凍サイクルが構成される。 Therefore, in the refrigeration cycle apparatus 10 in the series dehumidification heating mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a condenser and the indoor evaporator 18 functions as an evaporator is configured.
　さらに、室外熱交換器１６における冷媒の飽和温度が外気温Ｔａｍよりも高い場合には、室外熱交換器１６を凝縮器として機能させる冷凍サイクルが構成される。また、室外熱交換器１６における冷媒の飽和温度が外気温Ｔａｍよりも低い場合には、室外熱交換器１６を蒸発器として機能させる冷凍サイクルが構成される。 Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a refrigeration cycle in which the outdoor heat exchanger 16 functions as a condenser is configured. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a refrigeration cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.
　そして、室外熱交換器１６における冷媒の飽和温度が外気温Ｔａｍよりも高い場合には、目標吹出温度ＴＡＯの上昇に伴って室外熱交換器１６の冷媒の飽和温度を低下させて、室外熱交換器１６における冷媒の放熱量を減少させることができる。これにより、水－冷媒熱交換器１２における冷媒の放熱量を増加させて、ヒータコア４２における送風空気の加熱能力を向上させることができる。 When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is reduced with the rise of the target outlet temperature TAO, and the outdoor heat exchange is performed. The heat radiation amount of the refrigerant in the vessel 16 can be reduced. Thereby, the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air in the heater core 42 can be improved.
　また、室外熱交換器１６における冷媒の飽和温度が外気温Ｔａｍよりも低い場合には、目標吹出温度ＴＡＯの上昇に伴って室外熱交換器１６の冷媒の飽和温度を低下させて、室外熱交換器１６における冷媒の吸熱量を増加させることができる。これにより、水－冷媒熱交換器１２における冷媒の放熱量を増加させて、ヒータコア４２における送風空気の加熱能力を向上させることができる。 Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is reduced with an increase in the target outlet temperature TAO, and the outdoor heat exchange is performed. The amount of heat absorbed by the refrigerant in the vessel 16 can be increased. Thereby, the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air in the heater core 42 can be improved.
　従って、直列除湿暖房モードでは、室内蒸発器１８にて冷却されて除湿された送風空気を、ヒータコア４２にて再加熱して車室内に吹き出すことによって、車室内の除湿暖房を行うことができる。さらに、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂの絞り開度を調整することによって、水－冷媒熱交換器１２における冷媒の放熱量を調整して、ヒータコア４２における送風空気の加熱能力を調整することができる。 Therefore, in the in-line dehumidifying and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed. Further, by adjusting the throttle openings of the heating expansion valve 14a and the cooling expansion valve 14b, the amount of refrigerant radiated in the water-refrigerant heat exchanger 12 is adjusted, and the heating capacity of the blower air in the heater core 42 is adjusted. can do.
　（ｃ）並列除湿暖房モード
　並列除湿暖房モードでは、制御装置６０が、暖房用膨張弁１４ａを絞り状態とし、冷房用膨張弁１４ｂを絞り状態とする。また、制御装置６０は、除湿用開閉弁１５ａを開き、暖房用開閉弁１５ｂを開く。 (C) Parallel dehumidification and heating mode In the parallel dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to a throttled state and sets the cooling expansion valve 14b to a throttled state. Further, the control device 60 opens the dehumidifying on-off valve 15a and opens the heating on-off valve 15b.
　これにより、並列除湿暖房モードの冷凍サイクル装置１０では、圧縮機１１、水－冷媒熱交換器１２、暖房用膨張弁１４ａ、室外熱交換器１６、暖房用通路２２ｂ（暖房用開閉弁１５ｂ）、アキュムレータ２１、圧縮機１１の順に冷媒が循環する蒸気圧縮式の冷凍サイクルが構成される。同時に、圧縮機１１、水－冷媒熱交換器１２、バイパス通路２２ａ（除湿用開閉弁１５ａ）、冷房用膨張弁１４ｂ、室内蒸発器１８、蒸発圧力調整弁２０、アキュムレータ２１、圧縮機１１の順に冷媒が循環する蒸気圧縮式の冷凍サイクルが構成される。すなわち、室外熱交換器１６と室内蒸発器１８が冷媒流れに対して並列的に接続される冷凍サイクルが構成される。 Thus, in the refrigeration cycle apparatus 10 in the parallel dehumidifying and heating mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b (heating on-off valve 15b), A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the accumulator 21 and the compressor 11 is configured. At the same time, the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a (dehumidifying on-off valve 15a), the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 in this order. A vapor compression refrigeration cycle in which the refrigerant circulates is configured. That is, a refrigeration cycle in which the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to the refrigerant flow is configured.
　このサイクル構成で、制御装置６０は、出力側に接続された各種制御対象機器へ出力される制御信号等を適宜決定し、決定された制御信号等を各種制御対象機器へ出力する。 In this cycle configuration, the control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and outputs the determined control signals and the like to various control target devices.
　例えば、制御装置６０は、第１冷媒圧力センサ６５ａによって検出された圧力Ｐ１が、目標凝縮圧力ＰＤＯに近づくように、圧縮機１１の回転数Ｎｃを制御する制御信号を決定する。この制御マップでは、目標吹出温度ＴＡＯの上昇に伴って、目標凝縮圧力ＰＤＯが上昇するように決定される。 For example, the control device 60 determines a control signal for controlling the rotation speed Nc of the compressor 11 such that the pressure P1 detected by the first refrigerant pressure sensor 65a approaches the target condensing pressure PDO. In this control map, it is determined that the target condensing pressure PDO increases as the target outlet temperature TAO increases.
　また、制御装置６０は、第１冷房モードと同様に、ＣＯＰが極大値に近づくように、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂへ出力される制御信号を決定する。従って、並列除湿暖房モードでは、サイクルの余剰冷媒がアキュムレータ２１内に貯えられる。 {Circle around (5)} Similarly to the first cooling mode, control device 60 determines a control signal to be output to heating expansion valve 14a and cooling expansion valve 14b such that COP approaches the maximum value. Therefore, in the parallel dehumidification heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
　このため、並列除湿暖房モードの冷凍サイクル装置１０では、水－冷媒熱交換器１２を凝縮器として機能させ、室外熱交換器１６および室内蒸発器１８を蒸発器として機能させる冷凍サイクルが構成される。 For this reason, in the refrigeration cycle apparatus 10 in the parallel dehumidification heating mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 16 and the indoor evaporator 18 function as an evaporator is configured. .
　従って、並列除湿暖房モードでは、室内蒸発器１８にて冷却されて除湿された送風空気を、ヒータコア４２にて再加熱して車室内に吹き出すことによって、車室内の除湿暖房を行うことができる。 Therefore, in the parallel dehumidifying and heating mode, the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed.
　さらに、蒸発圧力調整弁２０の作用によって、室内蒸発器１８の着霜を招くことなく、室外熱交換器１６における冷媒の蒸発温度を、室内蒸発器１８における冷媒の蒸発温度よりも低下させることができる。その結果、直列除湿暖房モード時よりも室外熱交換器１６における冷媒の吸熱量を増加させて、送風空気の加熱能力を増加させることができる。 Further, the evaporation temperature of the refrigerant in the outdoor heat exchanger 16 can be made lower than the evaporation temperature of the refrigerant in the indoor evaporator 18 without causing frost on the indoor evaporator 18 by the action of the evaporation pressure adjusting valve 20. it can. As a result, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased more than in the in-line dehumidifying and heating mode, and the heating capacity of the blown air can be increased.
　（ｄ）暖房モード
　暖房モードでは、制御装置６０が、暖房用膨張弁１４ａを絞り状態とし、冷房用膨張弁１４ｂを全閉状態とする。また、制御装置６０は、除湿用開閉弁１５ａを閉じ、暖房用開閉弁１５ｂを開く。 (D) Heating Mode In the heating mode, the control device 60 sets the heating expansion valve 14a to the throttled state and sets the cooling expansion valve 14b to the fully closed state. Further, the control device 60 closes the dehumidifying on-off valve 15a and opens the heating on-off valve 15b.
　これにより、暖房モードの冷凍サイクル装置１０では、圧縮機１１、水－冷媒熱交換器１２、暖房用膨張弁１４ａ、室外熱交換器１６、暖房用通路２２ｂ（暖房用開閉弁１５ｂ）、アキュムレータ２１、圧縮機１１の順に冷媒が循環する蒸気圧縮式の冷凍サイクルが構成される。 Thereby, in the refrigeration cycle apparatus 10 in the heating mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b (heating on-off valve 15b), the accumulator 21 Then, a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 is configured.
　このサイクル構成で、制御装置６０は、並列除湿暖房モードと同様に、出力側に接続された各種制御対象機器へ出力される制御信号等を適宜決定し、決定された制御信号等を各種制御対象機器へ出力する。 In this cycle configuration, similarly to the parallel dehumidifying and heating mode, the control device 60 appropriately determines control signals and the like to be output to various control target devices connected to the output side, and determines the determined control signals and the like for various control targets. Output to device.
　例えば、制御装置６０は、第１冷房モードと同様に、ＣＯＰが極大値に近づくように、暖房用膨張弁１４ａへ出力される制御信号を決定する。従って、暖房モードでは、サイクルの余剰冷媒がアキュムレータ２１内に貯えられる。 For example, the control device 60 determines a control signal to be output to the heating expansion valve 14a such that the COP approaches the local maximum value, as in the first cooling mode. Therefore, in the heating mode, the surplus refrigerant of the cycle is stored in the accumulator 21.
　このため、暖房モードの冷凍サイクル装置１０では、水－冷媒熱交換器１２を凝縮器として機能させ、室外熱交換器１６を蒸発器として機能させる冷凍サイクルが構成される。従って、暖房モードでは、ヒータコア４２にて加熱された送風空気を車室内に吹き出すことによって、車室内の暖房を行うことができる。 Therefore, in the refrigeration cycle apparatus 10 in the heating mode, a refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 16 functions as an evaporator. Therefore, in the heating mode, the inside of the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment.
　以上の如く、本実施形態の冷凍サイクル装置１０では、冷媒回路を切り替えて各種運モードの運転を行うことができる。これにより、車両用空調装置１では車室内の快適な空調を実現することができる。 As described above, in the refrigeration cycle apparatus 10 of the present embodiment, the operation of various operation modes can be performed by switching the refrigerant circuit. Thereby, in the vehicle air conditioner 1, comfortable air conditioning in the vehicle compartment can be realized.
　さらに、本実施形態の冷凍サイクル装置１０では、低圧側貯液部であるアキュムレータ２１を備えている。従って、運転モードに応じて凝縮器として機能する熱交換器が変化しても、アキュムレータ２１に余剰冷媒を確実に貯えることができる。 Furthermore, the refrigeration cycle device 10 of the present embodiment includes an accumulator 21 which is a low-pressure side liquid storage unit. Therefore, even if the heat exchanger functioning as a condenser changes according to the operation mode, the surplus refrigerant can be reliably stored in the accumulator 21.
　ところが、本実施形態の第１冷房モードのように、アキュムレータ２１に余剰冷媒を貯える運転モードでは、室内蒸発器１８にて発揮される送風空気の冷却能力を向上させにくい。その理由は、第１冷房モードでは、室内蒸発器１８の出口側冷媒のエンタルピから室内蒸発器１８の入口側冷媒のエンタルピを減算したエンタルピ差Δｉｅを拡大させにくいからである。 However, in the operation mode in which the surplus refrigerant is stored in the accumulator 21 as in the first cooling mode of the present embodiment, it is difficult to improve the cooling capacity of the blown air exhibited by the indoor evaporator 18. The reason is that in the first cooling mode, it is difficult to increase the enthalpy difference Δie obtained by subtracting the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 from the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18.
　より詳細には、第１冷房モードでは、室内蒸発器１８の出口側冷媒が飽和気相冷媒に近づくので、室内蒸発器１８の出口側冷媒のエンタルピを増加させることによって、エンタルピ差Δｉｅを拡大させることは難しい。 More specifically, in the first cooling mode, the outlet refrigerant of the indoor evaporator 18 approaches the saturated gas-phase refrigerant, so that the enthalpy difference Δie is increased by increasing the enthalpy of the outlet refrigerant of the indoor evaporator 18. It is difficult.
　さらに、本実施形態のように、オイル戻し穴２１３ｃが形成されたアキュムレータ２１を備える冷凍サイクル装置１０では、圧縮機１１へ吸入される冷媒が、乾き度の高い気液二相冷媒となる。このため、室内蒸発器１８の出口側冷媒が飽和気相冷媒よりもエンタルピの低い気液二相冷媒となってしまい、より一層、エンタルピ差Δｉｅを拡大させることが難しい。 Further, in the refrigeration cycle apparatus 10 including the accumulator 21 in which the oil return hole 213c is formed as in the present embodiment, the refrigerant drawn into the compressor 11 is a gas-liquid two-phase refrigerant having a high degree of dryness. For this reason, the refrigerant on the outlet side of the indoor evaporator 18 becomes a gas-liquid two-phase refrigerant having a lower enthalpy than the saturated gas-phase refrigerant, and it is difficult to further increase the enthalpy difference Δie.
　また、第１冷房モード時に、室外熱交換器１６から流出する冷媒の過冷却度を増加させ、室内蒸発器１８の入口側冷媒のエンタルピを低減させることによって、エンタルピ差Δｉｅを拡大させる手段が考えられる。 Means for increasing the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 16 in the first cooling mode and reducing the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 to increase the enthalpy difference Δie may be considered. Can be
　しかし、室外熱交換器１６から流出する冷媒の過冷却度を増加させると、室外熱交換器１６における冷媒凝縮圧力が上昇するので、サイクル構成機器の耐久寿命に悪影響を与えてしまうおそれがある。そのため、第１冷房モードのように、アキュムレータ２１に余剰冷媒を貯える運転モードでは、室内蒸発器１８における冷却能力を向上させにくい。 However, if the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 16 is increased, the refrigerant condensing pressure in the outdoor heat exchanger 16 increases, which may adversely affect the durability life of the cycle components. Therefore, in the operation mode in which the excess refrigerant is stored in the accumulator 21 as in the first cooling mode, it is difficult to improve the cooling capacity of the indoor evaporator 18.
　これに対して、本実施形態の冷凍サイクル装置１０の冷房モードでは、アキュムレータ２１に余剰冷媒を貯える第１冷房モードから、モジュレータ部１６５に余剰冷媒を貯える第２冷房モードに切り替えることができる。 On the other hand, in the cooling mode of the refrigeration cycle apparatus 10 of the present embodiment, the first cooling mode in which the excess refrigerant is stored in the accumulator 21 can be switched to the second cooling mode in which the excess refrigerant is stored in the modulator section 165.
　この第２冷房モードでは、図９、図１０を用いて説明したように、室外熱交換器１６における冷媒凝縮圧力を不必要に上昇させてしまうことなく、室外熱交換器１６から流出する冷媒の過冷却度を増加させることができる。すなわち、室外熱交換器１６における冷媒凝縮圧力を不必要に上昇させてしまうことなく、室内蒸発器１８の入口側冷媒のエンタルピを低減させることができる。 In the second cooling mode, as described with reference to FIGS. 9 and 10, the refrigerant flowing out of the outdoor heat exchanger 16 does not needlessly increase the refrigerant condensation pressure in the outdoor heat exchanger 16. The degree of supercooling can be increased. That is, the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 can be reduced without unnecessarily increasing the refrigerant condensing pressure in the outdoor heat exchanger 16.
　さらに、第２冷房モードでは、サイクルの余剰冷媒がモジュレータ部１６５内に貯えられているので、アキュムレータ２１へ過熱度を有する低圧気相冷媒を流入させることができる。従って、室内蒸発器１８の入口側冷媒のエンタルピを増加させることができる。 Further, in the second cooling mode, since the surplus refrigerant of the cycle is stored in the modulator unit 165, the low-pressure gas-phase refrigerant having a degree of superheat can flow into the accumulator 21. Therefore, the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18 can be increased.
　その結果、第２冷房モードでは、第１冷房モードよりもエンタルピ差Δｉｅを拡大させて、室内蒸発器１８における冷却能力を向上させることができる。すなわち、本実施形態の冷凍サイクル装置１０によれば、室内蒸発器１８における冷却能力を充分に向上させることができる。 As a result, in the second cooling mode, the enthalpy difference Δie can be expanded more than in the first cooling mode, and the cooling capacity of the indoor evaporator 18 can be improved. That is, according to the refrigeration cycle device 10 of the present embodiment, the cooling capacity of the indoor evaporator 18 can be sufficiently improved.
　また、本実施形態の冷凍サイクル装置１０では、図５のステップＳ１０、Ｓ２０で説明した冷却能力不足条件が成立した際に、目標過冷却度を上昇させる。これによれば、室内蒸発器１８における送風空気の冷却能力が不足した際に、確実に第１冷房モードから第２冷房モードへ移行させて、冷却能力を向上させることができる。 In addition, in the refrigeration cycle apparatus 10 of the present embodiment, when the cooling capacity shortage condition described in steps S10 and S20 in FIG. 5 is satisfied, the target degree of supercooling is increased. According to this, when the cooling capacity of the blown air in the indoor evaporator 18 is insufficient, it is possible to surely shift from the first cooling mode to the second cooling mode and improve the cooling capacity.
　また、本実施形態の冷凍サイクル装置１０では、第２冷房モードへ移行した際に、目標過熱度を上昇させる。これによれば、第２冷房モードへ移行した際に、室内蒸発器１８の出口側冷媒のエンタルピを低減させることができるので、より一層、冷却能力を向上させることができる。 In addition, in the refrigeration cycle apparatus 10 of the present embodiment, the target degree of superheat is increased when shifting to the second cooling mode. According to this, when the mode shifts to the second cooling mode, the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 can be reduced, so that the cooling capacity can be further improved.
　また、本実施形態の室外熱交換器１６では、第２冷房モードへ移行した際に、第２熱交換部１６ｂが高圧液相冷媒で満たされるように、第２熱交換部１６ｂの熱交換面積が設定されている。これによれば、第２冷房モード時に、第２熱交換部１６ｂの全域を過冷却部として利用することができ、室外熱交換器１６から流出して冷房用膨張弁１４ｂへ流入する冷媒の過冷却度ＳＣを目標過冷却度ＳＣＯ２に近づけることができる。 Further, in the outdoor heat exchanger 16 of the present embodiment, when the mode is shifted to the second cooling mode, the heat exchange area of the second heat exchange unit 16b is filled so that the second heat exchange unit 16b is filled with the high-pressure liquid-phase refrigerant. Is set. According to this, in the second cooling mode, the entire area of the second heat exchange section 16b can be used as a subcooling section, and the excess refrigerant flowing out of the outdoor heat exchanger 16 and flowing into the cooling expansion valve 14b can be used. The cooling degree SC can be made closer to the target supercooling degree SCO2.
　ここで、本開示の発明者らの検討によれば、以下のことが確認されている。まず、室外熱交換器１６の体格を、車両用空調装置に適用される一般的な冷凍サイクル装置の室外熱交換器（いわゆる、コンデンサ）と同等に設定する。且つ、第１熱交換部１６ａの熱交換面積と第２熱交換部１６ｂの熱交換面積と同等に設定する。これによれば、第２冷房モード時に過冷却度ＳＣを確実に増加させて目標過冷却度ＳＣＯ２に近づけることができることが確認されている。 Here, according to the study of the inventors of the present disclosure, the following has been confirmed. First, the physique of the outdoor heat exchanger 16 is set to be equal to that of an outdoor heat exchanger (so-called condenser) of a general refrigeration cycle device applied to a vehicle air conditioner. In addition, the heat exchange area of the first heat exchange section 16a is set to be equal to the heat exchange area of the second heat exchange section 16b. According to this, it has been confirmed that the subcooling degree SC can be reliably increased in the second cooling mode to approach the target supercooling degree SCO2.
　また、本実施形態の室外熱交換器１６では、第１熱交換部１６ａの冷媒出口１６３ｄが、第１熱交換部１６ａの最上方側に配置されている。これによれば、モジュレータ部１６５の容積が不必要に拡大してしまうことを抑制することができる。 Further, in the outdoor heat exchanger 16 of the present embodiment, the refrigerant outlet 163d of the first heat exchange unit 16a is arranged on the uppermost side of the first heat exchange unit 16a. According to this, it is possible to prevent the volume of the modulator section 165 from unnecessarily expanding.
　さらに、モジュレータ部１６５の冷媒入口１６５ａが、モジュレータ部１６５の最下方側に配置されている。これによれば、第１熱交換部１６ａから流出したモジュレータ部１６５へ流入する際に、冷媒が流れ淀んでしまう領域が形成されにくく、モジュレータ部１６５内の底部側に、液相冷媒に溶け込んだ冷凍機油が滞留してしまうことを抑制することができる。 Furthermore, the refrigerant inlet 165a of the modulator section 165 is arranged at the lowermost side of the modulator section 165. According to this, when flowing into the modulator section 165 flowing out of the first heat exchange section 16a, it is difficult to form a region in which the refrigerant flows and stagnates, and the refrigerant melts into the liquid-phase refrigerant on the bottom side inside the modulator section 165. The stagnation of the refrigerating machine oil can be suppressed.
　また、本実施形態の室外熱交換器１６では、第１熱交換部１６ａを、第２熱交換部１６ｂよりも下方側に配置している。そして、モジュレータ部１６５の内部空間から他方のタンク１６３の第２分配空間１６３ｃへ流入した冷媒が、下方側から上方側へ向かう速度成分を有するようにしている。 In addition, in the outdoor heat exchanger 16 of the present embodiment, the first heat exchange unit 16a is disposed below the second heat exchange unit 16b. The refrigerant flowing from the inner space of the modulator section 165 into the second distribution space 163c of the other tank 163 has a velocity component from the lower side to the upper side.
　これによれば、暖房モード時のように、室外熱交換器１６を蒸発器として用いる際に、第２分配空間１６３ｃへ流入した冷媒が、重力の作用によって第２分配空間１６３ｃの下方側に偏在してしまうことを抑制することができる。従って、第２パスを構成するそれぞれのチューブ１６１へ均等な流量の冷媒を分配することができ、第２熱交換部１６ｂにて、均等に冷媒を蒸発させることができる。 According to this, when the outdoor heat exchanger 16 is used as an evaporator as in the heating mode, the refrigerant flowing into the second distribution space 163c is unevenly distributed below the second distribution space 163c by the action of gravity. Can be suppressed. Therefore, a uniform flow rate of the refrigerant can be distributed to each of the tubes 161 constituting the second path, and the refrigerant can be uniformly evaporated in the second heat exchange unit 16b.
　（第２実施形態）
　本実施形態では、第１実施形態に対して、図１１に示すように、室外熱交換器１６の構成を変更した例を説明する。本実施形態の室外熱交換器１６では、第２熱交換部１６ｂが、第１熱交換部１６ａよりも上下方向下方側に配置されている。 (2nd Embodiment)
In the present embodiment, an example in which the configuration of the outdoor heat exchanger 16 is changed from the first embodiment as shown in FIG. 11 will be described. In the outdoor heat exchanger 16 of the present embodiment, the second heat exchange unit 16b is disposed below the first heat exchange unit 16a in the vertical direction.
　より具体的には、本実施形態の室外熱交換器１６では、一方のタンク１６２の上方側の空間を形成する部位に、冷媒流入ポート１６２ｄが接続されている。また、一方のタンク１６２の下方側の空間を形成する部位に、冷媒流出ポート１６２ｅが接続されている。 More specifically, in the outdoor heat exchanger 16 of the present embodiment, a refrigerant inflow port 162d is connected to a portion forming a space above the one tank 162. In addition, a refrigerant outflow port 162e is connected to a portion forming a space below the one tank 162.
　従って、一方のタンク１６２の上方側に、第１分配空間１６２ｂが形成される。さらに、一方のタンク１６２の下方側に、第２集合空間１６２ｃが形成される。また、他方のタンク１６３の上方側に、第１集合空間１６３ｂが形成される。さらに、他方のタンク１６３の下方側に、第２分配空間１６３ｃが形成される。 Therefore, the first distribution space 162b is formed above the one tank 162. Further, a second collecting space 162c is formed below one tank 162. Further, a first collecting space 163b is formed above the other tank 163. Further, a second distribution space 163c is formed below the other tank 163.
　つまり、本実施形態の室外熱交換器１６では、第１実施形態の室外熱交換器１６に対して、冷媒の流れ方向が逆転する。 That is, in the outdoor heat exchanger 16 of the present embodiment, the flow direction of the refrigerant is reversed with respect to the outdoor heat exchanger 16 of the first embodiment.
　ここで、第１実施形態で説明したように、室外熱交換器１６では、第１熱交換部１６ａの熱交換面積と第２熱交換部１６ｂの熱交換面積が同等となっている。このため、本実施形態においても、第２熱交換部１６ｂの熱交換面積は、第２冷却モード時に、第２熱交換部１６ｂが高圧液相冷媒で満たされるように設定されていることになる。 Here, as described in the first embodiment, in the outdoor heat exchanger 16, the heat exchange area of the first heat exchange section 16a is equal to the heat exchange area of the second heat exchange section 16b. Therefore, also in the present embodiment, the heat exchange area of the second heat exchange unit 16b is set so that the second heat exchange unit 16b is filled with the high-pressure liquid-phase refrigerant in the second cooling mode. .
　その他の構成および作動は、第１実施形態と同様である。従って、本実施形態の冷凍サイクル装置１０においても、第１実施形態と同様の効果を得ることができる。すなわち、本実施形態の冷凍サイクル装置１０においても、室内蒸発器１８における冷却能力を充分に向上させることができる。 Other configurations and operations are the same as those of the first embodiment. Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, the same effect as that of the first embodiment can be obtained. That is, also in the refrigeration cycle device 10 of the present embodiment, the cooling capacity of the indoor evaporator 18 can be sufficiently improved.
　（他の実施形態）
　本開示は上述の実施形態に限定されることなく、本開示の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。 (Other embodiments)
The present disclosure is not limited to the above-described embodiments, and can be variously modified as follows without departing from the spirit of the present disclosure.
　上述の実施形態では、本開示に係る冷凍サイクル装置１０を、車両用空調装置１適用した例を説明したが、冷凍サイクル装置１０の適用はこれに限定されない。車両用に限定されることなく、定置型の空調装置、冷蔵装置等に適用してもよい。 In the above-described embodiment, the example in which the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1 has been described, but the application of the refrigeration cycle device 10 is not limited thereto. The present invention is not limited to vehicles, and may be applied to stationary air conditioners, refrigeration devices, and the like.
　冷凍サイクル装置の各構成は、上述の実施形態に開示されたものに限定されない。 各 Each configuration of the refrigeration cycle device is not limited to the configuration disclosed in the above embodiment.
　例えば、上述の実施形態では、圧縮機１１として、電動圧縮機を採用した例を説明したが、内燃機関を有する車両に適用する場合等には、エンジン駆動式の圧縮機を採用してもよい。さらに、エンジン駆動式の圧縮機としては、吐出容量を変化させることによって冷媒吐出能力を調整可能に構成された可変容量型圧縮機を採用してもよい。 For example, in the above-described embodiment, an example in which an electric compressor is employed as the compressor 11 has been described. However, when the invention is applied to a vehicle having an internal combustion engine, an engine-driven compressor may be employed. . Further, as the engine-driven compressor, a variable displacement compressor configured to adjust the refrigerant discharge capacity by changing the discharge capacity may be adopted.
　また、上述の実施形態では、暖房用膨張弁１４ａおよび冷房用膨張弁１４ｂとして、全閉機能を有するものを採用した例を説明したが、全閉機能を有しない電気式膨張弁と開閉弁とを直列的に接続したものを採用してもよい。 Further, in the above-described embodiment, an example in which the heating expansion valve 14a and the cooling expansion valve 14b have a fully-closed function has been described. However, the electric expansion valve and the on-off valve that do not have the fully-closed function are described. May be employed in series.
　また、上述の実施形態では、冷媒としてＲ１２３４ｙｆを採用した例を説明したが、冷媒はこれに限定されない。例えば、Ｒ１３４ａ、Ｒ６００ａ、Ｒ４１０Ａ、Ｒ４０４Ａ、Ｒ３２、Ｒ４０７Ｃ、等を採用してもよい。または、これらの冷媒のうち複数種を混合させた混合冷媒等を採用してもよい。 In the above-described embodiment, the example in which R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Alternatively, a mixed refrigerant obtained by mixing a plurality of types of these refrigerants may be employed.
　また、上述の実施形態では、複数の運転モードに切り替え可能な冷凍サイクル装置１０について説明したが、冷凍サイクル装置１０の運転モードの切り替えはこれに限定されない。少なくとも、第１冷房モードと第２冷房モードとの切り替えを実行可能であれば、室内蒸発器１８にて発揮される冷却能力を充分に向上させることができる。 In the above-described embodiment, the refrigeration cycle apparatus 10 that can be switched to a plurality of operation modes has been described. However, the switching of the operation mode of the refrigeration cycle apparatus 10 is not limited to this. At least, if the switching between the first cooling mode and the second cooling mode can be executed, the cooling capacity exhibited by the indoor evaporator 18 can be sufficiently improved.
　上述の実施形態では、水－冷媒熱交換器１２および高温側熱媒体回路４０の各構成機器によって構成された加熱部を採用したが、加熱部はこれに限定されない。例えば、圧縮機１１から吐出された高圧冷媒と送風空気とを直接的に熱交換させる室内凝縮器を採用し、室内凝縮器をヒータコア４２と同様に空調ケース３１内に配置してもよい。 In the above-described embodiment, the heating unit constituted by the components of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is employed, but the heating unit is not limited to this. For example, an indoor condenser that directly exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air may be adopted, and the indoor condenser may be arranged in the air-conditioning case 31 like the heater core 42.
　上述の実施形態では、蒸発器温度Ｔｅｆｉｎが目標蒸発器温度ＴＥＯになっており、かつ、圧縮機１１の回転数Ｎｃが最大回転数ＮｃＭａｘになっている際に、冷却能力不足条件が成立したと判定しているが、冷却能力不足条件はこれに限定されない。例えば、冷房モード時に、空調風温度センサ６９によって検出された送風空気温度ＴＡＶが目標吹出温度ＴＡＯより高くなっている際に、冷却能力不足条件が成立したと判定してもよい。 In the above-described embodiment, when the evaporator temperature Tefin has reached the target evaporator temperature TEO and the rotation speed Nc of the compressor 11 has reached the maximum rotation speed NcMax, the cooling capacity shortage condition has been satisfied. Although it is determined, the cooling capacity shortage condition is not limited to this. For example, in the cooling mode, when the blast air temperature TAV detected by the conditioned air temperature sensor 69 is higher than the target outlet temperature TAO, it may be determined that the cooling capacity shortage condition has been satisfied.
　本開示は、実施例に準拠して記述されたが、本開示は当該実施例や構造に限定されるものではないと理解される。本開示は、様々な変形例や均等範囲内の変形をも包含する。加えて、様々な組み合わせや形態、さらには、それらに一要素のみ、それ以上、あるいはそれ以下、を含む他の組み合わせや形態をも、本開示の範疇や思想範囲に入るものである。 Although the present disclosure has been described based on the embodiments, it is understood that the present disclosure is not limited to the embodiments and the structure. The present disclosure also encompasses various modifications and variations within an equivalent range. In addition, various combinations and forms, and other combinations and forms including only one element, more or less, are also included in the scope and spirit of the present disclosure.

Claims (6)

  1. 　冷媒を圧縮して吐出する圧縮機（１１）と、
    　前記圧縮機から吐出された吐出冷媒と外気とを熱交換させる室外熱交換器（１６）と、
    　前記室外熱交換器から流出した冷媒を減圧させる減圧部（１４ｂ）と、
    　前記減圧部から流出した冷媒を蒸発させて冷却対象流体を冷却する蒸発器（１８）と、
    　前記蒸発器から流出した冷媒の気液を分離して、分離された低圧液相冷媒を貯えることが可能な低圧側貯液部（２１）と、を備え、
    　前記室外熱交換器（１６）は、前記吐出冷媒と前記外気とを熱交換させる第１熱交換部（１６ａ）、前記第１熱交換部から流出した冷媒の気液を分離して、分離された高圧液相冷媒を貯えることが可能な高圧側貯液部（１６５）、および前記高圧側貯液部から流出した冷媒と前記外気とを熱交換させる第２熱交換部（１６ｂ）を有し、
    　前記蒸発器にて前記冷却対象流体を冷却する第１冷却モード時には、前記低圧側貯液部内に前記低圧液相冷媒が貯えられるように前記減圧部の絞り開度が制御され、
    　前記蒸発器にて前記第１冷却モードよりも高い冷却能力で前記冷却対象流体を冷却する第２冷却モード時には、前記高圧側貯液部内に前記高圧液相冷媒が貯えられるように前記減圧部の絞り開度が制御される冷凍サイクル装置。     A compressor (11) for compressing and discharging the refrigerant;
    An outdoor heat exchanger (16) for exchanging heat between the refrigerant discharged from the compressor and outside air;
    A decompression unit (14b) for decompressing the refrigerant flowing out of the outdoor heat exchanger;
    An evaporator (18) for evaporating the refrigerant flowing out of the decompression unit and cooling a cooling target fluid;
    A low-pressure side liquid storage part (21) capable of separating gas-liquid of the refrigerant flowing out of the evaporator and storing the separated low-pressure liquid-phase refrigerant;
    The outdoor heat exchanger (16) is a first heat exchange section (16a) for exchanging heat between the discharged refrigerant and the outside air, and separates gas and liquid of the refrigerant flowing out of the first heat exchange section. And a second heat exchange section (16b) for exchanging heat between the refrigerant flowing out of the high pressure side liquid storage section and the outside air. ,
    In the first cooling mode in which the cooling target fluid is cooled by the evaporator, the throttle opening of the pressure reducing unit is controlled such that the low-pressure liquid-phase refrigerant is stored in the low-pressure side liquid storage unit,
    In the second cooling mode in which the evaporator cools the cooling target fluid with a higher cooling capacity than the first cooling mode, the evacuation unit is configured to store the high-pressure liquid refrigerant in the high-pressure side liquid storage unit. A refrigeration cycle device whose throttle opening is controlled.
  2. 　前記減圧部の作動を制御する減圧制御部（６０ｂ）と、
    　前記減圧部へ流入する冷媒の目標過冷却度（ＳＣＯ１、ＳＣＯ２）を決定する目標過冷却度決定部（Ｓ３０、Ｓ１００）と、を備え、
    　前記減圧制御部は、前記減圧部へ流入する冷媒の過冷却度（ＳＣ）が、前記目標過冷却度に近づくように、前記減圧部の作動を制御するものであり、
    　前記目標過冷却度決定部は、予め定めた冷却能力不足条件が成立した際に、前記目標過冷却度を上昇させるものである請求項１に記載の冷凍サイクル装置。     A pressure reduction control unit (60b) for controlling the operation of the pressure reduction unit;
    A target supercooling degree determining unit (S30, S100) for determining a target supercooling degree (SCO1, SCO2) of the refrigerant flowing into the pressure reducing unit.
    The pressure reduction control unit controls the operation of the pressure reduction unit such that the degree of supercooling (SC) of the refrigerant flowing into the pressure reduction unit approaches the target degree of supercooling,
    The refrigeration cycle apparatus according to claim 1, wherein the target subcooling degree determination unit increases the target subcooling degree when a predetermined cooling capacity shortage condition is satisfied.
  3. 　前記蒸発器の出口側冷媒の目標過熱度（ＳＨＯ２）を決定する目標過熱度決定部（Ｓ１２０）を備え、
    　前記減圧制御部は、前記第２冷却モードへ切り替えられた際に、前記蒸発器の出口側冷媒の過熱度（ＳＨ）が、前記目標過熱度（ＳＨＯ２）に近づくように、前記減圧部の作動を制御する請求項２に記載の冷凍サイクル装置。     A target superheat determining unit (S120) for determining a target superheat (SHO2) of the refrigerant on the outlet side of the evaporator;
    The pressure reduction control unit operates the pressure reduction unit such that the superheat degree (SH) of the refrigerant on the outlet side of the evaporator approaches the target superheat degree (SHO2) when the mode is switched to the second cooling mode. The refrigeration cycle apparatus according to claim 2, which controls the following.
  4. 　前記第２熱交換部の熱交換面積は、前記第２冷却モード時に、前記第２熱交換部が前記高圧液相冷媒で満たされるように設定されている請求項１ないし３のいずれか１つに記載の冷凍サイクル装置。 The heat exchange area of the second heat exchange unit is set such that the second heat exchange unit is filled with the high-pressure liquid-phase refrigerant in the second cooling mode. A refrigeration cycle apparatus according to item 1.
  5. 　前記第１熱交換部の熱交換面積と前記第２熱交換部の熱交換面積が同等である請求項４に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 4, wherein the heat exchange area of the first heat exchange section is equal to the heat exchange area of the second heat exchange section.
  6. 　前記第１熱交換部の冷媒出口は、前記第１熱交換部の最上方側に配置されており、
    　前記高圧側貯液部の冷媒入口は、前記高圧側貯液部の最下方側に配置されている請求項１ないし５のいずれか１つに記載の冷凍サイクル装置。     The refrigerant outlet of the first heat exchange unit is disposed on the uppermost side of the first heat exchange unit,
    The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein a refrigerant inlet of the high-pressure side liquid storage section is disposed at a lowermost side of the high-pressure side liquid storage section.
PCT/JP2019/036255 2018-10-05 2019-09-16 Refrigeration cycle device WO2020071097A1 (en)

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JP7331806B2 (en) * 2020-08-20 2023-08-23 株式会社デンソー refrigeration cycle equipment
WO2024034320A1 (en) * 2022-08-10 2024-02-15 株式会社デンソー Refrigeration cycle device

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