WO2022091816A1 - Appareil à cycle de réfrigération - Google Patents

Appareil à cycle de réfrigération Download PDF

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Publication number
WO2022091816A1
WO2022091816A1 PCT/JP2021/038243 JP2021038243W WO2022091816A1 WO 2022091816 A1 WO2022091816 A1 WO 2022091816A1 JP 2021038243 W JP2021038243 W JP 2021038243W WO 2022091816 A1 WO2022091816 A1 WO 2022091816A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
valve
flow path
compressor
Prior art date
Application number
PCT/JP2021/038243
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English (en)
Japanese (ja)
Inventor
陽平 長野
陽一郎 河本
公和 小原
浩 茶木田
Original Assignee
株式会社デンソー
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Publication of WO2022091816A1 publication Critical patent/WO2022091816A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/124—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston servo actuated
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This disclosure relates to a steam compression type refrigeration cycle device.
  • valve device of a refrigeration cycle device a valve body, a control chamber into which a driving fluid for driving the valve body is introduced, and a pressure control unit for adjusting the pressure in the control chamber are known (for example,). See Patent Document 1).
  • the pressure control unit of the valve device disclosed in Patent Document 1 is connected to each of the refrigerant inlet and the refrigerant outlet of the valve device via the capillary tube, and the pressure in the control chamber is controlled by using the refrigerant introduced through the capillary tube. It is configured to control.
  • the steam compression type refrigeration cycle device is It is equipped with a valve device that performs at least one of decompression and flow rate adjustment of the refrigerant flowing in the cycle.
  • the valve device A valve chamber that distributes the refrigerant that has flowed in from the inflow port to the outflow port, A valve body that is driven inside the valve chamber and changes the flow rate of the refrigerant flowing from the inlet to the outlet.
  • a control room in which the driving fluid for driving the valve body is introduced A pressure control unit that controls the pressure in the control room, A high-pressure connection flow path that communicates with the high-pressure point where the high-pressure refrigerant flows in both the heat utilization mode and the cold heat utilization mode in the cycle.
  • the pressure control unit is connected to the high-pressure connection flow path and the low-pressure connection flow path, and controls the pressure in the control room by adjusting the introduction ratio between the introduction amount of the high-pressure refrigerant and the introduction amount of the low-pressure refrigerant in the control room.
  • the control chamber can be controlled to a desired pressure by the pressure control unit. can. Therefore, the operation required for the valve device can be realized in either the thermal utilization mode or the cold utilization mode.
  • FIG. 8 shows a cross section of IX-IX of FIG. 8, which is a cross-sectional view showing a non-energized state of the microvalve. It is sectional drawing which shows the XX cross section of FIG. FIG. 8 shows a cross section of IX-IX of FIG. 8, which is a cross-sectional view showing a state of energization of the microvalve. It is sectional drawing which shows the cross section of XII-XII of FIG. It is explanatory drawing for demonstrating the adjustment method of a control pressure. It is a schematic perspective view of each expansion valve which concerns on 2nd Embodiment.
  • FIG. 25 is a cross-sectional view taken along the line XXVI-XXVI of FIG.
  • FIG. 26 is a cross-sectional view taken along the line XXVII-XXVII of FIG.
  • the refrigerating cycle device 30 includes a compressor 31, a condenser 32, a first expansion valve 33, an outdoor heat exchanger 34, a second expansion valve 35, a cooling evaporator 36, and a bypass valve 37. ing. Each of these constituent devices is connected to each other by a refrigerant pipe. Further, the refrigeration cycle device 30 includes a control device 300 that controls the operation of each component device.
  • the refrigeration cycle device 30 uses an HFC-based refrigerant (specifically, R134a) as the refrigerant.
  • Refrigerating machine oil for lubricating the compressor 31 is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in a cycle together with the refrigerant.
  • an HFO-based refrigerant for example, R1234yf
  • a natural refrigerant for example, R744
  • the compressor 31 sucks in the refrigerant in the refrigerating cycle device 30, compresses it, and discharges it.
  • the compressor 31 is composed of an electric compressor in which a fixed capacity type compression mechanism having a fixed discharge capacity is driven by an electric motor.
  • the compressor 31 is arranged inside the hood of the vehicle. The operation (for example, rotation speed) of the electric motor constituting the compressor 31 is controlled by a control signal output from the control device 300 described later.
  • the refrigerant inlet side of the condenser 32 is connected to the refrigerant discharge side of the compressor 31.
  • the condenser 32 is a heat exchanger that dissipates heat from the refrigerant discharged from the compressor 31.
  • the condenser 32 includes a refrigerant flow path portion 321 through which the refrigerant flows and a heat medium flow path portion 322 through which the heat medium of the heater circuit HC flows, and heats the refrigerant and the heat medium flowing through the heater circuit HC. It constitutes a heat exchanger for heating that is exchanged to heat a heat medium.
  • the condenser 32 constitutes a radiator that dissipates heat from the refrigerant discharged from the compressor 31 in the thermal utilization mode.
  • the heater circuit HC is a circuit for being used as a heat source for heating the blown air that blows the refrigerant discharged from the compressor 31 into the vehicle interior, warming up the battery, and the like.
  • the heater circuit HC is provided with a heater core for radiating the heat medium to the air blown into the vehicle interior, a radiator for radiating the heat medium to the battery, and the like.
  • the heater core is arranged inside the air conditioning case C together with the cooling evaporator 36 described later.
  • the first expansion valve 33 is connected to the refrigerant outlet side of the condenser 32.
  • the first expansion valve 33 is a first decompression unit that depressurizes the refrigerant that has passed through the condenser 32.
  • the first expansion valve 33 is a heating expansion valve that reduces the pressure of the refrigerant that has passed through the condenser 32 during heating and dehumidifying heating of the vehicle interior.
  • the first expansion valve 33 has a structure in which the depressurizing function of the refrigerant is not exerted in the fully open state where the throttle opening is maximized.
  • the first expansion valve 33 constitutes a part of the valve device of the present disclosure. The details of the first expansion valve 33 will be described later.
  • the refrigerant inlet side of the outdoor heat exchanger 34 is connected to the refrigerant outlet side of the first expansion valve 33.
  • the outdoor heat exchanger 34 is a heat exchanger that exchanges heat with the outside air blown from the outdoor fan 341 for the refrigerant that has passed through the first expansion valve 33.
  • the outdoor heat exchanger 34 functions as a radiator that dissipates heat from the outside air during cooling, and functions as a heat absorber that absorbs heat from the outside air during heating.
  • the outdoor fan 341 is a blower that generates an air flow that passes through the outdoor heat exchanger 34.
  • a second expansion valve 35 is connected to the refrigerant outlet side of the outdoor heat exchanger 34.
  • the second expansion valve 35 is a second pressure reducing unit that reduces the pressure of the refrigerant that has passed through the outdoor heat exchanger 34.
  • the second expansion valve 35 is a cooling expansion valve that reduces the pressure of the refrigerant that has passed through the outdoor heat exchanger 34 during cooling and dehumidifying and heating of the vehicle interior.
  • the second expansion valve 35 has a structure in which the flow of the refrigerant is blocked in a fully closed state where the throttle opening is minimized.
  • the second expansion valve 35 constitutes a part of the valve device of the present disclosure as well as the first expansion valve 33. The details of the second expansion valve 35 will be described later.
  • the refrigerant inlet side of the cooling evaporator 36 is connected to the refrigerant outlet side of the second expansion valve 35.
  • the cooling evaporator 36 is an evaporator that evaporates the refrigerant that has passed through the second expansion valve 35.
  • the cooling evaporator 36 is arranged inside the air conditioning case C and exchanges heat between the refrigerant and the air blown from the indoor fan 361 to evaporate the refrigerant.
  • the cooling evaporator 36 is an air cooler that cools the air blown from the indoor fan 361 by exchanging heat with the refrigerant.
  • the cooling evaporator 36 is arranged in the air conditioning case C on the upstream side of the air flow with respect to the heater core.
  • the indoor fan 361 is a blower that blows air cooled by the cooling evaporator 36 into the vehicle interior.
  • a bypass flow path 38 that bypasses the second expansion valve 35 and the cooling evaporator 36 and leads to the refrigerant suction side of the compressor 31 is connected to the refrigerant outlet side of the outdoor heat exchanger 34.
  • the bypass flow path 38 bypasses the second expansion valve 35 and the cooling evaporator 36 and guides the refrigerant that has passed through the outdoor heat exchanger 34 during heating to the refrigerant suction side of the compressor 31.
  • One end of the bypass flow path 38 is connected to a refrigerant branch portion 381 provided in the refrigerant flow path from the refrigerant outlet of the outdoor heat exchanger 34 to the refrigerant inlet of the second expansion valve 35.
  • the other end of the bypass flow path 38 is connected to a refrigerant merging portion 382 provided in the refrigerant flow path from the refrigerant outlet of the cooling evaporator 36 to the refrigerant suction port of the compressor 31.
  • a bypass valve 37 is provided in the bypass flow path 38.
  • the bypass valve 37 is an opening / closing portion that opens / closes the bypass flow path 38.
  • the bypass valve 37 adjusts the flow rate of the refrigerant flowing through the bypass flow path 38 by opening and closing the bypass flow path 38.
  • the bypass valve 37 is composed of a solenoid valve that drives the valve body by the electromagnetic attraction force of the solenoid.
  • the opening / closing operation of the bypass valve 37 is controlled by a control signal output from the control device 300 described later.
  • the bypass valve 37 may have a structure in which the valve body is driven by a stepping motor or the like.
  • An accumulator ACC is provided on the refrigerant suction side of the compressor 31. Specifically, the accumulator ACC is provided between the refrigerant merging portion 382 and the compressor 31. The accumulator ACC separates the gas and liquid of the refrigerant before being sucked into the compressor 31 and causes the gas-rich refrigerant to flow out to the refrigerant suction side of the compressor 31.
  • the refrigerant flow path from the refrigerant discharge side of the compressor 31 to the condenser 32 constitutes a discharge refrigerant flow path 311 through which a gas single-phase refrigerant flows.
  • the refrigerating cycle device 30 constitutes an intake refrigerant flow path 312 through which a gas-rich refrigerant flows in the refrigerant flow path from the accumulator ACC to the refrigerant suction side of the compressor 31.
  • the control device 300 constituting the electronic control unit of the refrigeration cycle device 30 will be described with reference to FIG.
  • the control device 300 includes a microcomputer including a memory such as a processor, a ROM, and a RAM, and peripheral circuits thereof.
  • the memory of the control device 300 is composed of a non-transitional substantive storage medium.
  • the air conditioning sensor group 301 and an operation panel 302 are connected to the input side of the control device 300.
  • the air conditioning sensor group 301 is composed of a plurality of types of sensors used for controlling cooling processing and the like.
  • the air conditioning sensor group 301 includes, for example, a temperature sensor (such as an evaporator temperature sensor) that detects the refrigerant temperature on the low pressure side of the cycle, a high pressure sensor that detects the refrigerant pressure on the high pressure side of the cycle, and a temperature that detects the temperature of the high pressure refrigerant. Includes sensor.
  • the various operation switches of the operation panel 302 include an auto switch, an operation mode changeover switch, an air volume setting switch, a temperature setting switch, a blowout mode changeover switch, and the like.
  • the control device 300 performs various arithmetic processes based on various information acquired from the air conditioning sensor group 301 and the operation panel 302, and a control program stored in the memory, and controls the operation of each component device connected to the output side. do.
  • a compressor 31, a first expansion valve 33, an outdoor fan 341, a second expansion valve 35, an indoor fan 361, and a bypass valve 37 are connected to the output side of the control device 300.
  • the control device 300 determines the refrigerant discharge performance (for example, refrigerant pressure) by the compressor 31, the throttle opening of the expansion valves 33 and 35, the ventilation performance of the fans 341 and 361, and the open / closed state of the bypass valve 37 according to the situation. Can be changed. That is, the refrigerating cycle device 30 desires the air supplied to the vehicle interior by the control device 300 controlling the operation of the compressor 31, the expansion valves 33, 35, the fans 341, 361, and the bypass valve 37, respectively. Can be adjusted to the temperature of.
  • the refrigeration cycle device 30 appropriately switches the operation mode of the refrigeration cycle device 30 by receiving inputs from the air conditioning sensor group 301 and the operation panel 302. Specifically, the control device 300 controls the expansion valves 33, 35, the bypass valve 37, and the like to change the flow method of the refrigerant in the refrigeration cycle device 30, thereby switching the operation mode of the refrigeration cycle device 30.
  • the refrigeration cycle device 30 can be set to three operation modes such as indoor cooling, indoor heating, and dehumidifying heating.
  • the indoor cooling is an operation mode in which air cooled to a desired temperature by the cooling evaporator 36 is blown into the vehicle interior.
  • This operation mode is a cold heat utilization mode using a low pressure refrigerant whose pressure is lower than the reference pressure difference by a reference pressure difference or more than the high pressure refrigerant in the cycle.
  • the reference pressure difference is greater than or equal to the required pressure required to drive the valve bodies of the expansion valves 33 and 35.
  • the indoor cooling is executed by the refrigerating cycle device 30, for example, when the operation mode is set to the cooling mode by the changeover switch. During this indoor cooling, the flow of the heat medium in the heater circuit HC is stopped.
  • the control device 300 appropriately determines the operating state of various devices during indoor cooling by using the detection signal of the air conditioning sensor group 301 and the operation signal of the operation panel 302. For example, as shown in FIG. 3, the control device 300 controls the expansion valves 33 and 35 so that the first expansion valve 33 is in the fully open state and the second expansion valve 35 is in the throttle state. Further, the control device 300 controls the bypass valve 37 to be in the closed state. The control device 300 appropriately determines control signals for other devices such as the compressor 31, fans 341, and 361 by using the detection signals of the air conditioning sensor group 301 and the operation signals of the operation panel 302.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the condenser 32 during indoor cooling. Since the heat medium does not flow through the heater circuit HC during indoor cooling, the refrigerant that has flowed into the condenser 32 flows into the first expansion valve 33 with almost no heat dissipation.
  • the refrigerant flowing into the first expansion valve 33 flows into the outdoor heat exchanger 34 with almost no decompression.
  • the refrigerant flowing into the outdoor heat exchanger 34 dissipates heat to the outside air and condenses.
  • the refrigerant that has passed through the outdoor heat exchanger 34 flows into the second expansion valve 35 and is depressurized by the second expansion valve 35 until the desired pressure is reached. Since the bypass valve 37 is closed during indoor cooling, the refrigerant does not flow into the bypass flow path 38, and the entire amount of the refrigerant is depressurized by the second expansion valve 35.
  • the refrigerant decompressed by the second expansion valve 35 flows into the cooling evaporator 36.
  • the refrigerant flowing into the cooling evaporator 36 absorbs heat from the air blown from the indoor fan 361 and evaporates. Air cooled to a desired temperature by the cooling evaporator 36 is blown into the vehicle interior.
  • the refrigerant that has passed through the cooling evaporator 36 flows into the accumulator ACC to separate the gas and liquid, and then the separated gas-rich refrigerant is sucked into the compressor 31.
  • the refrigerant sucked into the compressor 31 is compressed by the compressor 31 until it becomes a high-pressure refrigerant again.
  • the air cooled by the cooling evaporator 36 is blown into the vehicle interior to realize indoor cooling. Since the first expansion valve 33 is fully open during indoor cooling, there is almost no pressure difference between the front and rear of the first expansion valve 33.
  • the room heating is an operation mode in which air heated to a desired temperature by the heater core is blown into the vehicle interior.
  • This operation mode is a thermal utilization mode that utilizes a high-pressure refrigerant in the cycle.
  • the room heating is executed by the refrigeration cycle device 30, for example, when the operation mode is set to the heating mode by the changeover switch.
  • the heater circuit HC is set in the path through which the heat medium flows with respect to the heater core.
  • the control device 300 appropriately determines the operating state of various devices during indoor heating by using the detection signal of the air conditioning sensor group 301 and the operation signal of the operation panel 302. For example, as shown in FIG. 3, the control device 300 controls the expansion valves 33 and 35 so that the first expansion valve 33 is in the throttled state and the second expansion valve 35 is in the fully closed state. Further, the control device 300 controls the bypass valve 37 in the open state. The control device 300 appropriately determines control signals for other devices such as the compressor 31, fans 341, and 361 by using the detection signals of the air conditioning sensor group 301 and the operation signals of the operation panel 302.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the condenser 32 during indoor heating.
  • the heat medium flowing through the heater circuit HC flows to the heater core, so that the refrigerant flowing into the condenser 32 is dissipated to the air blown into the vehicle interior through the heater core.
  • air heated to a desired temperature by the heater core is blown out into the vehicle interior.
  • the refrigerant that has passed through the condenser 32 flows into the first expansion valve 33 and is depressurized by the first expansion valve 33 until the desired pressure is reached.
  • the refrigerant decompressed by the first expansion valve 33 flows into the outdoor heat exchanger 34.
  • the refrigerant flowing into the outdoor heat exchanger 34 absorbs heat from the air blown from the outdoor fan 341 and evaporates. Since the bypass valve 37 is in the open state during indoor heating, the refrigerant that has passed through the outdoor heat exchanger 34 flows into the accumulator ACC via the bypass flow path 38. The refrigerant flowing into the accumulator ACC is separated from the gas and liquid, and then the separated gas-rich refrigerant is sucked into the compressor 31. The refrigerant sucked into the compressor 31 is compressed by the compressor 31 until it becomes a high-pressure refrigerant again. Since the second expansion valve 35 is fully closed during indoor heating, the refrigerant does not flow into the cooling evaporator 36, and the entire amount of the refrigerant is sucked into the compressor 31 via the bypass flow path 38. Will be done.
  • the air heated by the heater core is blown into the vehicle interior to realize indoor heating.
  • the second expansion valve 35 is in a fully closed state, and there is almost no pressure difference between the front and rear of the second expansion valve 35.
  • the dehumidifying heating is an operation mode in which the air is cooled to a temperature lower than the dew point temperature by the cooling evaporator 36, then the temperature is raised to a desired temperature by the heater core, and the air is blown into the vehicle interior. Since this operation mode uses each of the high-pressure refrigerant and the low-pressure refrigerant in the cycle, it corresponds to each of the heat utilization mode and the cold heat utilization mode.
  • the dehumidifying and heating is executed by the refrigerating cycle device 30 when the operation mode is set to the dehumidifying and heating mode by, for example, the operation mode changeover switch. During this dehumidifying and heating, the heater circuit HC is set in the path through which the heat medium flows with respect to the heater core.
  • the control device 300 appropriately determines the operating state of various devices during dehumidifying and heating by using the detection signal of the air conditioning sensor group 301 and the operation signal of the operation panel 302. For example, as shown in FIG. 3, the control device 300 controls each of the first expansion valve 33 and the second expansion valve 35 in a throttled state. Further, the control device 300 controls the bypass valve 37 to be in the closed state. The control device 300 appropriately determines control signals for other devices such as the compressor 31, fans 341, and 361 by using the detection signals of the air conditioning sensor group 301 and the operation signals of the operation panel 302.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the condenser 32 during dehumidification and heating.
  • the heat medium flowing through the heater circuit HC flows to the heater core, so that the refrigerant flowing into the condenser 32 dissipates heat to the air blown into the vehicle interior through the heater core.
  • air heated to a desired temperature by the heater core is blown out into the vehicle interior.
  • the refrigerant that has passed through the condenser 32 flows into the first expansion valve 33 and is depressurized by the first expansion valve 33 until the desired pressure is reached.
  • the refrigerant decompressed by the first expansion valve 33 flows into the outdoor heat exchanger 34.
  • the refrigerant flowing into the outdoor heat exchanger 34 exchanges heat with the outside air.
  • the refrigerant flowing into the outdoor heat exchanger 34 absorbs heat from the outside air when the temperature of the refrigerant is lower than the outside air, and dissipates heat to the outside air when the temperature of the refrigerant is higher than the outside air.
  • the refrigerant that has passed through the outdoor heat exchanger 34 flows into the second expansion valve 35 and is depressurized by the second expansion valve 35 until the desired pressure is reached. Since the bypass valve 37 is closed during dehumidifying and heating, the refrigerant does not flow into the bypass flow path 38, and the entire amount of the refrigerant is depressurized by the second expansion valve 35.
  • the refrigerant decompressed by the second expansion valve 35 flows into the cooling evaporator 36.
  • the refrigerant flowing into the cooling evaporator 36 absorbs heat from the air blown from the indoor fan 361 and evaporates. As a result, the air blown from the indoor fan 361 is cooled by the cooling evaporator 36 and dehumidified.
  • the air dehumidified by the cooling evaporator 36 is heated to a desired temperature by the heater core and then blown out into the vehicle interior.
  • the refrigerant that has passed through the cooling evaporator 36 flows into the accumulator ACC to separate the gas and liquid, and then the separated gas-rich refrigerant is sucked into the compressor 31.
  • the refrigerant sucked into the compressor 31 is compressed by the compressor 31 until it becomes a high-pressure refrigerant again.
  • the air dehumidified by the cooling evaporator 36 is heated by the heater core and then blown out into the vehicle interior to realize dehumidifying and heating in the room.
  • the first expansion valve 33 is in the throttled state, but the pressure difference before and after the first expansion valve 33 tends to be smaller than that at the time of indoor heating.
  • the second expansion valve 35 is also in the throttled state, but the pressure difference before and after the second expansion valve 35 tends to be smaller than that during indoor cooling.
  • the refrigerating cycle device 30 has a high-pressure portion in which a high-pressure refrigerant always flows in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating in the cycle.
  • This high-pressure portion includes a high-pressure region HPA from the refrigerant discharge side of the compressor 31 to the refrigerant inlet side of the first expansion valve 33.
  • the refrigerating cycle device 30 has a low-pressure portion in which the low-pressure refrigerant always flows in any of the indoor cooling, indoor heating, and dehumidifying heating operation modes in the cycle.
  • This low-pressure portion includes a low-pressure region LPA from the refrigerant confluence portion 382 to the refrigerant suction side of the compressor 31.
  • the first expansion valve 33 and the second expansion valve 35 have different control modes, but have the same basic structure. Therefore, in FIG. 4, a reference code indicating a component of the first expansion valve 33 and a reference code indicating a component of the second expansion valve 35 are shown together.
  • the first two digits of the code indicating a part of the components of the first expansion valve 33 are set to "33"
  • the second expansion valve 35 is used.
  • the first two digits of the code indicating a part of the constituent elements of the above are set to "35".
  • each expansion valve 33, 35 includes a body unit 330, 350, a main valve 332, 352, a pressure control unit 337, 357, and a circuit board 338, 358.
  • Each expansion valve 33, 35 changes the throttle opening of the internal flow paths 331, 351 formed inside the body portions 330, 350, and makes the pressure of the refrigerant passing through the expansion valves 33, 35 a desired pressure. It is to adjust to.
  • the body portions 330 and 350 form the outer shells of the expansion valves 33 and 35, respectively.
  • the body portions 330 and 350 are, for example, formed by drilling a metal block made of an aluminum alloy.
  • Internal flow paths 331, 351 through which the refrigerant flows, valve chambers 333, 353, control chambers 334, 354, and the like are formed in the body portions 330 and 350.
  • the internal flow paths 331 and 351 are connected to the inlet portions 330a and 350a and the outlet portions 330b and 350b that open on the side surfaces of the body portions 330 and 350.
  • Valve chambers 333 and 353 are formed in the middle of the internal flow paths 331 and 351.
  • the valve chamber 333, 353 houses a part of the main valves 332 and 352.
  • the valve chambers 333 and 353 communicate with the inlet portions 330a and 350a, which are the inlets of the refrigerant, and the outlet portions 330b, 350b, which are the outlets of the refrigerant.
  • the valve chambers 333 and 353 distribute the refrigerant flowing from the inlet portions 330a and 350a to the outlet portions 330b and 350b.
  • the valve chambers 333 and 353 are provided with throttle portions 333a and 353a in which the flow path through which the refrigerant flows is narrowed down.
  • the throttle portions 333a and 353a are flow paths that guide the refrigerant flowing into the valve chambers 333 and 353 from the inlet portions 330a and 350a to the outlet portions 330b and 350b while decompressing and expanding.
  • Valve seats 333b and 353b are formed on the refrigerant inlet side of the throttle portions 333a and 353a so that the valve bodies 332a and 352a of the main valves 332 and 352 come into contact with each other.
  • the flow path through which the refrigerant flows before passing through the throttle portions 333a and 353a in the internal flow paths 331 and 351 constitutes the inlet flow paths 331a and 351a. Further, the flow paths through which the refrigerant flowing out from the throttle portions 333a and 353a in the internal flow paths 331 and 351 flow form the outlet flow paths 331b and 351b.
  • the main valves 332 and 352 have valve bodies 332a and 352a, support portions 332b and 352b, first springs 332c and 352c, second springs 332d and 352d, adjusting screws 332e and 352e, operating rods 332f and 352f, caps 332i and 352i. Have.
  • the valve bodies 332a and 352a are driven inside the valve chambers 333 and 353, and change the flow rate of the refrigerant flowing from the inlet portions 330a and 350a to the outlet portions 330b and 350b. That is, the valve bodies 332a and 352a are displaced along the axial center CL of the main valves 332 and 352 to adjust the passage area of the throttle portions 333a and 353a.
  • the direction extending along the axial center CL is referred to as the valve axial direction DRax.
  • the main valves 332 and 352 are arranged in a posture in which the valve axial DRax coincides with the vertical DRg.
  • the valve bodies 332a and 352a are valve portions that are displaced in the valve axis direction DRax in the main valves 332 and 352.
  • the valve bodies 332a and 352a are composed of spherical valve bodies.
  • the expansion valves 33 and 35 are poppet type in which the valve bodies 332a and 352a are displaced in the direction in which they intersect with the valve seats 333b and 353b (for example, in the orthogonal direction) to change the throttle opening of the internal flow paths 331 and 351. It has a valve structure of.
  • the valve bodies 332a and 352a are arranged in the valve chamber 333, 353 together with the support portions 332b and 352b and the first springs 332c and 352c.
  • the support portions 332b and 352b are fixed to the other side of the valve bodies 332a and 352a in the axial direction.
  • the first springs 332c and 352c are urging members that urge the valve bodies 332a and 352a in the valve closing direction via the support portions 332b and 352b.
  • the load that the first springs 332c and 352c urge on the valve bodies 332a and 352a can be adjusted by the adjusting screws 332e and 352e provided on the body portions 330 and 350.
  • the adjusting screws 332e and 352e are screwed into screw holes opened in the portions of the body portions 330 and 350 facing the first springs 332c and 352c.
  • the load of the first springs 332c and 352c urging the valve bodies 332a and 352a can be adjusted. ..
  • actuating rods 332f and 352f are arranged on one side of the DRax in the valve axis direction.
  • the operating rods 332f and 352f are metal rods having a substantially cylindrical shape.
  • the actuating rods 332f and 352f are arranged inside the throttle portions 333a and 353a in a posture extending along the valve axis direction DRax.
  • stoppers 332g and 352g are fixed to one side of the DRax in the valve axis direction.
  • the stoppers 332g and 352g limit the axial displacement of the working rods 332f and 352f.
  • a partition portion 332h or 352h is provided at one end of the actuating rods 332f and 352f on one side in the valve axis direction DRax.
  • the partition portions 332h and 352h partition the internal space of the body portions 330 and 350 on one side of the throttle portion 333a and 353a in the valve axial direction to the control chamber 334 and 354 and the low pressure space 335 and 355. ..
  • the refrigerant pressure-adjusted by the pressure control unit 337 and 357 is introduced into the control chamber 334 and 354 as a driving fluid that presses the valve bodies 332a and 352a toward the valve opening side or the valve closing side. That is, the control chambers 334 and 354 form a space in which the driving fluid for driving the valve bodies 332a and 352a is introduced.
  • the partition portions 332h and 352h receive the pressure of the driving fluid introduced into the control chambers 334 and 354.
  • Second springs 332d and 352d are arranged in the control chambers 334 and 354.
  • the second springs 332d and 352d are urging members that urge the valve bodies 332a and 352a in the valve opening direction via the partition portions 332h and 352h, the stoppers 332g and 352g, and the actuating rods 332f and 352f.
  • the caps 332i and 352i are closing members that close the opening on the upper side of the control chamber 334 and 354.
  • the second springs 332d and 352d are arranged between the bottom surfaces of the caps 332i and 352i and the partition portions 332h and 352h.
  • first recesses 330c and 350c, second recesses 330d and 350d, and third recesses 330e and 350e are formed on the side portions of the control chambers 334 and 354.
  • the first recesses 330c, 350c, the second recesses 330d, 350d, and the third recesses 330e, 350e are recesses into which the first protrusion Y21, the second protrusion Y22, and the third protrusion Y23 of the valve module Y0, which will be described later, are fitted. Is.
  • the first recesses 330c, 350c, the second recesses 330d, 350d, the third recesses 330e, 350e are in the order of the third recesses 330e, 350e, the first recess 330c, 350c, the second recess 330d, 350d from the upper side to the lower side. They are arranged so that they are lined up in a straight line.
  • first through holes 330f and 350f are formed to communicate the first recesses 330c and 350c with the control chambers 334 and 354.
  • second through holes 330g and 350g are formed so as to communicate the second recesses 330d and 350d with the external flow path.
  • third through holes 330h and 350h are formed to communicate the third recesses 330e and 350e with the external flow path.
  • the second through holes 330 g and 350 g are connected to the discharge refrigerant flow path 311 in the high pressure region HPA.
  • the second through holes 330 g and 350 g are connected to the discharged refrigerant flow path 311 via, for example, a capillary tube (not shown).
  • the second through holes 330 g and 350 g form a high-pressure connection flow path communicating with a high-pressure portion through which the high-pressure refrigerant flows in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating.
  • the third through holes 330h and 350h are connected to the suction refrigerant flow path 312 in the low pressure region LPA.
  • the third through holes 330h and 350h are connected to the intake refrigerant flow path 312 via, for example, a capillary tube (not shown).
  • the third through holes 330h and 350h form a low-pressure connection flow path that communicates with a low-pressure portion through which the low-pressure refrigerant flows in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating.
  • the flow path area (that is, the throttle opening) of the internal flow paths 331 and 351 changes depending on the positions of the valve bodies 332a and 352a.
  • the positions of the valve bodies 332a and 352a are determined by the force acting on the valve bodies 332a and 352a.
  • the positions of the valve bodies 332a and 352a are the load Fm due to the pressure of the driving fluid in the control chamber 334 and 354, and the loads Fs1, Fs2 and valve chamber 333,353 from the springs 332c, 352c, 332d and 352d, respectively. It is determined by the load Fc due to the refrigerant pressure in.
  • the pressure of the driving fluid in the control chamber 334 and 354 may be referred to as a control pressure Pm.
  • Each expansion valve 33, 35 has a pressure difference between the pressure of the high pressure refrigerant (that is, the high pressure pressure Ph) and the control pressure Pm when the control pressure Pm becomes the pressure equivalent to the pressure of the low pressure refrigerant (that is, the low pressure pressure Pl). Is the maximum.
  • the valve bodies 332a and 352a are displaced to the positions where the throttle opening is minimized.
  • the expansion valves 33 and 35 have a smaller throttle opening of the internal flow paths 331 and 351 when the control pressure Pm is smaller, and a larger throttle opening when the control pressure Pm is larger. It has a structure.
  • the control pressure Pm of each of the expansion valves 33 and 35 of the present embodiment is adjusted by the pressure control unit 337 and 357.
  • the pressure control unit 337, 357 controls the pressure in the control chamber 334, 354. That is, the pressure control unit 337, 357 controls the pressure in the control chamber 334, 354 by adjusting the introduction ratio of the introduction amount of the high pressure refrigerant and the introduction amount of the low pressure refrigerant into the control chamber 334, 354.
  • the pressure difference between the front and rear of the expansion valves 33 and 35 may be almost eliminated depending on the operation mode. be.
  • the pressure control units 337 and 357 cannot control the control chambers 334 and 354 to a desired pressure, and the operations required for the expansion valves 33 and 35 cannot be realized.
  • the control chamber 334 cannot be controlled to a desired pressure by the pressure control unit 337, and the first expansion valve 33 may be switched to the throttled state. Can not.
  • the pressure control units 337 and 357 are connected to the second through holes 330g and 350g communicating with the high pressure points in the cycle and the third through holes 330h and 350h communicating with the low pressure points in the cycle. ing.
  • the pressure in the control chambers 334 and 354 can be appropriately controlled by the pressure control units 337 and 357 even when there is almost no pressure difference between the front and rear of the expansion valves 33 and 35.
  • the pressure control unit 337 and 357 are attached to the body units 330 and 350. Then, the drive fluid whose pressure is adjusted by the pressure control unit 337 and 357 is introduced into the control chamber 334 and 354 via the first through holes 330f and 350f.
  • the pressure control unit 337, 357 includes a micro valve Y1 that functions as a pilot valve for driving the main valves 332 and 352.
  • the pressure control unit 337, 357 is driven by a drive circuit mounted on the circuit board 338, 358.
  • the circuit board 338, 358 is fixed to the opposite side of the pressure control unit 337, 357, which is attached to the body portions 330, 350.
  • the circuit board 338 and 358 are connected to the connection terminals of the pressure control units 337 and 357.
  • the pressure control unit 337 and 357 are supplied with electric power via the circuit board 338 and 358.
  • the circuit boards 338 and 358 are connected to the electrical wirings Y6 and Y7 of the valve module Y0 via connection terminals.
  • the main valves 332 and 352 and the pressure control unit 337 and 357 are larger than the others. Therefore, if the main valves 332 and 352 and the pressure control units 337 and 357 are arranged side by side in the valve axial direction DRax, the expansion valves 33 and 35 and other parts arranged around the expansion valves 33 and 35 are likely to interfere with each other. Therefore, the layout of the expansion valves 33, 35 and other parts is restricted. This is not preferable because it causes a decrease in the degree of freedom in designing the expansion valves 33 and 35.
  • the first expansion valve 33 is arranged at different positions in the direction in which the valve body 332a and the pressure control unit 337 are orthogonal to the valve axial direction DRax.
  • the valve body 352a and the pressure control unit 357 are arranged at different positions in the direction orthogonal to the valve axial direction DRax.
  • the pressure control units 337 and 357 are arranged so as to be offset in the direction orthogonal to the valve axis direction DRax with respect to the main valves 332 and 352.
  • the valve axial DRax corresponds to the vertical DRg. Therefore, the main valves 332 and 352 and the pressure control units 337 and 357 are arranged at different positions in the horizontal direction.
  • At least a part of the pressure control unit 337 and 357 of the present embodiment is arranged so as to overlap the main valves 332 and 352 in the direction orthogonal to the valve axis direction DRax.
  • the pressure control unit 337, 357 has the second springs 332d, 352d and the cap 332i, which are arranged in the control chamber 334, 354 of the main valves 332 and 352 in the direction orthogonal to the valve axial direction DRax. It overlaps with a part of 352i.
  • the pressure control unit 337, 357 and the control chamber 334, 354 are arranged adjacent to each other. Therefore, the first through holes 330f and 350f that guide the driving fluid from the pressure control unit 337 and 357 to the control chamber 334 and 354 can be formed in a hole shape having no bent portion and a small length. By having such a hole shape, the first through holes 330f and 350f have a low pressure loss when the driving fluid flows.
  • the pressure control unit 337, 357 is attached to a portion of the body portions 330, 350 that is closer to the outlet portions 330b, 350b than the inlet portions 330a, 350a in the vertical DRg.
  • the circuit boards 338 and 358 are connected to the pressure control units 337 and 357 in a posture in which the plate surfaces 338a and 358a of the circuit boards 338 and 358 intersect with each other in the horizontal direction.
  • the circuit board 338 and 358 are connected to the pressure control unit 337 and 357 in a posture in which the plate surfaces 338a and 358a extend in parallel with the vertical DRg.
  • the circuit boards 338 and 358 are arranged so that the entire circuit boards 338 and 358 overlap the body portions 330 and 350 in the horizontal direction so as not to protrude above the upper ends of the body portions 330 and 350.
  • the pressure control unit 337 and 357 are configured by the valve module Y0.
  • the details of the valve module Y0 constituting the pressure control unit 337 and 357 will be described with reference to FIGS. 6 to 13.
  • valve module Y0 configuration As shown in FIG. 6, the valve module Y0 has a microvalve Y1, a valve casing Y2, a sealing member Y3, three O-rings Y4, Y5a, Y5b, two electrical wirings Y6, Y7, and a conversion plate Y8. ing.
  • the micro valve Y1 is a valve component having a fluid chamber Y19 for adjusting the pressure of the driving fluid (refrigerant in this example) to be introduced into the control chamber 334 and 354.
  • the microvalve Y1 has a plate shape, and the entire microvalve Y1 is composed of a semiconductor chip.
  • the length of the microvalve Y1 in the thickness direction is, for example, 2 mm
  • the length in the longitudinal direction orthogonal to the thickness direction is, for example, 10 mm
  • the length in the lateral direction orthogonal to both the longitudinal direction and the thickness direction Is, for example, 5 mm, but is not limited thereto.
  • the electrical wirings Y6 and Y7 extend from the surface of the two plate surfaces of the microvalve Y1 opposite to the valve casing Y2, pass through the sealing member Y3 and the valve casing Y2, and pass through the sealing member Y3 and the valve casing Y2 to the outside of the valve module Y0. Connected to the power supply at. As a result, electric power is supplied from the power source to the microvalve Y1 through the electric wirings Y6 and Y7.
  • the conversion plate Y8 is a plate-shaped member arranged between the microvalve Y1 and the valve casing Y2.
  • the conversion plate Y8 is a glass substrate.
  • One side of the two plate surfaces of the conversion plate Y8 is fixed to the microvalve Y1 with an adhesive, and the other side is fixed to the valve casing Y2 with an adhesive.
  • the conversion plate Y8 is formed with flow paths Y81, Y82, and Y83 for connecting the three refrigerant holes described later of the micro valve Y1 and the three communication holes of the valve casing Y2.
  • These flow paths Y81, Y82, and Y83 are members for absorbing the difference between the pitches of the above-mentioned three refrigerant holes arranged in a row and the pitches of the above-mentioned three communication holes arranged in a row.
  • the flow paths Y81, Y82, and Y83 penetrate from one of the two plate surfaces of the conversion plate Y8 to the other.
  • the valve casing Y2 is a resin casing that houses the microvalve Y1 and the conversion plate Y8.
  • the valve casing Y2 is formed by resin molding containing polyphenylene sulfide as a main component.
  • the valve casing Y2 is configured such that the linear expansion coefficient is a value between the linear expansion coefficient of the microvalve Y1 and the linear expansion coefficients of the body portions 330 and 350.
  • the valve casing Y2 constitutes a component mounting portion for mounting the microvalve Y1 to the body portions 330 and 350.
  • the valve casing Y2 is a box body having a bottom wall on one side and an open side on the other side.
  • the bottom wall of the valve casing Y2 is interposed between the body portions 330 and 350 and the microvalve Y1 so that the microvalve Y1 and the conversion plate Y8 do not come into direct contact with the body portions 330 and 350. Then, one surface of the bottom wall is in contact with and fixed to the body portions 330 and 350, and the other surface is in contact with and fixed to the conversion plate Y8.
  • valve casing Y2 can absorb the difference in the linear expansion coefficient between the micro valve Y1 and the body portions 330 and 350. This is because the linear expansion coefficient of the valve casing Y2 is a value between the linear expansion coefficient of the microvalve Y1 and the linear expansion coefficients of the body portions 330 and 350.
  • the coefficient of linear expansion of the conversion plate Y8 is a value between the coefficient of linear expansion of the microvalve Y1 and the coefficient of linear expansion of the valve casing Y2.
  • the bottom wall of the valve casing Y2 has a plate-shaped base portion Y20 facing the microvalve Y1 and a pillar-shaped first protruding portion Y21 and a second protruding portion Y21 protruding from the base portion Y20 in a direction away from the microvalve Y1. It has a portion Y22 and a third protruding portion Y23.
  • the first protruding portion Y21, the second protruding portion Y22, and the third protruding portion Y23 are fitted into the first recesses 330c and 350c, the second recesses 330d and 350d, and the third recesses 330e and 350e formed in the body portions 330 and 350. It has been.
  • the first protrusion Y21 is formed with a first communication hole YV1 that penetrates from the end on the side of the microvalve Y1 to the end opposite to the microvalve Y1.
  • the second protrusion Y22 is formed with a second communication hole YV2 that penetrates from the end on the side of the microvalve Y1 to the end opposite to the microvalve Y1.
  • the third protrusion Y23 is formed with a third communication hole YV3 that penetrates from the end on the side of the microvalve Y1 to the end opposite to the microvalve Y1.
  • the first communication hole YV1, the second communication hole YV2, and the third communication hole YV3 are arranged in a row, and the first communication hole YV1 is located between the second communication hole YV2 and the third communication hole YV3.
  • the microvalve Y1 side end of the first communication hole YV1 communicates with the valve casing Y2 side end of the flow path Y81 formed in the conversion plate Y8.
  • the microvalve Y1 side end of the second communication hole YV2 communicates with the valve casing Y2 side end of the flow path Y82 formed in the conversion plate Y8.
  • the microvalve Y1 side end of the third communication hole YV3 communicates with the valve casing Y2 side end of the flow path Y83 formed in the conversion plate Y8.
  • the sealing member Y3 is a member made of epoxy resin that seals the other side of the valve casing Y2 that has been opened.
  • the sealing member Y3 covers the entire plate surface on the side opposite to the conversion plate Y8 side of the two plate surfaces on the front and back of the micro valve Y1. Further, the sealing member Y3 covers a part of the plate surface of the conversion plate Y8 on the side opposite to the bottom wall side of the valve casing Y2. Further, the sealing member Y3 covers the electric wirings Y6 and Y7 to realize waterproofing and insulation of the electric wirings Y6 and Y7.
  • the sealing member Y3 is formed by resin potting molding or the like.
  • the O-ring Y4 is attached to the outer periphery of the first protruding portion Y21 and seals between the body portions 330 and 350 and the first protruding portion Y21 to suppress leakage of the refrigerant to the outside and to the outside of the refrigerant circuit. ..
  • the O-ring Y5a is attached to the outer periphery of the second protruding portion Y22 and seals between the body portions 330 and 350 and the second protruding portion Y22 to suppress leakage of the refrigerant to the outside and to the outside of the refrigerant circuit.
  • the O-ring Y5b is attached to the outer periphery of the third protruding portion Y23 and seals between the body portions 330 and 350 and the third protruding portion Y23 to suppress leakage of the refrigerant to the outside and to the outside of the refrigerant circuit. ..
  • microvalve Y1 is a MEMS having a first outer layer Y11, an intermediate layer Y12, and a second outer layer Y13, all of which are semiconductors.
  • MEMS is an abbreviation for Micro Electro Mechanical Systems.
  • the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13 are rectangular plate-shaped members having the same outer shape, and are laminated in the order of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13.
  • the second outer layer Y13 is arranged on the side closest to the bottom wall of the valve casing Y2.
  • the structures of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13, which will be described later, are formed by a semiconductor manufacturing process such as chemical etching.
  • the first outer layer Y11 is a semiconductor member. As shown in FIG. 7, two through holes Y14 and Y15 penetrating the front and back are formed in the first outer layer Y11. The microvalve Y1 side ends of the electrical wirings Y6 and Y7 are inserted into the through holes Y14 and Y15, respectively.
  • the second outer layer Y13 is a semiconductor member. As shown in FIGS. 7, 9, and 10, the second outer layer Y13 is formed with a first refrigerant hole Y16, a second refrigerant hole Y17, and a third refrigerant hole Y18 penetrating the front and back surfaces.
  • the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 correspond to the first fluid hole, the second fluid hole, and the third fluid hole, respectively.
  • the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 communicate with the flow paths Y81, Y82, and Y83 of the conversion plate Y8, respectively.
  • the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 are arranged in a row.
  • the first refrigerant hole Y16 is arranged between the second refrigerant hole Y17 and the third refrigerant hole Y18.
  • the intermediate layer Y12 is a conductive semiconductor member, and is sandwiched between the first outer layer Y11 and the second outer layer Y13. As shown in FIG. 9, the intermediate layer Y12 has a first fixed portion Y121, a second fixed portion Y122, a plurality of first ribs Y123, a plurality of second ribs Y124, a spine Y125, an arm Y126, a beam Y127, and a movable beam. It has a part Y128.
  • the first fixing portion Y121 is a member fixed to the first outer layer Y11 and the second outer layer Y13.
  • the first fixed portion Y121 is formed so as to surround the second fixed portion Y122, the first rib Y123, the second rib Y124, the spine Y125, the arm Y126, the beam Y127, and the movable portion Y128 in the same fluid chamber Y19.
  • the fluid chamber Y19 is a chamber surrounded by a first fixing portion Y121, a first outer layer Y11, and a second outer layer Y13. In the fluid chamber Y19, the refrigerant introduced into the first control chamber PC1 flows.
  • the first fixed portion Y121, the first outer layer Y11, and the second outer layer Y13 correspond to the base portion as a whole.
  • the electrical wirings Y6 and Y7 are electrical wirings for changing the temperature of the plurality of first ribs Y123 and the plurality of second ribs Y124 to displace them.
  • the refrigerant passes from the fluid chamber Y19 to the microvalve Y1 through other than the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18. It is done in a form that suppresses leakage.
  • the second fixing portion Y122 is fixed to the first outer layer Y11 and the second outer layer Y13.
  • the second fixed portion Y122 is surrounded by the first fixed portion Y121 and is arranged away from the first fixed portion Y121.
  • the plurality of first ribs Y123, the plurality of second ribs Y124, the spine Y125, the arm Y126, the beam Y127, and the movable portion Y128 are not fixed to the first outer layer Y11 and the second outer layer Y13, and are the first. It is displaceable with respect to the outer layer Y11 and the second outer layer Y13.
  • the spine Y125 has an elongated rod shape extending in the lateral direction of the rectangular shape of the intermediate layer Y12. One end of the spine Y125 in the longitudinal direction is connected to the beam Y127.
  • the plurality of first ribs Y123 are arranged on one side of the spine Y125 in a direction orthogonal to the longitudinal direction of the spine Y125.
  • the plurality of first ribs Y123 are arranged in the longitudinal direction of the spine Y125.
  • Each first rib Y123 has an elongated rod shape and can be expanded and contracted according to the temperature.
  • Each first rib Y123 is connected to the first fixing portion Y121 at one end in the longitudinal direction thereof, and is connected to the spine Y125 at the other end.
  • Each of the first ribs Y123 is skewed with respect to the spine Y125 so as to approach the spine Y125 side from the first fixing portion Y121 side so as to be offset toward the beam Y127 side in the longitudinal direction of the spine Y125. ..
  • the plurality of first ribs Y123 extend in parallel with each other.
  • the plurality of second ribs Y124 are arranged on the other side of the spine Y125 in a direction orthogonal to the longitudinal direction of the spine Y125.
  • the plurality of second ribs Y124 are arranged in the longitudinal direction of the spine Y125.
  • Each second rib Y124 has an elongated rod shape and can be expanded and contracted according to the temperature.
  • Each second rib Y124 is connected to the second fixing portion Y122 at one end in the longitudinal direction thereof, and is connected to the spine Y125 at the other end.
  • Each of the second ribs Y124 is skewed with respect to the spine Y125 so as to approach the spine Y125 side from the second fixed portion Y122 side so as to be offset toward the beam Y127 side in the longitudinal direction of the spine Y125. ..
  • the plurality of second ribs Y124 extend in parallel with each other.
  • the plurality of first ribs Y123, the plurality of second ribs Y124, and the spine Y125 correspond to the drive unit as a whole.
  • the arm Y126 has an elongated rod shape that extends non-orthogonally and parallel to the spine Y125. One end of the arm Y126 in the longitudinal direction is connected to the beam Y127, and the other end is connected to the first fixing portion Y121.
  • the beam Y127 has an elongated rod shape extending in a direction intersecting the spine Y125 and the arm Y126 at about 90 °. One end of the beam Y127 is connected to the movable portion Y128. The arm Y126 and the beam Y127 correspond to the amplification portion as a whole.
  • connection position YP1 between the arm Y126 and the beam Y127, the connection position YP2 between the spine Y125 and the beam Y127, and the connection position YP3 between the beam Y127 and the movable portion Y128 are arranged in this order along the longitudinal direction of the beam Y127. If the connection point between the first fixing portion Y121 and the arm Y126 is a hinge YP0, the connection position from the hinge YP0 is more than the linear distance from the hinge YP0 to the connection position YP2 in the plane parallel to the plate surface of the intermediate layer Y12.
  • the straight line distance to YP3 is longer.
  • the value obtained by dividing the former straight line distance by the latter straight line distance may be 1/5 or less, or may be 1/10 or less.
  • the movable portion Y128 adjusts the pressure of the refrigerant flowing through the fluid chamber Y19.
  • the movable portion Y128 has a rectangular shape whose outer shape extends in a direction of approximately 90 ° with respect to the longitudinal direction of the beam Y127.
  • the movable portion Y128 can move integrally with the beam Y127 in the fluid chamber Y19.
  • the movable portion Y128 has a frame shape surrounding the through hole Y120 penetrating the front and back of the intermediate layer Y12. Therefore, the through hole Y120 also moves integrally with the movable portion Y128.
  • the through hole Y120 is a part of the fluid chamber Y19.
  • the movable portion Y128 moves as described above to change the opening degree of the second refrigerant hole Y17 with respect to the through hole Y120 and the opening degree of the third refrigerant hole Y18 with respect to the through hole Y120.
  • the first refrigerant hole Y16 always communicates with the through hole Y120 in full opening.
  • the Y1 side end of the micro valve is connected.
  • the microvalve Y1 side end of the electric wiring Y7 passing through the through hole Y15 of the first outer layer Y11 shown in FIG. 7 is connected to the second application point Y130 of the second fixing portion Y122.
  • valve module Y0 Opera of the valve module Y0 will be described.
  • a voltage is applied between the electrical wirings Y6 and Y7 to the first application point Y129 and the second application point Y130.
  • a current flows through the plurality of first ribs Y123 and the plurality of second ribs Y124. Due to this current, the plurality of first ribs Y123 and the plurality of second ribs Y124 generate heat. As a result, each of the plurality of first ribs Y123 and the plurality of second ribs Y124 expands in the longitudinal direction thereof.
  • connection position YP2 corresponds to the urging position and the pressure adjusting urging position.
  • the member consisting of the beam Y127 and the arm Y126 changes their postures integrally with the hinge YP0 as the fulcrum and the connection position YP2 as the power point.
  • the movable portion Y128 connected to the end of the beam Y127 opposite to the arm Y126 also moves in the longitudinal direction to the side where the spine Y125 pushes the beam Y127.
  • the plurality of first ribs Y123 and the plurality of second ribs Y124 urge the spine Y125 to the side opposite to the connection position YP2.
  • the urged spine Y125 pulls the beam Y127 at the connection position YP2.
  • the member including the beam Y127 and the arm Y126 changes their postures integrally with the hinge YP0 as the fulcrum and the connection position YP2 as the power point.
  • the movable portion Y128 connected to the end of the beam Y127 opposite to the arm Y126 also moves in the longitudinal direction to the side where the spine Y125 pulls the beam Y127.
  • the movable portion Y128 stops at a predetermined non-energized position.
  • the microvalve Y1 When the microvalve Y1 is energized, the larger the power supplied from the electrical wirings Y6 and Y7 to the microvalve Y1 via the first application point Y129 and the second application point Y130, the more the movable portion with respect to the non-energized position. The amount of movement of Y128 also increases. This is because the higher the electric power supplied to the micro valve Y1, the higher the temperature of the first rib Y123 and the second rib Y124, and the larger the degree of expansion.
  • the larger the duty ratio the larger the amount of movement of the movable portion Y128 with respect to the non-energized state.
  • the through hole Y120 has the first refrigerant hole Y16 and the third refrigerant hole Y18 in the direction orthogonal to the plate surface of the intermediate layer Y12. Although it overlaps, it does not overlap with the second refrigerant hole Y17 in the relevant direction.
  • the second refrigerant hole Y17 overlaps the movable portion Y128 in the direction orthogonal to the plate surface of the intermediate layer Y12. That is, at this time, the first refrigerant hole Y16 and the third refrigerant hole Y18 are fully opened with respect to the through hole Y120, and the second refrigerant hole Y17 is fully closed.
  • the first refrigerant hole Y16 communicates with the third refrigerant hole Y18 via the movable portion Y128, and the second refrigerant hole Y17 is blocked from both the first refrigerant hole Y16 and the third refrigerant hole Y18.
  • the movable portion Y128 when the movable portion Y128 is located at the position farthest from the non-energized position due to the energization of the micro valve Y1, the position of the movable portion Y128 at that time is referred to as the maximum energized position. ..
  • the electric power supplied to the microvalve Y1 becomes the maximum within the control range.
  • the duty ratio becomes the maximum value (for example, 100%) within the control range in the above-mentioned PWM control.
  • the through hole Y120 overlaps with the first refrigerant hole Y16 and the second refrigerant hole Y17 in the direction orthogonal to the plate surface of the intermediate layer Y12, but the third refrigerant hole Y17 is in that direction. It does not overlap with Y18.
  • the third refrigerant hole Y18 overlaps the movable portion Y128 in the direction orthogonal to the plate surface of the intermediate layer Y12. That is, at this time, the first refrigerant hole Y16 and the second refrigerant hole Y17 are fully opened with respect to the through hole Y120, and the third refrigerant hole Y18 is fully closed.
  • the first refrigerant hole Y16 communicates with the second refrigerant hole Y17 via the movable portion Y128, and the third refrigerant hole Y18 is blocked from both the first refrigerant hole Y16 and the second refrigerant hole Y17.
  • the movable portion Y128 can be stopped at any intermediate position between the non-energized position and the maximum energized position.
  • the electric power supplied to the microvalve Y1 is the maximum value within the control range. It should be half.
  • the duty ratio of PWM control may be 50%.
  • the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 all communicate with the through hole Y120.
  • the second refrigerant hole Y17 and the third refrigerant hole Y18 are not fully opened with respect to the through hole Y120, and have an opening degree of less than 100% and larger than 0%.
  • the opening degree of the third refrigerant hole Y18 with respect to the through hole Y120 decreases, and the opening degree of the second refrigerant hole Y17 increases.
  • the micro valve Y1 functions as a lever in which the beam Y127 and the arm Y126 have the hinge YP0 as a fulcrum, the connection position YP2 as a power point, and the connection position YP3 as an action point.
  • the linear distance from the hinge YP0 to the connection position YP3 is longer than the linear distance from the hinge YP0 to the connection position YP2 in the plane parallel to the plate surface of the intermediate layer Y12. Therefore, the amount of movement of the connection position YP3, which is the point of action, is larger than the amount of movement of the connection position YP2, which is the point of effort. Therefore, the amount of displacement due to thermal expansion is amplified by the lever and transmitted to the movable portion Y128.
  • the flow path of the refrigerant in the micro valve Y1 has a U-turn structure. Specifically, the refrigerant flows into the microvalve Y1 from one surface of the microvalve Y1, passes through the microvalve Y1, and flows out of the microvalve Y1 from the same surface of the microvalve Y1.
  • the flow path of the refrigerant in the valve module Y0 also has a U-turn structure. Specifically, the refrigerant flows into the valve module Y0 from one surface of the valve module Y0, passes through the valve module Y0, and flows out of the valve module Y0 from the same side surface of the valve module Y0.
  • the direction orthogonal to the plate surface of the intermediate layer Y12 is the stacking direction of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13.
  • the first refrigerant hole Y16 communicates with the control chamber 334 and 354 via the first communication holes YV1, the first recesses 330c, and the first through holes 330f and 350f of 350c.
  • the second refrigerant hole Y17 communicates with the high pressure region HPA in the cycle through the second communication holes YV2, the second recess 330d, and the second through holes 330g and 350g of 350d.
  • the third refrigerant hole Y18 communicates with the low pressure region LPA in the cycle through the third through holes 330h and 350h of the third communication holes YV3 and the third recesses 330e and 350e.
  • the refrigerant holes Y16, Y17, and Y18 communicate with each other, and the control chamber 334 and 354 have a low voltage in the cycle. Communicates with region LPA and high pressure region HPA. As a result, the pressure in the control chamber 334 and 354 (that is, the control pressure Pm) becomes an intermediate pressure larger than the low pressure pressure Pl and smaller than the high pressure pressure Ph.
  • the movable portion Y128 when the movable portion Y128 is in the maximum energized position by energizing the micro valve Y1, the first refrigerant hole Y16 and the second refrigerant hole Y17 communicate with each other, and the control chamber 334 and 354 communicate with the high-pressure region HPA in the cycle. Communicate. As a result, the pressure in the control chamber 334 and 354 (that is, the control pressure Pm) becomes the high pressure pressure Ph.
  • the control pressure Pm is changed by changing the voltage applied to the microvalve Y1 by PWM control.
  • the refrigeration cycle apparatus 30 increases the control pressure Pm by increasing the duty ratio of PWM control, and decreases the control pressure Pm by decreasing the duty ratio of PWM control.
  • control device 300 controls the first expansion valve 33 to the fully open state by maximizing the duty ratio of the PWM control to the micro valve Y1 of the first expansion valve 33 during indoor cooling. Further, the control device 300 controls the second expansion valve 35 to the throttled state by setting the duty ratio of the PWM control to the micro valve Y1 of the second expansion valve 35 to an intermediate value during indoor cooling.
  • the control device 300 controls the first expansion valve 33 to the throttled state by setting the duty ratio of the PWM control to the micro valve Y1 of the first expansion valve 33 to an intermediate value at the time of indoor heating. Further, the control device 300 controls the second expansion valve 35 to be in a fully closed state by minimizing the duty ratio of the PWM control to the micro valve Y1 of the second expansion valve 35 during indoor heating.
  • the control device 300 controls the first expansion valve 33 to the throttled state by setting the duty ratio of the PWM control to the micro valve Y1 of the first expansion valve 33 to an intermediate value during dehumidifying and heating. Further, the control device 300 controls the second expansion valve 35 to the throttled state by setting the duty ratio of the PWM control to the micro valve Y1 of the second expansion valve 35 to an intermediate value during dehumidifying and heating.
  • Each expansion valve 33, 35 of the refrigeration cycle device 30 described above can introduce the high-pressure refrigerant and the low-pressure refrigerant in the cycle into the pressure control unit 337, 357 in any of the cases of indoor cooling, indoor heating, and dehumidifying heating. It has become. According to this, the control chamber 334 and 354 can be controlled to a desired pressure by the pressure control unit 337 and 357. Therefore, the operation required for the expansion valves 33 and 35 can be realized in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating.
  • the pressure control unit 337, 357 includes a high-pressure connection flow path communicating with a high-pressure point where the high-pressure refrigerant flows in the cycle.
  • This high-pressure connection flow path is connected to the refrigerant flow path from the refrigerant discharge side of the compressor 31 to the first expansion valve 33 constituting the valve device.
  • the pressure control units 337 and 357 of the expansion valves 33 and 35 are connected to the discharge refrigerant flow path 311 via the second through holes 330 g and 350 g. According to this, the discharge refrigerant (that is, the gas single-phase refrigerant) of the compressor 31 in which the state of the refrigerant is stable is introduced.
  • the pressure control of the control chamber 334 and 354 by the pressure control unit 337 and 357 is performed as compared with the case where the refrigerant after passing through the condenser 32 accompanied by the phase change is introduced into the pressure control unit 337 and 357. It will be easier.
  • the gas single-phase high-pressure refrigerant can be introduced into the pressure control unit 337, 357 in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating. Therefore, compared to the case where the phase state of the refrigerant introduced into the pressure control unit 337 and 357 changes in the room cooling, the room heating, and the dehumidifying heating, the pressure control unit 337 and 357 presses the control room 334 and 354 with a desired pressure. Easy to control.
  • the pressure control unit 337, 357 includes a low-pressure connection flow path communicating with a low-pressure point where the low-pressure refrigerant flows in the cycle.
  • This low-pressure connection flow path is connected to the refrigerant flow path from the refrigerant merging portion 382 to the refrigerant suction side of the compressor 31.
  • the pressure control units 337 and 357 of the expansion valves 33 and 35 are connected to the suction refrigerant flow path 312 via the third through holes 330h and 350h. According to this, the gas-rich refrigerant after passing through the accumulator ACC is introduced.
  • the pressure control of the control chamber 334 and 354 by the pressure control unit 337 and 357 becomes easier as compared with the case where the refrigerant before flowing into the accumulator ACC is introduced into the pressure control unit 337 and 357.
  • the gas-rich low-pressure refrigerant can be introduced into the pressure control unit 337 and 357 in any of the operation modes of indoor cooling, indoor heating, and dehumidifying heating. Therefore, compared to the case where the phase state of the refrigerant introduced into the pressure control unit 337 and 357 changes in the room cooling, the room heating, and the dehumidifying heating, the pressure control unit 337 and 357 presses the control room 334 and 354 with a desired pressure. Easy to control.
  • the first expansion valve 33 that decompresses the refrigerant during indoor heating and the second expansion valve 35 that depressurizes the refrigerant during indoor cooling and dehumidifying heating each constitute the valve device of the present disclosure. .. Even with such a cycle configuration, the high-pressure refrigerant and the low-pressure refrigerant can be introduced into the pressure control unit 337 and 357 regardless of the operation mode. Therefore, the pressure control unit 337 and 357 desired the control chamber 334 and 354. The pressure can be controlled.
  • the pressure control unit 337, 357 is composed of a valve module Y0.
  • the valve module Y0 is smaller than a solenoid valve or an electric valve because the valve bodies 332a and 352a are configured to be displaced to the valve opening side or the valve closing side by adjusting the pressure of the control chamber 334 and 354 by the micro valve Y1.
  • the microvalve Y1 is formed of a semiconductor chip as described above. Further, as described above, the displacement amount due to thermal expansion can be amplified by using a lever, which makes it possible to configure the valve to be smaller than an electromagnetic valve or an electric valve that does not use such a lever.
  • the micro valve Y1 is configured to change the pressure of the control chamber 334 and 354 by adjusting the opening degrees of the second refrigerant hole Y17 and the third refrigerant hole Y18 by the movable portion Y128. According to this, the valve bodies 332a and 352a can be displaced to the valve closing side and the valve opening side by adjusting the pressure of the control chamber 334 and 354 by the micro valve Y1.
  • the expansion valves 33 and 35 are arranged at different positions in the direction in which the main valves 332 and 352 and the pressure control unit 337 and 357 are orthogonal to the valve axial direction DRax. In this way, if the pressure control unit 337, 357 and the main valves 332, 352 have a layout that does not overlap with the valve axial DRax, they are arranged around the expansion valves 33, 35 and the expansion valves 33, 35. It becomes difficult for it to interfere with other parts. As a result, the degree of freedom in the layout of the expansion valves 33, 35 and other parts is increased, so that the degree of freedom in design can be improved.
  • expansion valves 33 and 35 Other components arranged around the expansion valves 33 and 35 include a condenser 32 located before and after the flow direction of the refrigerant, an outdoor heat exchanger 34, a cooling evaporator 36, and the like. Further, each of the expansion valves 33 and 35 needs a space for displacing the main valves 332 and 352 in the valve axial direction DRax. Therefore, if the pressure control units 337 and 357 and the main valves 332 and 352 overlap each other in the valve axial direction DRax, it is inevitable that the body size of each of the expansion valves 33 and 35 will increase in the valve axial direction DRax.
  • the pressure control unit 337, 357 of the present embodiment has a layout in which at least a part thereof overlaps with the main valves 332 and 352 in the direction orthogonal to the valve axial direction DRax.
  • the layout is such that at least a part of the pressure control unit 337 and 357 and the main valves 332 and 352 overlap in the direction perpendicular to the valve axis direction DRax, the valve axis direction DRax of each expansion valve 33 and 35 is formed. It is possible to suppress the increase in size of the physique in.
  • expansion valves 33 and 35 having the same basic structure are exemplified, but the expansion valves 33 and 35 are not limited thereto.
  • the expansion valves 33 and 35 may have different structures.
  • one expansion valve is configured in the same manner as described in the first embodiment, and the other expansion valve is an electric expansion valve including a solenoid and an electric motor. It may be configured.
  • the second expansion valve 35 may not have a fully closed function.
  • Each of the expansion valves 33 and 35 of the first embodiment is arranged so that the pressure control units 337 and 357 and the valve bodies 332a and 352a do not overlap each other in the direction of the valve axial direction DRax, but the present invention is limited to this. Not done.
  • the expansion valves 33 and 35 may be arranged so that the pressure control units 337 and 357 and the valve bodies 332a and 352a overlap each other in the direction of the valve axial DRax. That is, the pressure control units 337 and 357 may be arranged in the expansion valves 33 and 35 at positions shifted in the valve axis direction DRax with respect to the positions where the valve bodies 332a and 352a are arranged. This also applies to the second embodiment.
  • the bypass valve 37 of the first embodiment is composed of a solenoid valve that drives the valve body by the electromagnetic attraction force of the solenoid, but the bypass valve 37 is not limited to this, and is configured in the same manner as the expansion valves 33 and 35, for example. May be good.
  • each expansion valve 33, 35 includes a rectangular parallelepiped body portion 330, 350.
  • Through holes 330j and 350j penetrating from the upper surface to the lower surface and bottomed holes 330k and 350k extending downward from the upper surface are formed in the body portions 330 and 350.
  • the through holes 330j and 350j and the bottomed holes 330k and 350k are formed at different positions in the body portions 330 and 350 in the direction orthogonal to the valve axial direction DRax.
  • the main valves 332 and 352 are arranged in the through holes 330j and 350j, and the pressure control units 337 and 357 are arranged in the bottomed holes 330k and 350k.
  • the main valves 332, 352 and the pressure control unit 337, 357 are arranged at different positions in the direction orthogonal to the valve axial direction DRax.
  • the pressure control units 337 and 357 are arranged offset with respect to the main valves 332 and 352 in the direction orthogonal to the valve axis direction DRax.
  • At least a part of the pressure control unit 337 and 357 is arranged so as to overlap the main valves 332 and 352 in the direction orthogonal to the valve axial direction DRax. As a result, the pressure control unit 337, 357 and the control chamber 334, 354 are arranged adjacent to each other.
  • the main valves 332 and 352 have valve bodies 332a and 352a, support portions 332b and 352b, first springs 332c and 352c, second springs 332d and 352d, adjusting screws 332e and 352e, and actuating rods 332f. It has 352f, caps 332i and 352i.
  • the caps 332i, 352i, the second springs 332d, 352d, the operating rods 332f, 352f, the valve bodies 332a, 352a, the support portions 332b, 352b, the first springs 332c, 352c, and the adjusting screws 332e, 352e are in this order in the valve axis direction. They are arranged side by side in the DRax.
  • the stoppers 332g and 352g are fixed to the ends of the operating rods 332f and 352f via the partition portions 332h and 352h. That is, in the main valves 332 and 352, the stoppers 332g and 352g, the partition portions 332h and 352h, and the operating rods 332f and 352f are arranged in this order in the valve axial direction DRax.
  • An O-ring S1 as a sealing member is provided on the outer periphery of the partition portions 332h and 352h. Further, O-rings S2, S3, and S4 as sealing members are also provided on the outer circumferences of the caps 332i and 352i and the outer circumferences of the adjusting screws 332e and 352e.
  • the first connecting pipes 339a, 359a, the second connecting pipes 339b, 359b, and the third connecting pipes 339c, 359c are connected to the body portions 330 and 350.
  • the first connecting pipe 339a, 359a, the second connecting pipe 339b, 359b, and the third connecting pipe 339c, 359c are composed of thin tubes such as a capillary tube.
  • the first connecting pipes 339a and 359a are pipes that communicate the second flow path Z23, which will be described later, with the control chambers 334 and 354.
  • the second connecting pipe 339b, 359b is a pipe that communicates the first flow path Z22, which will be described later, with the high-pressure region HPA in the cycle.
  • the third connecting pipe 339c, 359c is a pipe that communicates the third flow path Z24, which will be described later, with the low pressure region LPA in the cycle.
  • the pressure control unit 337, 357 is composed of the valve module Z0 shown in FIGS. 16 and 17.
  • the valve module Z0 has an outer shape corresponding to the bottomed holes 330k and 350k so that it can be fitted into the bottomed holes 330k and 350k.
  • the valve module Z0 of the present embodiment has a micro valve Z1, a valve casing Z2, three O-rings Z4, Z5a, Z5b, two terminals Z6, Z7, and a lid Z8.
  • the valve casing Z2 has a substantially cylindrical shape.
  • the valve casing Z2 has a recess Z21 formed in the lower end portion constituting the bottom portion, which is recessed toward the upper end portion.
  • the valve casing Z2 is formed with a first flow path Z22, a second flow path Z23, and a third flow path Z24.
  • the first flow path Z22 is formed by the space inside the recess Z21 of the valve casing Z2.
  • the first flow path Z22 communicates with the high pressure region HPA in the cycle via the second communication pipes 339b and 359b.
  • the second flow path Z23 penetrates the valve casing Z2 from the side surface to the lower end of the valve casing Z2.
  • the second flow path Z23 communicates with the control chamber 334 and 354 via the first communication pipes 339a and 359a.
  • the second flow path Z23 has a second horizontal hole Z23a and a second vertical hole Z23b.
  • the second lateral hole Z23a is a through hole extending in a direction intersecting the axial center CLm of the valve casing Z2.
  • the second vertical hole Z23b branches in the middle of the second horizontal hole Z23a and extends to the lower end along the axial center CLm of the valve casing Z2.
  • the second flow path Z23 is open at a position substantially intermediate between the upper end portion and the lower end portion on the side surface of the valve casing Z2. Further, as shown in FIG. 17, the second flow path Z23 is open to the bottom surface of the recess Z21.
  • the third flow path Z24 penetrates the valve casing Z2 from the side surface to the lower end of the valve casing Z2.
  • the third flow path Z24 communicates with the low pressure region LPA in the cycle via the third connecting pipes 339c and 359c.
  • the third flow path Z24 has a third horizontal hole Z24a and a third vertical hole Z24b.
  • the third lateral hole Z24a is a through hole extending in a direction intersecting the axial center CLm of the valve casing Z2.
  • the third vertical hole Z24b branches in the middle of the third horizontal hole Z24a and extends to the lower end along the axial center CLm of the valve casing Z2.
  • the third flow path Z24 opens at a position closer to the upper end portion than the opening of the second flow path Z23 on the side surface of the valve casing Z2. Further, as shown in FIG. 17, the third flow path Z24 opens at a position different from the opening of the second flow path Z23 on the bottom surface of the recess Z21.
  • the second flow path Z23 and the third flow path Z24 are formed at different positions in the valve casing Z2 so as not to communicate with each other.
  • a first groove portion Z25, a second groove portion Z26, and a third groove portion Z27 are formed on the side surface of the valve casing Z2.
  • the first groove portion Z25, the second groove portion Z26, and the third groove portion Z27 extend along the circumferential direction of the valve casing Z2.
  • the first groove portion Z25 is formed below the position where the second flow path Z23 opens on the side surface of the valve casing Z2.
  • An O-ring Z4 is attached to the first groove portion Z25.
  • the O-ring Z4 suppresses refrigerant leakage from the gap between the valve casing Z2 and the bottomed holes 330k and 350k.
  • the second groove portion Z26 is formed between the opening of the second flow path Z23 and the opening of the third flow path Z24 on the side surface of the valve casing Z2.
  • An O-ring Z5a is attached to the second groove portion Z26.
  • the O-ring Z5a suppresses refrigerant leakage from the gap between the valve casing Z2 and the bottomed holes 330k and 350k.
  • the third groove portion Z27 is formed above the position where the third flow path Z24 opens on the side surface of the valve casing Z2.
  • An O-ring Z5b is attached to the third groove portion Z27.
  • the O-ring Z5b suppresses refrigerant leakage from the gap between the valve casing Z2 and the bottomed holes 330k and 350k.
  • the second flow path Z23 is the first connecting pipe 339a, through a gap between the opening formed by the second flow path Z23 and the inner walls of the bottomed holes 330k and 350k on the side surface of the valve casing Z2.
  • the third flow path Z24 communicates with the third connecting pipes 339c and 359c through a gap between the opening formed by the third flow path Z24 and the inner walls of the bottomed holes 330k and 350k on the side surface of the valve casing Z2. do.
  • the lid Z8 is arranged at the upper end portion, and a part of the terminals Z6 and Z7 protrudes from the upper end portion.
  • the terminals Z6 and Z7 are wiring components that electrically connect the circuit board 338 and 358 and the microvalve Z1.
  • the terminals Z6 and Z7 are insert-molded into the valve casing Z2 so that a part thereof protrudes from the upper end portion of the valve casing Z2.
  • the lid Z8 is an annular component having a window portion Z81 formed substantially in the center.
  • the lid Z8 is fixed to the bottomed holes 330k and 350k by a joining means such as caulking, screwing, and welding.
  • the window portion Z81 of the lid Z8 is an insertion hole through which the terminals Z6 and Z7 pass.
  • the microvalve Z1 of the present embodiment is configured in the same manner as the microvalve Y1 described in the first embodiment.
  • those common to the components of the micro valve Y1 of the first embodiment are described by changing "Y1" at the beginning of the reference numeral to "Z1".
  • those corresponding to the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 of the first embodiment are the first refrigerant hole Z16 and the second refrigerant hole Z17.
  • the third refrigerant hole Z18 are the first refrigerant hole Z16 and the second refrigerant hole Z17.
  • the micro valve Z1 is arranged in the recess Z21 of the valve casing Z2. Although not shown, the microvalve Z1 is supported by a support member provided in the recess Z21.
  • the surface of the microvalve Z1 on which the first refrigerant hole Z16, the second refrigerant hole Z17, and the third refrigerant hole Z18 are formed is arranged inside the recess Z21 in a posture facing the bottom surface of the recess Z21.
  • the first refrigerant hole Z16 faces the opening of the second flow path Z23
  • the second refrigerant hole Z17 faces the first flow path Z22
  • the third refrigerant hole Z18 faces the opening. It is arranged inside the recess Z21 so as to face the opening of the three flow paths Z24.
  • the first refrigerant hole Z16 communicates with the second flow path Z23
  • the second refrigerant hole Z17 communicates with the first flow path Z22
  • the third refrigerant hole Z18 communicates with the third flow path Z24.
  • the micro valve Z1 is provided with an electrode Z28 on the opposite side of the surface on which the first refrigerant hole Z16, the second refrigerant hole Z17, and the third refrigerant hole Z18 are formed.
  • the electrode Z28 is a component that electrically connects the microvalve Z1 to the terminals Z6 and Z7. A part of the electrode Z28 and a part of the microvalve Z1 are sealed by the mold resin portion Z29.
  • the micro valve Z1 is connected to the circuit board 338 and 358 via the electrodes Z28, terminals Z6 and Z7.
  • the microvalve Z1 is driven by power supply from the circuit board 338 and 358.
  • the circuit boards 338 and 358 are connected to the terminals Z6 and Z7 of the pressure control units 337 and 357 in a posture in which the plate surfaces 338a and 358a of the circuit boards 338 and 358 are horizontally parallel to each other. ..
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effect as that of the first embodiment from the same configuration as that of the first embodiment or the equivalent configuration.
  • the main valves 332 and 352 are attached to the through holes 330j and 350j of the body portions 330 and 350 from the vertical DRg, and the pressure is applied to the bottomed holes 330k and 350k from the vertical DRg.
  • the structure is such that the control unit 337 and 357 are attached. According to this, the assembly work of the main valves 332 and 352 and the pressure control unit 337 and 357 with respect to the body portions 330 and 350 becomes easy.
  • the through holes 330j and 350j and the bottomed holes 330k and 350k of the body portions 330 and 350 are exemplified as extending along the vertical DRg, but the body portions 330 and 350 are limited to this. Not done.
  • the body portions 330 and 350 have different aspects from those described above, for example, if the through holes 330j and 350j and the bottomed holes 330k and 350k are formed at different positions in the direction orthogonal to the valve axial direction DRax. May be good.
  • the circuit board 338a and 358 are connected to the pressure control unit 337 and 357 in a posture in which the plate surfaces 338a and 358a of the circuit board 338a and 358 extend in the horizontal direction.
  • the circuit board 338 and 358 may be connected to the pressure control unit 337 and 357 in a posture in which the plate surfaces 338a and 358a intersect with each other in the horizontal direction.
  • the refrigerating cycle device 30 of the present embodiment is capable of cooling the equipment for cooling the equipment to be cooled such as the battery mounted on the vehicle by the endothermic action at the time of evaporation of the refrigerant.
  • the refrigerating cycle device 30 has a third expansion valve 39 and an equipment evaporator so as to be parallel to the second expansion valve 35 and the cooling evaporator 36 on the refrigerant outlet side of the condenser 32. 40 is connected.
  • the third expansion valve 39 is provided in a branch pipe branching from the refrigerant pipe connecting the outdoor heat exchanger 34 and the second expansion valve 35.
  • the third expansion valve 39 is an expansion valve for cooling the equipment that reduces the pressure of the refrigerant that has passed through the outdoor heat exchanger 34 when the equipment is cooled.
  • the third expansion valve 39 has a structure in which the flow of the refrigerant is blocked in a fully closed state where the throttle opening is minimized.
  • the third expansion valve 39 constitutes the third pressure reducing portion.
  • the first expansion valve 33, the second expansion valve 35, and the third expansion valve 39 of the present embodiment are configured as one integrated valve VD in which some parts are integrated.
  • the integrated valve VD constitutes the valve device of the present disclosure. Details of the integrated valve VD will be described later.
  • An equipment evaporator 40 is connected to the refrigerant outlet side of the third expansion valve 39.
  • the equipment evaporator 40 is a heat exchanger that evaporates the refrigerant that has passed through the third expansion valve 39.
  • the equipment evaporator 40 includes a refrigerant flow path portion 401 through which the refrigerant flows and a heat medium flow path portion 402 through which the heat medium of the cooling circuit LC flows, and the refrigerant and the heat medium flowing through the cooling circuit LC.
  • a cooling heat exchanger is configured to cool the heat medium by exchanging heat.
  • the cooling circuit LC is a circuit for utilizing the latent heat of vaporization of the refrigerant as a cooling heat source for cooling the equipment to be cooled.
  • the cooling circuit LC is provided with a heat absorber or the like for absorbing heat from the battery.
  • the cooling evaporator 36 constitutes the first evaporator
  • the equipment evaporator 40 constitutes the second evaporator.
  • the refrigerant outlet side of the equipment evaporator 40 is connected to the refrigerant confluence portion 382 that merges the refrigerant outlet side of the cooling evaporator 36 and the bypass flow path 38 via the evaporation pressure adjusting valve 41.
  • the evaporation pressure adjusting valve 41 maintains the pressure of the refrigerant passing through the equipment evaporator 40 to be equal to or higher than a predetermined set pressure value.
  • the evaporation pressure regulating valve 41 is composed of, for example, a bellows type valve.
  • the refrigerating cycle device 30 includes the evaporation pressure adjusting valve 41, for example, when cooling the equipment to be cooled and cooling the vehicle interior at the same time, cooling while maintaining the pressure of the refrigerant passing through the equipment evaporator 40.
  • the pressure of the refrigerant passing through the evaporator 36 can be reduced.
  • the refrigeration cycle device 30 is provided with a bypass flow path 43 different from the bypass flow path 38 described in the first embodiment.
  • the bypass flow path 43 added in the present embodiment will be referred to as a first bypass flow path 43
  • the bypass flow path 38 described in the first embodiment will be referred to as a second bypass flow path 38 to distinguish between the two.
  • the first bypass flow path 43 is a flow path through which the refrigerant that has passed through the condenser 32 flows by bypassing the first expansion valve 33 and the outdoor heat exchanger 34.
  • One end of the first bypass flow path 43 is connected between the refrigerant outlet side of the condenser 32 and the refrigerant inlet side of the first expansion valve 33, and the other end side is the refrigerant outlet side of the outdoor heat exchanger 34 and the second expansion. It is connected between the valve 35 and the third expansion valve 39 on the refrigerant inlet side.
  • a bypass valve 44 is provided in the first bypass flow path 43.
  • the bypass valve 44 added in the present embodiment will be referred to as a first bypass valve 44
  • the bypass valve 37 described in the first embodiment will be referred to as a second bypass valve 37 to distinguish between the two.
  • the first bypass valve 44 is an opening / closing portion that opens / closes the first bypass flow path 43.
  • the first bypass valve 44 adjusts the flow rate of the refrigerant flowing through the first bypass flow path 43 by opening and closing the first bypass flow path 43.
  • the first bypass valve 44 is configured in the same manner as the second bypass valve 37.
  • the first bypass valve 44 may be configured to be different from the second bypass valve 37.
  • the first bypass valve 44 constitutes the first opening / closing portion
  • the second bypass valve 37 constitutes the second opening / closing portion.
  • check valves 45a, 45b, 45c are arranged at a plurality of locations in the cycle in order to prevent the backflow of the refrigerant.
  • the first check valve 45a is arranged between the connection portion with the second bypass flow path 38 and the connection portion with the first bypass flow path 43 on the refrigerant outlet side of the outdoor heat exchanger 34. ..
  • a second check valve 45b is arranged between the second bypass valve 37 and the refrigerant merging portion 382.
  • a third check valve 45c is arranged between the cooling evaporator 36 and the refrigerant merging portion 382.
  • the device cooling sensor 303 is connected to the input side of the control device 300 in addition to the air conditioning sensor group 301.
  • the device cooling sensor 303 includes, for example, a temperature sensor that detects the temperature of the device to be cooled.
  • the control device 300 On the output side of the control device 300, a compressor 31, a first expansion valve 33, an outdoor fan 341, a second expansion valve 35, an indoor fan 361, a second bypass valve 37, a third expansion valve 39, and a first bypass valve 44 Is connected.
  • the control device 300 can change the throttle opening degree of the third expansion valve 39 according to the situation.
  • the refrigerating cycle device 30 appropriately switches the operation mode of the refrigerating cycle device 30 by receiving inputs from the air conditioning sensor group 301, the operation panel 302, and the equipment cooling sensor 303. Specifically, the control device 300 controls the expansion valves 33, 35, 39, the bypass valve 37, and the like to change the flow method of the refrigerant in the refrigeration cycle device 30, thereby changing the operation mode of the refrigeration cycle device 30. Switch.
  • the refrigerating cycle device 30 of the present embodiment can be set to five operation modes such as indoor cooling, indoor heating, serial dehumidifying and heating, parallel dehumidifying and heating, and equipment cooling.
  • the control device 300 controls the first bypass valve 44 and the third expansion valve 39 to be in a fully closed state.
  • the 1 expansion valve 33 and the 2nd expansion valve 35 are controlled in the same manner as in the first embodiment.
  • the basic operation of the refrigerating cycle device 30 when performing indoor cooling, indoor heating, and series dehumidifying and heating is the same as that of the first embodiment.
  • the operation of the refrigerating cycle device 30 when performing parallel dehumidifying heating and equipment cooling will be described.
  • the parallel dehumidifying / heating mode is an operation mode in which the air is cooled to a temperature lower than the dew point temperature by the cooling evaporator 36, then the temperature is raised to a desired temperature by the heater core, and the air is blown into the vehicle interior.
  • Parallel dehumidifying and heating is different from series dehumidifying and heating in that the outdoor heat exchanger 34 and the cooling evaporator 36 are arranged in parallel.
  • the parallel dehumidifying and heating is executed by the refrigerating cycle device 30 when the operation mode is set to the parallel dehumidifying mode by the changeover switch, for example.
  • the heater circuit HC is set in the path through which the heat medium flows with respect to the heater core.
  • the control device 300 appropriately determines the operating state of various devices during parallel dehumidification and heating by using the detection signal of the air conditioning sensor group 301 and the operation signal of the operation panel 302. For example, as shown in FIG. 23, the control device 300 controls the third expansion valve 39 to the fully closed state and controls each of the first expansion valve 33 and the second expansion valve 35 to the throttle state. Further, the control device 300 controls the first bypass valve 44 and the second bypass valve 37 in an open state. The control device 300 appropriately determines control signals for other devices such as the compressor 31, fans 341, and 361 by using the detection signals of the air conditioning sensor group 301 and the operation signals of the operation panel 302.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the condenser 32 during parallel dehumidification and heating.
  • the heat medium flowing through the heater circuit HC flows to the heater core, so that the refrigerant flowing into the condenser 32 is dissipated to the air blown into the vehicle interior through the heater core.
  • air heated to a desired temperature by the heater core is blown out into the vehicle interior.
  • the refrigerant flowing into the first expansion valve 33 is depressurized by the first expansion valve 33 until a desired pressure is reached.
  • the refrigerant decompressed by the first expansion valve 33 flows into the outdoor heat exchanger 34, absorbs heat from the outside air, and evaporates.
  • the refrigerant evaporated in the outdoor heat exchanger 34 flows into the accumulator ACC via the second bypass flow path 38 and the refrigerant confluence portion 382 to separate the gas and liquid, and then the separated gas-rich refrigerant is transferred to the compressor 31. Inhaled.
  • the refrigerant flowing in the first bypass flow path 43 flows into the second expansion valve 35 and is depressurized in the second expansion valve 35 until a desired pressure is reached.
  • the refrigerant decompressed by the second expansion valve 35 flows into the cooling evaporator 36.
  • the refrigerant flowing into the cooling evaporator 36 absorbs heat from the air blown from the indoor fan 361 and evaporates. As a result, the air blown from the indoor fan 361 is cooled by the cooling evaporator 36 and dehumidified.
  • the air dehumidified by the cooling evaporator 36 is heated to a desired temperature by the heater core and then blown out into the vehicle interior.
  • the refrigerant that has passed through the cooling evaporator 36 flows into the accumulator ACC to separate the gas and liquid, and then the separated gas-rich refrigerant is sucked into the compressor 31.
  • the refrigerant sucked into the compressor 31 is compressed by the compressor 31 until it becomes a high-pressure refrigerant again.
  • the air dehumidified by the cooling evaporator 36 is heated by the heater core and then blown out into the vehicle interior to realize indoor dehumidification and heating.
  • the equipment cooling is an operation mode in which the equipment to be cooled is cooled to a desired temperature while blowing air cooled to a desired temperature by the cooling evaporator 36 into the vehicle interior.
  • the equipment cooling is executed by the refrigeration cycle device 30 when the temperature of the equipment to be cooled exceeds an appropriate temperature, for example, in a state where the operation mode is set to the cooling mode by the operation mode changeover switch.
  • the flow of the heat medium in the heater circuit HC is stopped.
  • the control device 300 appropriately determines the operating state of various devices when the device is cooled by using the air conditioning sensor group 301, the detection signal of the device cooling sensor 303, and the operation signal of the operation panel 302. For example, in the control device 300, as shown in FIG. 23, the expansion valves 33, 35, 39 so that the first expansion valve 33 is in the fully open state and the second expansion valve 35 and the third expansion valve 39 are in the throttle state. To control. Further, the control device 300 controls the first bypass valve 44 and the second bypass valve 37 in the closed state. The control device 300 appropriately determines control signals for other devices such as the compressor 31, fans 341, and 361 by using the detection signals of the air conditioning sensor group 301 and the operation signals of the operation panel 302.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the condenser 32 when the equipment is cooled. Since the heat medium does not flow in the heater circuit HC when the equipment is cooled, the refrigerant flowing into the condenser 32 flows into the first expansion valve 33 with almost no heat dissipation.
  • the refrigerant flowing into the first expansion valve 33 flows into the outdoor heat exchanger 34 with almost no decompression.
  • the refrigerant flowing into the outdoor heat exchanger 34 dissipates heat to the outside air and condenses.
  • the second expansion valve 35 and the third expansion valve 39 are in the throttled state, so that the refrigerant that has passed through the outdoor heat exchanger 34 flows into the second expansion valve 35 and the third expansion valve 39, respectively.
  • the refrigerant flowing into the second expansion valve 35 is depressurized by the second expansion valve 35 until it reaches a desired pressure.
  • the refrigerant decompressed by the second expansion valve 35 flows into the cooling evaporator 36.
  • the refrigerant flowing into the cooling evaporator 36 absorbs heat from the air blown from the indoor fan 361 and evaporates. Air cooled to a desired temperature by the cooling evaporator 36 is blown into the vehicle interior.
  • the refrigerant decompressed by the third expansion valve 39 flows into the equipment evaporator 40.
  • the refrigerant flowing into the equipment evaporator 40 absorbs heat from the heat medium flowing through the cooling circuit LC and evaporates.
  • the equipment to be cooled is cooled by the heat medium cooled by the equipment evaporator 40.
  • the refrigerant that has passed through the cooling evaporator 36 and the equipment evaporator 40 is gas-liquid separated by the accumulator ACC and then sucked into the compressor 31.
  • the refrigerant sucked into the compressor 31 is compressed by the compressor 31 until it becomes a high-pressure refrigerant again.
  • the air cooled by the cooling evaporator 36 is blown into the vehicle interior, and the equipment to be cooled is cooled by the heat medium cooled by the equipment evaporator 40.
  • the high-pressure points in the refrigeration cycle device 30 are the high-pressure region HPA1 from the refrigerant discharge side of the compressor 31 to the refrigerant inlet side of the first expansion valve 33, and the refrigerant of the first bypass valve 44 from the refrigerant discharge side of the compressor 31. It contains the high pressure region HPA2 up to the inlet side. Further, the low pressure portion in the refrigeration cycle device 30 includes a low pressure region LPA from the refrigerant confluence portion 382 to the refrigerant suction side of the compressor 31.
  • the integrated valve VD integrates the body portion BP and the circuit board CB in the expansion valves 33, 35, and 39, respectively.
  • the body portion BP forms the outer shell of each expansion valve 33, 35, 39.
  • the body portion BP is, for example, a metal block made of an aluminum alloy that has been drilled or the like. As shown in FIGS. 26 and 27, the body portion BP is formed with a first internal flow path 331, a second internal flow path 351 and a third internal flow path 391.
  • the first internal flow path 331 is a refrigerant flow path that constitutes a part of the first expansion valve 33, and the refrigerant that has passed through the condenser 32 passes through the first internal flow path 331.
  • the second internal flow path 351 is a refrigerant flow path that constitutes a part of the second expansion valve 35, and the refrigerant that has passed through the outdoor heat exchanger 34 passes through the second internal flow path 351.
  • the third internal flow path 391 is a refrigerant flow path that constitutes a part of the third expansion valve 39, and the refrigerant that has passed through the outdoor heat exchanger 34 passes through the third internal flow path 391.
  • an inlet portion 330a and an outlet portion 330b of the first internal flow path 331, an outlet portion 350b of the second internal flow path 351 and an outlet portion of the third internal flow path 391 are provided on the front surface of the body portion BP.
  • 390b is formed on the front surface of the body portion BP.
  • the body portion BP is formed with three through holes 330j, 350j, 390j penetrating from the front surface to the back surface of the body portion BP, and three bottomed holes 330k, 350k, 390k extending downward from the upper surface. Has been done.
  • the three through holes 330j, 350j, 390j extend in the horizontal direction.
  • the three bottomed holes 330k, 350k, and 390k extend in the vertical DR.
  • the three through holes 330j, 350j, 390j and the three bottomed holes 330k, 350k, and 390k are formed at different positions in the body portion BP in the direction orthogonal to the valve axial direction DRax.
  • the valve axis direction DRax is a direction in which the valve portions of the main valves 332, 352, and 392 of the expansion valves 33, 35, and 39 are displaced.
  • the displacement directions of the valve portions of the main valves 332, 352, and 392 of the expansion valves 33, 35, and 39 are the same.
  • the valve axial direction DRax is different for the expansion valves 33, 35, and 39.
  • the integrated valve VD includes a plurality of valve units UT1, UT2, UT3 in which the pressure control unit 337, 357, 397 and the valve bodies 332a, 352a, 392a are a set.
  • the integrated valve VD includes a first valve unit UT1, a second valve unit UT2, and a third valve unit UT3.
  • the first valve unit UT1 is a valve unit that includes a pressure control unit 337 of the first expansion valve 33 and a valve body 332a as a set.
  • the main valve 332 is arranged in the through hole 330j, and the pressure control unit 337 is arranged in the bottomed hole 330k.
  • the valve body 332a and the pressure control unit 337 of the first expansion valve 33 are arranged at different positions in the direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 337 of the first expansion valve 33 is arranged offset with respect to the valve body 332a of the first expansion valve 33 in a direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 337 is arranged at a position overlapping the throttle unit 333a in a direction orthogonal to the valve axis direction DRax. As a result, the physique of the first valve unit UT1 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the main valve 332 and the pressure control unit 337 of the first expansion valve 33 are configured in the same manner as in the second embodiment. This also applies to the second expansion valve 35 and the third expansion valve 39.
  • the second valve unit UT2 is a valve unit that includes the pressure control unit 357 of the second expansion valve 35 and the valve body 352a as a set.
  • the main valve 352 is arranged in the through hole 350j, and the pressure control unit 357 is arranged in the bottomed hole 350k.
  • the valve body 352a and the pressure control unit 357 of the second expansion valve 35 are arranged at different positions in the direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 357 of the second expansion valve 35 is arranged offset with respect to the valve body 352a of the second expansion valve 35 in a direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 357 is arranged at a position overlapping the throttle unit 353a in a direction orthogonal to the valve axis direction DRax. As a result, the physique of the second valve unit UT2 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the third valve unit UT3 is a valve unit that includes the pressure control unit 397 of the third expansion valve 39 and the valve body 392a as a set.
  • the main valve 392 is arranged in the through hole 390j, and the pressure control unit 397 is arranged in the bottomed hole 390k.
  • the valve body 392a and the pressure control unit 397 of the third expansion valve 39 are arranged at different positions in the direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 397 of the third expansion valve 39 is arranged offset with respect to the valve body 392a of the third expansion valve 39 in a direction orthogonal to the valve axial direction DRax.
  • the pressure control unit 397 is arranged at a position overlapping the throttle unit 393a in a direction orthogonal to the valve axis direction DRax. As a result, the physique of the third valve unit UT3 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the main valve 392 of the third expansion valve 39 includes a valve body 392a, a support portion 392b, a first spring 392c, a second spring 392d, an adjusting screw 392e, an operating rod 392f, and a stopper 392g. It has a partition portion 392h and a cap 392i.
  • valve body 392a, the support portion 392b, and the first spring 392c are housed in a valve chamber 393 provided in the middle of the internal flow path 391.
  • the valve chamber 393 is provided with a throttle portion 393a, and a valve seat 393b of the valve body 392a is formed.
  • the second spring 392d is arranged in the control chamber 394.
  • a refrigerant pressure-adjusted by the pressure control unit 397 of the third expansion valve 39 is introduced into the control chamber 394 as a driving fluid. Since the other components of the main valve 392 are the same as those of the main valves 332 and 352 described in the first and second embodiments, detailed description thereof will be omitted.
  • the pressure control unit 397 of the third expansion valve 39 is composed of the valve module Z0. Since the valve module Z0 is the same as that described in the second embodiment, the description thereof will be omitted.
  • the body portion BP is formed with a first pressure introduction path Lp1 for communicating the second flow path Z23 of the pressure control unit 397 of the third expansion valve 39 with the control chamber 394.
  • the body portion BP has a first pressure introduction path for communicating the second flow path Z23 of the pressure control unit 337 of the first expansion valve 33 and the control chamber 334, and the pressure control unit 357 of the second expansion valve 35.
  • a first pressure introduction path is formed to communicate the second flow path Z23 and the control chamber 354.
  • the body portion BP has a high pressure flow path L1 through which a high pressure refrigerant having a pressure equivalent to that of the refrigerant discharged from the compressor 31 flows, and a pressure equivalent to that of the refrigerant sucked into the compressor 31.
  • the high pressure flow path L1 is connected to a high pressure point in the cycle (for example, the discharge refrigerant flow path 311) via a capillary tube (not shown). Further, the high pressure flow path L1 is connected to the first flow path Z22 of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39 via the second pressure introduction path Lp2 formed in the body portion BP. ing. As a result, the pressure of the high-pressure refrigerant is introduced into the first flow path Z22 of each expansion valve 33, 35, 39. In the present embodiment, the high pressure flow path L1 and the second pressure introduction path Lp2 form a high pressure connection flow path.
  • the high pressure flow path L1 constitutes a single high pressure common portion connected to the high pressure point, and the second pressure introduction path Lp2 controls the pressure of the valve units UT1, UT2, and UT3 for the high pressure refrigerant flowing through the high pressure flow path L1. It constitutes a high-voltage distribution unit leading to units 337, 357, and 397.
  • the low pressure flow path L2 is connected to a low pressure point in the cycle (for example, the suction refrigerant flow path 312) via a capillary tube (not shown). Further, the low pressure flow path L2 is connected to the third flow path Z24 of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39 via the third pressure introduction path Lp3 formed in the body portion BP. ing. As a result, the pressure of the low-pressure refrigerant is introduced into the third flow path Z24 of each expansion valve 33, 35, 39. In the present embodiment, the low pressure flow path L2 and the third pressure introduction path Lp3 form a low pressure connection flow path.
  • the low pressure flow path L2 constitutes a single low pressure common portion connected to the low pressure point
  • the third pressure introduction path Lp3 controls the pressure of each valve unit UT1, UT2, UT3 for the low pressure refrigerant flowing through the low pressure flow path L2. It constitutes a low-pressure distribution section leading to sections 337, 357, and 397.
  • terminals Z6 and Z7 of the pressure control units 337, 357 and 397 of the expansion valves 33, 35 and 39 are connected to one circuit board CB.
  • the drive circuits of the pressure control units 337, 357, and 397 of the expansion valves 33, 35, and 39 are mounted on the circuit board CB.
  • the circuit board CB has a posture in which the plate surface extends along the alignment direction of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39, and is attached to the terminals Z6, Z7 of the pressure control units 337, 357, 397. It is connected.
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effects as those of the first embodiment and the second embodiment, which are the same or the same as those of the first embodiment and the second embodiment.
  • each expansion valve 33, 35, 39 is integrated as one integrated valve VD. That is, the three valve units UT1, UT2, and UT3 that set the valve bodies 332a, 352a, 392a of the expansion valves 33, 35, 39 and the pressure control units 337, 357, 397 as one set are for a single body unit BP. It is provided. In this way, if a plurality of valve units UT1, UT2, and UT3 are provided for a single body portion BP, the cycle is compared with the case where the plurality of valve units UT1, UT2, and UT3 are separately configured. The configuration can be simplified.
  • the integrated valve VD a part of the high pressure connection flow path and a part of the low pressure connection flow path are shared by the valve units UT1, UT2, and UT3. That is, in the integrated valve VD, the high pressure flow path L1 constituting the high pressure connection flow path and the low pressure flow path L2 constituting the low pressure connection flow path are shared by the valve units UT1, UT2, and UT3. According to this, the integrated valve VD can be simply realized as compared with the case where the high pressure connection flow path and the low pressure connection flow path are individually provided corresponding to the plurality of valve units UT1, UT2, and UT3.
  • the pressure control units 337, 357, and 397 of the valve units UT1, UT2, and UT3 are arranged so as not to overlap with the main valves 332, 352, and 392 in the valve axial direction DRax. That is, the pressure control units 337, 357, and 397 of the valve units UT1, UT2, and UT3 are arranged at positions shifted in the direction orthogonal to the valve axial direction DRax with respect to the positions where the main valves 332, 352, and 392 are arranged. Has been done.
  • the high-pressure flow path L1 of the integrated valve VD is connected to the discharge refrigerant flow path 311 and the low-pressure flow path L2 is connected to the intake refrigerant flow path 312. Not limited to this.
  • the high pressure flow path L1 is connected to the high pressure region HPA1 and HPA2 other than the discharge refrigerant flow path 311, or the low pressure flow path L2 is connected to the low pressure region LPA other than the suction refrigerant flow path 312. You may.
  • the pressure control units 337, 357, and 397 of the valve units UT1, UT2, and UT3 are arranged so as not to overlap with the main valves 332, 352, and 392 in the valve axial DRax.
  • the integrated valve VD is not limited to this. In the integrated valve VD, for example, among the valve units UT1, UT2, and UT3, some pressure control units 337, 357, and 397 are arranged so as not to overlap with the main valves 332, 352, and 392 in the valve axial DRax. May be.
  • the expansion valves 33, 35, and 39 are integrated, but the integrated valve VD is not limited to this, and other devices such as the bypass valve 37 are integrated. A part of each expansion valve 33, 35, 39 may be integrated.
  • the drive circuits of the expansion valves 33, 35, and 39 are mounted on a common circuit board CB, but the present invention is not limited to this, and for example, the expansion valves 33, The drive circuits 35 and 39 may be mounted on different boards.
  • the pressure control units 337, 357, 397 and the main valves 332, 352, 392 of the expansion valves 33, 35, 39 are exemplified, but each expansion is made substantially the same.
  • the valves 33, 35 and 39 are not limited to this.
  • Each expansion valve 33, 35, 39 may have a structure in which at least a part of the pressure control unit 337, 357, 397 and the main valves 332, 352, 392 is different.
  • the circuit board CB is connected to the pressure control unit 337, 357, 397 in a posture in which the plate surface of the circuit board CB extends along the horizontal direction, but the present invention is not limited to this.
  • the circuit board CB may be connected to the pressure control unit 337, 357, 397 in a posture in which the plate surfaces intersect with each other in the horizontal direction.
  • the equipment cooling is not limited to this, and may be executed during indoor heating or dehumidifying heating. Further, the equipment cooling may be performed in a situation where the room is not air-conditioned. This also applies to the subsequent embodiments.
  • the integrated valve VD integrates the body portion BP and the circuit board CB in each of the expansion valves 33, 35, and 39.
  • the body portion BP is formed with a first internal flow path 331, a second internal flow path 351 and a third internal flow path 391.
  • an inlet portion 330a and an outlet portion 330b of the first internal flow path 331, an outlet portion 350b of the second internal flow path 351 and an outlet portion 390b of the third internal flow path 391 are formed.
  • an inlet portion 350a of the second internal flow path 351 and an inlet portion 390a of the third internal flow path 391 are formed on the back surface of the body portion BP.
  • the body portion BP is formed with three through holes 330j, 350j and 390j penetrating from the upper surface to the lower surface of the body portion BP.
  • the three through holes 330j, 350j, and 390j extend in the vertical DR.
  • the integrated valve VD includes a first valve unit UT1, a second valve unit UT2, and a third valve unit UT3.
  • the first valve unit UT1 is a valve unit that includes a pressure control unit 337 of the first expansion valve 33 and a valve body 332a as a set.
  • the main valve 332 and the pressure control unit 337 are arranged side by side in the valve axial direction DRax in the through hole 330j. As a result, the physique of the first valve unit UT1 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the lower portion including the valve body 332a is inserted from the lower opening of the through hole 330j, and the upper portion of the valve body 332a is inserted from the upper opening of the through hole 330j together with the pressure control unit 337. It has been inserted.
  • the main valve 332 of the first expansion valve 33 is configured in the same manner as in the second embodiment. This also applies to the second expansion valve 35 and the third expansion valve 39.
  • the second valve unit UT2 is a valve unit that includes the pressure control unit 357 of the second expansion valve 35 and the valve body 352a as a set.
  • the main valve 352 and the pressure control unit 357 are arranged side by side in the valve axial direction DRax in the through hole 350j.
  • the physique of the second valve unit UT2 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the second valve unit UT2 has a lower portion inserted through the lower opening of the through hole 350j and an upper portion inserted through the upper opening of the through hole 350j, similarly to the first valve unit UT1.
  • the third valve unit UT3 is a valve unit that includes the pressure control unit 397 of the third expansion valve 39 and the valve body 392a as a set.
  • the main valve 392 and the pressure control unit 397 are arranged side by side in the valve axial direction DRax in the through hole 390i.
  • the physique of the third valve unit UT3 in the direction orthogonal to the valve axis direction DRax is suppressed.
  • the third valve unit UT3 has a lower portion inserted through the lower opening of the through hole 390j and an upper portion inserted through the upper opening of the through hole 390j, similarly to the first valve unit UT1.
  • the pressure control unit 337, 357, 397 valves with respect to the position where the valve bodies 332a, 352a, 392a are arranged so as to overlap the valve bodies 332a, 352a, 392a in the valve axial DRax. It is arranged at a position deviated from the axial DRax.
  • the first refrigerant hole Z16 faces the opening of the first flow path Z22
  • the second refrigerant hole Z17 faces the second flow path Z23
  • the third refrigerant hole Z18 faces the third. It is arranged inside the recess Z21 so as to face the opening of the flow path Z24.
  • the first refrigerant hole Z16 communicates with the first flow path Z22
  • the second refrigerant hole Z17 communicates with the second flow path Z23
  • the third refrigerant hole Z18 communicates with the third flow path Z24. Communicate.
  • the first flow path Z22 of the pressure control unit 337, 357, 397 communicates with the control chamber 334, 354, 394 via the first pressure introduction path Lp1 formed in the caps 332i, 352i, 392i.
  • the pressure of the drive fluid adjusted by the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39 is introduced into the control chambers 334, 354, 394 of the expansion valves 33, 35, 39. ..
  • the high pressure flow path L1 through which the high pressure refrigerant having the same pressure as the refrigerant discharged from the compressor 31 flows, and the low pressure through which the low pressure refrigerant having the same pressure as the refrigerant sucked into the compressor 31 flows.
  • the flow path L2 is formed.
  • the high pressure flow path L1 is connected to a high pressure point in the cycle. Specifically, the high-pressure flow path L1 is connected to a portion of the first internal flow path 331 located on the upstream side of the refrigerant flow with respect to the valve body 332a of the first expansion valve 33. Further, the high pressure flow path L1 is connected to the second flow path Z23 of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39 via the second pressure introduction path Lp2 formed in the body portion BP. ing. As a result, the pressure of the high-pressure refrigerant is introduced into the second flow path Z23 of each expansion valve 33, 35, 39.
  • the high pressure flow path L1 and the second pressure introduction path Lp2 form a high pressure connection flow path.
  • the high pressure flow path L1 constitutes a single high pressure common portion connected to the high pressure point, and the second pressure introduction path Lp2 controls the pressure of the valve units UT1, UT2, and UT3 for the high pressure refrigerant flowing through the high pressure flow path L1. It constitutes a high-voltage distribution unit leading to units 337, 357, and 397.
  • the low pressure flow path L2 is connected to the low pressure point in the cycle. Specifically, the low-pressure flow path L2 is connected to a portion of the second internal flow path 351 located on the downstream side of the refrigerant flow with respect to the valve body 352a of the second expansion valve 35. Further, the low pressure flow path L2 is connected to the third flow path Z24 of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39 via the third pressure introduction path Lp3 formed in the body portion BP. ing. As a result, the pressure of the low-pressure refrigerant is introduced into the third flow path Z24 of each expansion valve 33, 35, 39.
  • the low pressure flow path L2 and the third pressure introduction path Lp3 form a low pressure connection flow path.
  • the low pressure flow path L2 constitutes a single low pressure common portion connected to the low pressure point
  • the third pressure introduction path Lp3 controls the pressure of each valve unit UT1, UT2, UT3 for the low pressure refrigerant flowing through the low pressure flow path L2. It constitutes a low-pressure distribution section leading to sections 337, 357, and 397.
  • terminals Z6 and Z7 of the pressure control units 337, 357 and 397 of the expansion valves 33, 35 and 39 are connected to one circuit board CB.
  • the drive circuits of the pressure control units 337, 357, and 397 of the expansion valves 33, 35, and 39 are mounted on the circuit board CB.
  • the circuit board CB has a posture in which the plate surface extends along the alignment direction of the pressure control units 337, 357, 397 of the expansion valves 33, 35, 39, and is attached to the terminals Z6, Z7 of the pressure control units 337, 357, 397. It is connected.
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effect as that of the third embodiment from the same configuration as that of the third embodiment or the equivalent configuration.
  • the pressure control unit 337, 357, 397 and the valve bodies 332a, 352a, and 392a are arranged so as to overlap each other in the valve axis direction DRax. .. That is, in each valve unit UT1, UT2, UT3, the pressure control unit 337, 357, 397 is arranged at a position deviated from the position where the valve bodies 332a, 352a, 392a are arranged in the valve axial direction DRax.
  • each valve unit UT1, UT2, UT3 and a pressure control unit 337, 357, 397 are arranged in three through holes 330j, 350j, 390j extending vertically in the body portion BP. According to this, since it becomes easy to manufacture a molding mold for molding the body portion BP, it is possible to reduce the manufacturing cost of the integrated valve VD.
  • the refrigeration cycle device 30 of the present embodiment has a first expansion valve 33, an outdoor heat exchanger 34, a second bypass valve 37, a second bypass flow path 38, a first bypass flow path 43, and a first. 1 Bypass valve 44 and the like have been abolished.
  • the condenser 32 has a condensing unit 321a, a liquid receiving unit 321b, and a supercooling unit 321c.
  • the condensing unit 321a condenses by exchanging heat between the high-pressure refrigerant and the heat medium flowing through the heater circuit HC.
  • the liquid receiving unit 321b separates the gas and liquid of the refrigerant that has passed through the condensing unit 321a, and stores the separated liquid phase refrigerant as a surplus refrigerant in the cycle.
  • the supercooling unit 321c supercools the liquid phase refrigerant stored in the liquid receiving unit 321b by dissipating heat to a high-temperature heat medium before flowing into the condensing unit 321a.
  • the heater circuit HC is a circuit that circulates a high-temperature heat medium.
  • a pump WP, an electric heater EH, a heater core HX, a radiator OHX, a flow rate adjusting valve FR, and the like are arranged in the heater circuit HC.
  • the pump WP pumps a heat medium to the condenser 32 in the heater circuit HC.
  • the electric heater EH is an auxiliary heat source for heating the heat medium.
  • the heater core HX warms the blown air blown into the vehicle interior by using the refrigerant discharged from the compressor 11 as a heat source.
  • the radiator OHX is an outdoor heat exchanger that dissipates heat from a high-pressure refrigerant to the outside air via a heat medium.
  • the flow rate adjusting valve FR adjusts the flow rate of the heat medium through which the radiator OHX is passed.
  • the flow rate adjusting valve FR can change the usage mode of the high pressure refrigerant by adjusting the flow rate as described above.
  • the heater circuit HC can release the heat of the heat medium to the outside air by increasing the flow rate of the heat medium flowing into the radiator OHX by the flow rate adjusting valve FR. Further, the heater circuit HC can heat the vehicle interior by using the heat of the heat medium for heating the blown air by reducing the flow rate of the heat medium flowing into the radiator OHX.
  • the flow path on the refrigerant outlet side of the condenser 32 is bifurcated by the refrigerant branch portion 46a, the second expansion valve 35 and the cooling evaporator 36 are arranged in one flow path, and the other flow path is the second. 3
  • the expansion valve 39 and the equipment evaporator 40 are arranged.
  • the refrigerant outlet side of the cooling evaporator 36 and the refrigerant outlet side of the equipment evaporator 40 are merged by the refrigerant merging portion 46b.
  • the equipment evaporator 40 evaporates the refrigerant by exchanging heat between the refrigerant that has passed through the third expansion valve 39 and the heat medium that flows through the cooling circuit LC.
  • the cooling circuit LC is a circuit for utilizing the latent heat of vaporization of the refrigerant as a cooling heat source for cooling the equipment to be cooled.
  • the cooling circuit LC is provided with an outdoor heat exchanger that exchanges heat with the outside air for the heat medium.
  • the refrigerating cycle device 30 can absorb heat from the outside air via the heat medium flowing through the cooling circuit LC during indoor heating.
  • the refrigerating cycle device 30 configured in this way appropriately switches the operation mode of the refrigerating cycle device 30 by receiving inputs from the air conditioning sensor group 301, the operation panel 302, and the equipment cooling sensor 303.
  • the control device 300 switches the operation mode of the refrigeration cycle device 30 by controlling the expansion valves 35, 39 and the like to change the flow method of the refrigerant in the refrigeration cycle device 30.
  • the control device 300 controls the third expansion valve 39 to the fully closed state and the second expansion valve 35 to the throttle state during indoor cooling.
  • the control device 300 controls the second expansion valve 35 to be in a fully closed state and controls the third expansion valve 39 to be in a throttled state during indoor heating.
  • control device 300 controls each of the second expansion valve 35 and the third expansion valve 39 to the throttled state when the equipment is cooled.
  • the control device 300 increases the flow rate of the heat medium flowing into the radiator OHX by the flow rate adjusting valve FR during indoor cooling, and dissipates the heat medium flowing through the heater circuit HC to the outside air.
  • control device 300 reduces the flow rate of the heat medium flowing into the radiator OHX by the flow rate adjusting valve FR during indoor heating, and dissipates the heat medium flowing through the heater circuit HC to the blown air.
  • the high-pressure points are from the refrigerant discharge side of the compressor 31 to the refrigerant inlet side of the third expansion valve 39.
  • the low pressure portion in the refrigeration cycle device 30 includes a low pressure region LPA from the refrigerant confluence portion 46b to the refrigerant suction side of the compressor 31.
  • the second expansion valve 35 and the third expansion valve 39 of the present embodiment are configured as one integrated valve VD in which some parts are integrated.
  • This integrated valve VD excludes the first expansion valve 33 and the like from those described in the third embodiment and the fourth embodiment, connects the high pressure flow path L1 to the high pressure regions HPA1 and HPA2, and connects the low pressure flow path L2 to the low pressure. This can be achieved by connecting to the region LPA.
  • the integrated valve VD constitutes the valve device of the present disclosure.
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effect as that of the third embodiment from the same configuration as that of the third embodiment or the equivalent configuration.
  • the first three-way joint 47a is connected to the refrigerant outlet side of the condenser 12.
  • the inlet side of the liquid receiving portion 49 is connected to one of the outlets of the first three-way joint 47a via the first on-off valve 48a and the fifth three-way joint 47e.
  • a first expansion valve 33 is connected to the other outlet of the first three-way joint 47a via a second on-off valve 48b and a second three-way joint 47b.
  • one inflow port is connected to the outlet side of the second on-off valve 48b, and the other inflow port is connected to the outlet side of the liquid receiving portion 49.
  • a sixth three-way joint 47f and a first check valve 50a are arranged between the outlet of the liquid receiving portion 49 and the other inlet of the second three-way joint 47b.
  • the inflow port of the sixth three-way joint 47f is connected to the refrigerant outlet side of the liquid receiving portion 49.
  • One of the outlets of the sixth three-way joint 47f is connected to the inlet side of the first check valve 50a.
  • the inlet side of the 7th three-way joint 47g is connected to the other outlet of the sixth three-way joint 47f.
  • the refrigerant inlet side of the outdoor heat exchanger 34 is connected to the outlet of the second three-way joint 47b via the first expansion valve 33.
  • the first expansion valve 33 is a first pressure reducing unit that reduces the pressure of the refrigerant flowing out of the liquid receiving unit 49 during indoor heating.
  • the outdoor heat exchanger 34 is a heat exchanger that exchanges heat between the refrigerant flowing out from the first expansion valve 33 and the outside air.
  • the inlet side of the third three-way joint 47c is connected to the refrigerant outlet of the outdoor heat exchanger 34.
  • One inflow port side of the fourth three-way joint 47d is connected to one outflow port of the third three-way joint 47c via a third on-off valve 48c.
  • the other inlet side of the fifth three-way joint 47e is connected to the other outlet of the third three-way joint 47c via the second check valve 50b.
  • the refrigerant suction port side of the compressor 31 is connected to the outlet of the fourth three-way joint 47d.
  • the inlet side of the 7th three-way joint 47g is connected to the other outlet of the sixth three-way joint 47f via the liquid receiving portion 49.
  • the inlet side of the second expansion valve 35 is connected to one of the outlets of the seventh three-way joint 47g.
  • the inlet side of the third expansion valve 39 is connected to the other outlet of the seventh three-way joint 47 g.
  • a cooling evaporator 36 is connected to the refrigerant outlet side of the second expansion valve 35.
  • One inflow port of the eighth three-way joint 47h is connected to the refrigerant outlet side of the cooling evaporator 36.
  • An equipment evaporator 40 is connected to the refrigerant outlet side of the third expansion valve 39.
  • the other inlet of the eighth three-way joint 47h is connected to the refrigerant outlet side of the equipment evaporator 40.
  • the refrigerant suction port side of the compressor 31 is connected to the outlet of the eighth three-way joint 47h via the fourth three-way joint 47d.
  • the first expansion valve 33 constitutes the first pressure reducing unit
  • the second expansion valve 35 and the third expansion valve 39 form the second pressure reducing unit
  • the cooling evaporator 36 and the equipment evaporator 40 constitute an evaporation unit
  • the fourth three-way joint 47d constitutes a refrigerant confluence portion that joins the refrigerant flow downstream side of the outdoor heat exchanger 34 and the refrigerant flow downstream side of the cooling evaporator 36 and the equipment evaporator 40.
  • the first on-off valve 48a, the second on-off valve 48b, and the third on-off valve 48c form a flow path switching portion for switching the refrigerant circuit in the cycle.
  • the refrigerating cycle device 30 configured in this way appropriately switches the operation mode of the refrigerating cycle device 30 by receiving inputs from the air conditioning sensor group 301, the operation panel 302, and the equipment cooling sensor 303.
  • the operation during indoor heating, indoor cooling, dehumidifying heating, and equipment cooling will be described.
  • the control device 300 opens the first on-off valve 48a, closes the second on-off valve 48b, and opens the third on-off valve 48c during indoor heating. Further, the control device 300 controls the first expansion valve 33 to the throttled state, and controls the second expansion valve 35 and the third expansion valve 39 to the fully closed state. As a result, the refrigerating cycle device 30 switches to the first circuit in which the refrigerant discharged from the compressor 31 flows in the order of the condenser 32 ⁇ the liquid receiving unit 49 ⁇ the first expansion valve 33 ⁇ the outdoor heat exchanger 34 ⁇ the compressor 31. .. In this first circuit, the blown air heated by the heater core can be blown out into the vehicle interior. Since the second expansion valve 35 and the third expansion valve 39 are fully open during the room heating, there is almost no pressure difference between the second expansion valve 35 and the third expansion valve 39.
  • the control device 300 closes the first on-off valve 48a, opens the second on-off valve 48b, and closes the third on-off valve 48c during indoor cooling. Further, the control device 300 controls the first expansion valve 33 to the fully open state, the second expansion valve 35 to the throttle state, and the third expansion valve 39 to the fully closed state.
  • the refrigerating cycle device 30 the refrigerant discharged from the compressor 11 is condensed into a condenser 12 ⁇ a first expansion valve 33 ⁇ an outdoor heat exchanger 34 ⁇ a liquid receiving unit 49 ⁇ a second expansion valve 35 ⁇ a cooling evaporator 36.
  • the control device 300 opens the first on-off valve 48a, closes the second on-off valve 48b, and opens the third on-off valve 48c during dehumidifying and heating. Further, the control device 300 controls the first expansion valve 33 to the throttled state, the second expansion valve 35 to the throttled state, and the third expansion valve 39 to the fully closed state.
  • the refrigerant flowing in the order of the compressor 11 ⁇ the condenser 32 ⁇ the liquid receiving unit 19 flows in the order of the first expansion valve 33 ⁇ the outdoor heat exchanger 34 ⁇ the compressor 31, and the second. It switches to the third circuit that flows in the order of the expansion valve 35 ⁇ the cooling evaporator 36 ⁇ the compressor 31. In this third circuit, the blown air cooled and dehumidified by the cooling evaporator 36 can be reheated by the heater core and blown out into the vehicle interior.
  • the control device 300 closes the first on-off valve 48a, opens the second on-off valve 48b, and closes the third on-off valve 48c when the equipment is cooled. Further, the control device 300 controls the first expansion valve 33 to the fully open state, and controls the second expansion valve 35 and the third expansion valve 39 to the throttled state. As a result, in the refrigerating cycle device 30, the refrigerant flowing in the order of the compressor 11 ⁇ the condenser 12 ⁇ the first expansion valve 33 ⁇ the outdoor heat exchanger 34 ⁇ the liquid receiving unit 49 is transferred from the second expansion valve 35 ⁇ the cooling evaporator.
  • the circuit is switched to the flow in the order of the third expansion valve 39 ⁇ the evaporator 40 for equipment.
  • the equipment to be cooled can be cooled by the equipment evaporator 40 while blowing out the blown air cooled by the cooling evaporator 36 into the vehicle interior. Since the first expansion valve 33 is fully open during indoor cooling, there is almost no pressure difference between the front and rear of the first expansion valve 33.
  • the high-pressure points are the second expansion valve 35 and the third expansion from the refrigerant discharge side of the compressor 31. It includes a second high pressure region HPA2 up to the refrigerant inlet side of the valve 39.
  • the low-pressure portion includes a low-pressure region LPA from the fourth three-way joint 47d, which is the refrigerant confluence portion, to the refrigerant suction side of the compressor 31.
  • the first expansion valve 33, the second expansion valve 35, and the third expansion valve 39 of the present embodiment are configured as one integrated valve VD in which some parts are integrated.
  • the integrated valve VD connects the high pressure flow path L1 to the high pressure region HPA1 and HPA2, and connects the low pressure flow path L2 to the low pressure region LPA. It is possible to do so.
  • the integrated valve VD constitutes the valve device of the present disclosure.
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effect as that of the first embodiment from the same configuration as that of the first embodiment or the equivalent configuration.
  • the condenser 32 of the sixth embodiment is arranged between the compressor 31 and the first three-way joint 47a, but is not limited thereto.
  • the condenser 32 may be arranged, for example, between the first on-off valve 48a and the fifth three-way joint 47e, as shown in FIG. 33. Even with such a cycle configuration, it operates in the same manner as in the sixth embodiment, and the same effect as in the sixth embodiment can be obtained. That is, regardless of which operation mode the refrigerant circuit is switched to, the high-pressure liquid-phase refrigerant in the cycle can be stored in the liquid receiving unit 49 as a surplus refrigerant, so that the coefficient of performance can be improved.
  • the first expansion valve 33, the second expansion valve 35, and the third expansion valve 39 are configured as an integrated valve VD, but the present invention is not limited to this, and the first expansion valve 33 and the third expansion valve 39 are not limited to this.
  • the 2 expansion valve 35 and the 3rd expansion valve 39 may be configured separately.
  • the refrigeration cycle apparatus 30 of the present embodiment includes a compressor 31, a four-way valve 51, a first heat exchanger 52, a second heat exchanger 53, an expansion valve 33, and an accumulator ACC. ing.
  • the four-way valve 51 switches the flow direction of the refrigerant in the cycle in the opposite direction between the time of indoor cooling and the time of indoor heating.
  • the four-way valve 51 includes an introduction port 511 for introducing the refrigerant discharged from the compressor 31, and a take-out port 512 for leading the refrigerant to the refrigerant suction side of the compressor 31. Further, the four-way valve 51 includes a first communication port 513 communicating with the first heat exchanger 52 and a second communication port 514 communicating with the second heat exchanger 53.
  • the four-way valve 51 can be set to the first state in which the introduction port 511 communicates with the first communication port 513 and the take-out port 512 communicates with the second communication port 514. Further, the four-way valve 51 can be set to a second state in which the introduction port 511 communicates with the second communication port 514 and the out-licensing port 512 communicates with the first communication port 513. Specifically, the four-way valve 51 is set to the second state shown in FIG. 34 when the room is cooled, and is set to the first state shown in FIG. 35 when the room is heated.
  • the first heat exchanger 52 is a user-side heat exchanger arranged indoors.
  • the first heat exchanger 52 when the four-way valve 51 is set to the first state during indoor heating, the high-pressure refrigerant discharged from the compressor 31 flows into the first heat exchanger 52. As a result, indoor heating using the high-pressure refrigerant in the cycle is realized.
  • the refrigerant decompressed by the expansion valve 33 flows into the first heat exchanger 52. As a result, indoor cooling using the low-pressure refrigerant in the cycle is realized.
  • the second heat exchanger 53 is an outdoor heat exchanger arranged outdoors.
  • the refrigerant decompressed by the expansion valve 33 flows into the second heat exchanger 53.
  • the high-pressure refrigerant discharged from the compressor 31 flows into the second heat exchanger 53.
  • the expansion valve 33 is provided between the first heat exchanger 52 and the second heat exchanger 53, and reduces the pressure of the refrigerant that has passed through one of the heat exchangers of the first heat exchanger 52 and the second heat exchanger 53. At the same time, it is a decompression unit that causes the decompressed refrigerant to flow out toward the other heat exchanger. Specifically, the expansion valve 33 depressurizes the high-pressure refrigerant that has passed through the second heat exchanger 53 in the cooling mode. Further, the expansion valve 33 depressurizes the high-pressure refrigerant that has passed through the first heat exchanger 52 in the heating mode.
  • the refrigerating cycle device 30 configured in this way appropriately switches the operation mode of the refrigerating cycle device 30 by receiving inputs from the air conditioning sensor group 301 and the operation panel 302.
  • the operation of the indoor cooling and the indoor heating will be described.
  • the control device 300 switches the four-way valve 51 to the second state during indoor cooling.
  • the refrigerant discharged from the compressor 31 is the four-way valve 51 ⁇ the second heat exchanger 53 ⁇ the expansion valve 33 ⁇ the first heat exchanger 52 ⁇ the four-way valve 51 ⁇ the accumulator ACC ⁇ the compressor 31. It flows in the order of.
  • the blown air cooled by the first heat exchanger 52 can be blown into the vehicle interior.
  • the pressure on the second heat exchanger 53 side of the expansion valve 33 is higher than that on the first heat exchanger 52 side.
  • the control device 300 switches the four-way valve 51 to the first state when the room is heated.
  • the refrigerant discharged from the compressor 31 is the four-way valve 51 ⁇ the first heat exchanger 52 ⁇ the expansion valve 33 ⁇ the second heat exchanger 53 ⁇ the four-way valve 51 ⁇ the accumulator ACC ⁇ the compressor 31. It flows in the order of.
  • the blown air heated by the first heat exchanger 52 can be blown into the vehicle interior.
  • the pressure on the second heat exchanger 53 side of the expansion valve 33 is lower than that on the first heat exchanger 52 side. That is, the magnitude relation of the pressure before and after the expansion valve 33 is reversed between the time of indoor cooling and the time of indoor heating.
  • the high pressure point includes the high pressure region HPA from the refrigerant discharge side of the compressor 31 to the introduction port 511 of the four-way valve 51.
  • the low pressure portion includes a low pressure region LPA from the outlet port 512 of the four-way valve 51 to the refrigerant suction side of the compressor 31.
  • the expansion valve 33 of the present embodiment has the same configuration as that described in the first embodiment and the second embodiment, and the flow path corresponding to the high pressure flow path in the expansion valve 33 is connected to the high pressure region HPA. , It can be realized by connecting the flow path corresponding to the low pressure flow path to the low pressure region LPA.
  • the refrigerating cycle apparatus 30 of the present embodiment can obtain the same effect as that of the first embodiment from the same configuration as that of the first embodiment or the equivalent configuration.
  • the high-pressure refrigerant flowing through the discharge refrigerant flow path 311 is introduced into the pressure control unit 337, 357, 397, but the expansion valves 33, 35, and 39 are not limited thereto.
  • the high-pressure refrigerant flowing through the high-pressure region HPA other than the discharge refrigerant flow path 311 may be introduced into the pressure control unit 337, 357, 397.
  • the low pressure refrigerant flowing through the low pressure region LPA other than the suction refrigerant flow path 312 may be introduced into the pressure control unit 337, 357, 397.
  • the pressure control unit 337, 357, 397 may adjust the pressure in the control chamber 334, 354, 394 by using the output of, for example, an electric motor, a magnetic coupling, or the like.
  • each expansion valve 33, 35, 39 has a poppet type valve structure, but each expansion valve 33, 35, 39 has, for example, a spool type valve structure or a slide type. It may have a valve structure of.
  • the refrigerating cycle apparatus 30 has various circuits, but the refrigerating cycle apparatus 30 is not limited to this, and the refrigerating cycle apparatus 30 may have circuits other than those described above. Further, in the above-described embodiment, an example in which the refrigeration cycle device 30 is applied to a temperature control device mounted on an automobile has been described, but the refrigeration cycle device 30 can be applied to other than the temperature control device mounted on the automobile. be.
  • the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential or when they are clearly considered to be essential in principle.
  • the shape, positional relationship, etc. of a component or the like when the shape, positional relationship, etc. of a component or the like is referred to, the shape, positional relationship, etc. are not specified unless otherwise specified or limited in principle to a specific shape, positional relationship, etc. Not limited to, etc.
  • the controls and methods thereof of the present disclosure are realized in a dedicated computer provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program. May be good.
  • the control unit and the method thereof of the present disclosure may be realized by a dedicated computer provided by configuring a processor with one or more dedicated hardware logic circuits.
  • the control unit and its method of the present disclosure are composed of a combination of a processor and memory programmed to perform one or more functions and a processor composed of one or more hardware logic circuits. It may be realized by one or more dedicated computers.
  • the computer program may be stored in a computer-readable non-transitional tangible recording medium as an instruction executed by the computer.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

Un appareil à cycle de réfrigération (30) est pourvu d'un dispositif soupape (33, 35, 39, 54, VD) destiné à effectuer la réduction de pression et/ou le réglage de débit d'un fluide frigorigène s'écoulant dans un cycle. Le dispositif soupape comprend : une chambre de commande (334, 354, 394) dans laquelle est introduit un fluide moteur destiné à entraîner un corps de soupape ; et une partie de commande de pression (337, 357, 397) destinée à commander une pression dans la chambre de commande. Le dispositif soupape comprend un circuit d'écoulement de raccordement à haute pression (330g, 350g, L1, Lp2) communiquant avec un point à haute pression (HPA) à travers lequel un fluide frigorigène à haute pression circule dans le cycle dans, indifféremment, un mode d'utilisation d'énergie en chauffage ou un mode d'utilisation d'énergie en refroidissement. Le dispositif soupape comprend un circuit d'écoulement de raccordement à basse pression (330h, 350h, L2, Lp3) communiquant avec un point à basse pression (LPA) à travers lequel un fluide frigorigène à basse pression circule dans le cycle dans, indifféremment, un mode d'utilisation d'énergie en chauffage ou le mode d'utilisation d'énergie en refroidissement. La partie de commande de pression est raccordée au circuit d'écoulement de raccordement à haute pression et au circuit d'écoulement de raccordement à basse pression et commande la pression dans la chambre de commande par réglage d'un rapport d'introduction entre une quantité d'introduction du fluide frigorigène à haute pression et une quantité d'introduction du fluide frigorigène à basse pression par rapport à la chambre de commande.
PCT/JP2021/038243 2020-10-27 2021-10-15 Appareil à cycle de réfrigération WO2022091816A1 (fr)

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JP2020-179644 2020-10-27
JP2020179644A JP2022070536A (ja) 2020-10-27 2020-10-27 冷凍サイクル装置

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104344611A (zh) * 2013-08-08 2015-02-11 盾安环境技术有限公司 一种膨胀阀
US20150354875A1 (en) * 2013-06-25 2015-12-10 Zhejiang Dunan Hetian Metal Co., Ltd. On-Demand Micro Expansion Valve for a Refrigeration System
JP2018063108A (ja) * 2008-11-03 2018-04-19 アルケマ フランス 車両の加熱および／または空調方法
WO2020175545A1 (fr) * 2019-02-28 2020-09-03 株式会社デンソー Dispositif de vanne
WO2020175546A1 (fr) * 2019-02-28 2020-09-03 株式会社デンソー Dispositif à cycle de réfrigération, et vanne de réglage de pression d'évaporation
WO2020213537A1 (fr) * 2019-04-19 2020-10-22 株式会社デンソー Dispositif à cycle de réfrigération

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018063108A (ja) * 2008-11-03 2018-04-19 アルケマ フランス 車両の加熱および／または空調方法
US20150354875A1 (en) * 2013-06-25 2015-12-10 Zhejiang Dunan Hetian Metal Co., Ltd. On-Demand Micro Expansion Valve for a Refrigeration System
CN104344611A (zh) * 2013-08-08 2015-02-11 盾安环境技术有限公司 一种膨胀阀
WO2020175545A1 (fr) * 2019-02-28 2020-09-03 株式会社デンソー Dispositif de vanne
WO2020175546A1 (fr) * 2019-02-28 2020-09-03 株式会社デンソー Dispositif à cycle de réfrigération, et vanne de réglage de pression d'évaporation
WO2020213537A1 (fr) * 2019-04-19 2020-10-22 株式会社デンソー Dispositif à cycle de réfrigération

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