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WO2015111379A1 - Dispositif à cycle de congélation - Google Patents

Dispositif à cycle de congélation Download PDF

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Publication number
WO2015111379A1
WO2015111379A1 PCT/JP2015/000094 JP2015000094W WO2015111379A1 WO 2015111379 A1 WO2015111379 A1 WO 2015111379A1 JP 2015000094 W JP2015000094 W JP 2015000094W WO 2015111379 A1 WO2015111379 A1 WO 2015111379A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
compressor
air
evaporation pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/000094
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English (en)
Japanese (ja)
Inventor
桑原　幹治
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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Filing date
Publication date
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Publication of WO2015111379A1 publication Critical patent/WO2015111379A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00485—Valves for air-conditioning devices, e.g. thermostatic 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
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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

  • the present disclosure relates to a refrigeration cycle apparatus including an evaporation pressure adjustment valve.
  • a vapor compression type refrigeration cycle apparatus that cools blown air blown into a passenger compartment of a vehicle air conditioner that includes an evaporation pressure adjusting valve.
  • This type of evaporation pressure regulating valve is configured to reduce the refrigerant evaporation pressure (refrigerant evaporation) in the indoor evaporator in order to suppress frosting (frost) of the indoor evaporator that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant and the blown air.
  • the temperature is maintained at a predetermined reference evaporation pressure (reference evaporation temperature) or higher.
  • Patent Document 1 discloses an evaporation pressure adjusting valve that increases a valve opening (refrigerant passage area) with an increase in the flow rate of refrigerant flowing through an indoor evaporator. More specifically, the evaporating pressure adjusting valve of Patent Document 1 is connected to the refrigerant outlet side of the indoor evaporator to increase the flow rate of refrigerant flowing through the indoor evaporator (the flow rate of refrigerant flowing through the evaporating pressure adjusting valve). The set pressure increases in proportion to the accompanying increase in the displacement of the valve body.
  • the reference evaporation temperature is a constant determined to be higher than 0 ° C. in order to suppress frost formation (frost) of the indoor evaporator.
  • the set pressure of the evaporating pressure adjusting valve is the refrigerant pressure on the inlet side of the evaporating pressure adjusting valve when the evaporating pressure adjusting valve in the fully opened state starts to reduce the refrigerant passage area (refrigerant evaporation in the indoor evaporator). Pressure), which varies depending on the flow rate of the refrigerant flowing through the evaporation pressure regulating valve.
  • Patent Document 2 in addition to the indoor evaporator and the evaporation pressure regulating valve, an indoor condenser for exchanging heat between the high-pressure refrigerant discharged from the compressor and the blown air after passing through the indoor evaporator, and the indoor evaporator
  • a refrigeration cycle apparatus includes an outdoor heat exchanger in which refrigerant flows are connected in parallel to exchange heat between low-pressure refrigerant and outside air to evaporate the low-pressure refrigerant.
  • the refrigerant evaporating pressure in the outdoor heat exchanger is made lower than the refrigerant evaporating pressure in the indoor evaporator by the action of the evaporating pressure adjusting valve.
  • the target refrigerant in the indoor evaporator is used so that the refrigeration cycle apparatus exhibits a high cooling capacity as the cooling heat load increases. Reduce evaporation temperature. Then, in order to bring the actual refrigerant evaporation temperature in the indoor evaporator closer to the target refrigerant evaporation temperature, the refrigerant discharge capacity (rotation speed) of the compressor is increased.
  • the present disclosure aims to suppress an unnecessary increase in power consumption of a compressor in a refrigeration cycle apparatus including an evaporation pressure adjusting valve.
  • a refrigeration cycle apparatus includes a compressor that compresses and discharges a refrigerant, an outdoor heat exchanger that exchanges heat between the refrigerant discharged from the compressor and outside air, and a refrigerant that has flowed out of the outdoor heat exchanger
  • a decompressor for reducing the pressure, an evaporator for exchanging heat between the low-pressure refrigerant decompressed by the decompressor and the heat exchange target fluid, and evaporating the low-pressure refrigerant, and a refrigerant evaporation pressure in the evaporator is equal to or higher than a predetermined reference evaporation pressure
  • An evaporating pressure adjusting valve that adjusts the target evaporating pressure, a target evaporating pressure determining unit that determines a target evaporating pressure in the evaporator, and a discharge capacity control unit that controls the operation of the compressor.
  • the target evaporating pressure determining unit determines that the target evaporating pressure is reduced as the cooling capacity of the heat exchange target fluid required for the evaporator increases, and the evaporating pressure adjusting valve circulates the evaporator. As the refrigerant flow rate increases, the set pressure increases. The target evaporation pressure determination unit is adjusted so that the refrigerant evaporation pressure approaches the higher of the target evaporation pressure and the set pressure when the discharge capacity control unit controls the operation of the compressor.
  • the set pressure is the evaporation pressure when the evaporation pressure regulating valve in the fully open state starts to reduce the refrigerant passage area in order to maintain the refrigerant evaporation temperature in the evaporator above the reference evaporation temperature.
  • This is the refrigerant pressure at the inlet side of the regulating valve (refrigerant evaporation pressure in the evaporator).
  • this set pressure is a value that varies depending on the flow rate of the refrigerant flowing through the evaporation pressure adjusting valve.
  • the operation of the compressor is controlled so that the refrigerant evaporation pressure approaches the target evaporation pressure.
  • the cooling capacity required for the evaporator can be exhibited without unnecessarily increasing the power consumption of the compressor.
  • the operation of the compressor is controlled so that the refrigerant evaporation pressure approaches the set pressure.
  • the cooling ability of the heat exchange target fluid required for the evaporator is the ability to cool the heat exchange target fluid at a desired flow rate to a desired temperature in the evaporator, specifically, It can be defined using a value obtained by integrating the enthalpy difference (refrigeration capacity) obtained by subtracting the enthalpy of the inlet side refrigerant from the enthalpy of the evaporator outlet side refrigerant and the flow rate (mass flow rate) of the refrigerant flowing through the evaporator. .
  • the evaporating pressure adjusting valve is configured such that the refrigerant passage area inside increases as the refrigerant evaporating pressure increases, and the refrigerant passage increases as the refrigerant evaporating pressure increases.
  • the degree of increase when the area increases may be larger than the degree of increase when the refrigerant passage area increases linearly in proportion to the increase in the refrigerant evaporation pressure.
  • the evaporator passage area of the evaporation pressure regulating valve increases linearly in proportion to the increase in the flow rate of the refrigerant flowing through the evaporator.
  • the degree of increase in the set pressure accompanying an increase in the flow rate of the refrigerant flowing through can be reduced.
  • the refrigerant flow rate range in which the target evaporation pressure becomes higher than the set pressure can be expanded, and the cooling capacity required for the evaporator can be exhibited without unnecessarily increasing the power consumption of the compressor.
  • the range of the refrigerant flow rate can be expanded.
  • the discharge capacity control unit may control the operation of the compressor so as to suppress the evaporation pressure regulating valve from decreasing the internal refrigerant passage area. According to this, when the set pressure is higher than the target evaporation pressure, the refrigerant evaporation pressure can be easily brought close to the set pressure.
  • FIG. 1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. It is an axial sectional view of the evaporation pressure regulating valve of the first embodiment. It is a side view of the cylindrical valve body part of the evaporation pressure regulating valve of the first embodiment.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. It is a graph which shows the relationship between the displacement amount of the cylindrical valve body part in the evaporation pressure regulating valve of 1st Embodiment, and a refrigerant passage area. It is a graph which shows the relationship between the refrigerant
  • the refrigeration cycle apparatus 10 is applied to a vehicle air conditioner 1 for an electric vehicle that obtains a driving force for vehicle traveling from a traveling electric motor.
  • the refrigeration cycle apparatus 10 functions to cool or heat the air (blasted air) blown into the vehicle interior, which is the air-conditioning target space, in the vehicle air conditioner 1. Accordingly, the heat exchange target fluid of this embodiment is blown air.
  • the refrigeration cycle apparatus 10 of the present embodiment is a heating mode refrigerant circuit that heats the air and heats the interior of the vehicle, and dehumidifies that dehumidifies and heats the interior of the vehicle by reheating the air that has been cooled and dehumidified.
  • the refrigerant circuit can be switched to a heating mode refrigerant circuit and a cooling mode refrigerant circuit that cools the vehicle interior by cooling the blown air.
  • the refrigerant flow in the refrigerant circuit in the heating mode is indicated by black arrows
  • the refrigerant flow in the refrigerant circuit in the dehumidifying and heating mode is indicated by hatched arrows
  • the refrigerant flow in the refrigerant circuit in the cooling mode is further indicated.
  • the flow is indicated by white arrows.
  • an HFC-based refrigerant (specifically, R134a) is adopted as the refrigerant, and a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure Pd does not exceed the critical pressure of the refrigerant. It is composed.
  • an HFO refrigerant (for example, R1234yf) or the like may be adopted as the refrigerant.
  • refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.
  • the compressor 11 is disposed in the vehicle bonnet, sucks the refrigerant in the refrigeration cycle apparatus 10, compresses and discharges it, and is a fixed capacity type with a fixed discharge capacity. It is comprised as an electric compressor which drives this compression mechanism with an electric motor. Specifically, various compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be employed as the compression mechanism.
  • the electric motor is one whose operation (number of rotations) is controlled by a control signal output from the air conditioning control device 40 described later, and any type of an AC motor and a DC motor may be adopted. And the refrigerant
  • the refrigerant inlet side of the indoor condenser 12 is connected to the discharge port side of the compressor 11.
  • the indoor condenser 12 is disposed in a casing 31 of an indoor air conditioning unit 30 described later, and exchanges heat between the discharged refrigerant (high-pressure refrigerant) discharged from the compressor 11 and the blown air that has passed through the indoor evaporator 18 described later.
  • a heating heat exchanger heat radiator for heating the blown air.
  • the refrigerant outlet side of the indoor condenser 12 is connected to one refrigerant inlet / outlet of the first three-way joint 13a that branches the flow of the refrigerant flowing out of the indoor condenser 12 in the dehumidifying heating mode.
  • a three-way joint may be formed by joining pipes having different pipe diameters, or may be formed by providing a plurality of refrigerant passages in a metal block or a resin block.
  • the basic configuration of second to fourth three-way joints 13b to 13d described later is the same as that of the first three-way joint 13a.
  • a first refrigerant passage 14a that guides the refrigerant flowing out of the indoor condenser 12 to the refrigerant inlet side of the outdoor heat exchanger 16 is connected to another refrigerant inlet / outlet of the first three-way joint 13a.
  • the refrigerant that has flowed out of the indoor condenser 12 is supplied to the inlet side (specifically, the second expansion valve 15b disposed in the third refrigerant passage 14c described later). Is connected to the second refrigerant passage 14b leading to one refrigerant inflow / outlet of the third three-way joint 13c.
  • a first expansion valve 15a is disposed as an outdoor unit decompression device that decompresses the refrigerant flowing out of the indoor condenser 12 during the heating mode and the dehumidifying heating mode.
  • the first expansion valve 15a is a variable throttle mechanism that includes a valve body that can change the throttle opening degree and an electric actuator that includes a stepping motor that changes the throttle opening degree of the valve body. .
  • the first expansion valve 15a is configured as a variable throttle mechanism with a fully open function that functions as a simple refrigerant passage with almost no refrigerant decompression effect by fully opening the throttle opening.
  • the operation of the first expansion valve 15a is controlled by a control signal (control pulse) output from the air conditioning control device 40.
  • the refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet side of the first expansion valve 15a.
  • the outdoor heat exchanger 16 is disposed on the vehicle front side in the vehicle bonnet, and exchanges heat between the refrigerant circulating inside and the air outside the vehicle (outside air) blown from a blower fan (not shown).
  • the blower fan is an electric blower whose number of rotations (blowing capacity) is controlled by a control voltage output from the air conditioning control device 40.
  • One refrigerant inlet / outlet of the second three-way joint 13b is connected to the refrigerant outlet side of the outdoor heat exchanger 16.
  • a third refrigerant passage 14c that guides the refrigerant flowing out of the outdoor heat exchanger 16 to the refrigerant inlet side of the indoor evaporator 18 is connected to another refrigerant inlet / outlet of the second three-way joint 13b.
  • the refrigerant flowing out of the outdoor heat exchanger 16 is supplied to another refrigerant inflow / outlet of the second three-way joint 13b from the inlet side of the accumulator 20 (specifically, one refrigerant of the fourth three-way joint 13d).
  • a fourth refrigerant passage 14d leading to the inflow / outlet is connected.
  • the third refrigerant passage 14c is connected to the check valve 17 that only allows the refrigerant to flow from the second three-way joint 13b side to the indoor evaporator 18 side, and the third three-way joint 13c to which the second refrigerant passage 14b described above is connected.
  • the second expansion valve 15b serving as a decompression device that decompresses the refrigerant that flows out of the outdoor heat exchanger 16 and flows into the indoor evaporator 18 is provided with respect to the refrigerant flow. Arranged in order.
  • the basic configuration of the second expansion valve 15b is the same as that of the first expansion valve 15a. Furthermore, the second expansion valve 15b of the present embodiment not only has a fully-open function that fully opens the refrigerant passage from the outdoor heat exchanger 16 to the indoor evaporator 18 when the throttle opening is fully opened, but also fully closes the throttle opening. In this case, it is composed of a variable throttle mechanism with a fully closing function that closes the refrigerant passage.
  • the refrigerant circuit can be switched by closing the third refrigerant passage 14c with the second expansion valve 15b fully closed.
  • the second expansion valve 15b functions as a refrigerant unit decompression device and also functions as a refrigerant circuit switching unit that switches a refrigerant circuit of the refrigerant circulating in the cycle.
  • the indoor evaporator 18 is disposed in the casing 31 of the indoor air conditioning unit 30 on the upstream side of the blower air flow of the indoor condenser 12, and in the cooling mode and the dehumidifying heating mode, the low-pressure refrigerant that circulates inside the indoor evaporator 18 12 is a heat exchanger for cooling (evaporator) that cools the blown air by causing heat exchange with the blown air before passing through 12 and evaporating the refrigerant to exhibit an endothermic effect.
  • evaporator heat exchanger for cooling
  • the inlet side of the evaporation pressure adjusting valve 19 is connected to the refrigerant outlet side of the indoor evaporator 18.
  • the evaporation pressure adjusting valve 19 sets the refrigerant evaporation pressure (refrigerant evaporation temperature) in the indoor evaporator 18 to be equal to or higher than a predetermined reference evaporation pressure (reference evaporation temperature) in order to suppress frost formation (frost) of the indoor evaporator 18. It fulfills the function of maintaining.
  • R134a is used as the refrigerant, and the reference evaporation temperature is determined to be a value slightly higher than 0 ° C., so the reference evaporation pressure is a value slightly higher than 0.293 MPa.
  • the detailed configuration of the evaporation pressure adjusting valve 19 will be described later.
  • the fourth three-way joint 13d to which the above-described fourth refrigerant passage 14d is connected is connected to the outlet side of the evaporation pressure adjusting valve 19. Furthermore, the inlet side of the accumulator 20 is connected to another refrigerant inlet / outlet of the fourth three-way joint 13d.
  • a first on-off valve 21 for opening and closing the fourth refrigerant passage 14d is disposed in the fourth refrigerant passage 14d that connects the second three-way joint 13b and the fourth three-way joint 13d.
  • the first on-off valve 21 is an electromagnetic valve whose operation is controlled by a control signal output from the air-conditioning control device 40, and functions as a refrigerant circuit switching unit.
  • a second on-off valve 22 for opening and closing the second refrigerant passage 14b is disposed in the second refrigerant passage 14b connecting the first three-way joint 13a and the third three-way joint 13c.
  • the basic configuration of the second on-off valve 22 is the same as that of the first on-off valve 21.
  • the second on-off valve 22 functions as a refrigerant circuit switching unit together with the second expansion valve 15 b and the first on-off valve 21.
  • the accumulator 20 is a gas-liquid separator that separates the gas-liquid of the refrigerant that has flowed into the accumulator and stores excess refrigerant in the cycle.
  • the suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 20. Therefore, the accumulator 20 functions to prevent liquid phase refrigerant from being sucked into the compressor 11 and prevent liquid compression in the compressor 11.
  • the evaporation pressure adjusting valve 19 is constituted by a pure mechanical mechanism. Specifically, the evaporating pressure adjusting valve 19 has a body 91 configured by combining a plurality of metal members, and a cylindrical valve body portion 92, a refrigerant passage formed inside the body 91, A bellows 93, a spring 94 and the like are arranged.
  • the body 91 forms an outer shell of the evaporation pressure regulating valve 19 and is formed in a cylindrical shape.
  • An inflow port 91a connected to the refrigerant outlet side of the indoor evaporator 18 is provided on one end side in the axial direction of the body 91 formed in a cylindrical shape, and connected to the inlet side of the accumulator 20 on the other end side in the axial direction.
  • An outlet 91b is provided.
  • a cylinder portion 91c is formed on the downstream side of the refrigerant flow of the inlet 91a of the body 91.
  • a cylindrical space is formed inside the cylinder portion 91c, and the cylindrical portion 92a of the cylindrical valve body portion 92 is fitted in the cylindrical space so as to be slidable in the axial direction. That is, the outer diameter size of the cylindrical portion 92a of the cylindrical valve body portion 92 and the inner diameter size of the cylinder portion 91c are in a dimensional relationship of the clearance fit.
  • the cylindrical valve body 92 is formed of a bottomed cylindrical (cup-shaped) metal member, and is disposed on the other axial end side (outlet 91b side). On the bottom surface is provided a flange 92b that extends perpendicular to the axial direction. The flange portion 92b is a portion that abuts on the most downstream end portion of the cylinder portion 91c and regulates the displacement of the cylindrical valve body portion 92. Furthermore, a plurality (six in this embodiment) of communication holes 92c are formed on the side surface of the cylindrical portion 92a of the cylindrical valve body portion 92 so as to communicate the inner peripheral side and the outer peripheral side thereof. For example, as shown in FIG.
  • the communication hole 92 c is a plurality of triangular openings arranged in the circumferential direction of the cylindrical valve body portion 92, and one side of each triangular opening is the same as that of the cylindrical valve body portion 92. It is provided on the circumference and is disposed closer to the inlet 91a side of the evaporation pressure regulating valve 19 than the other two sides of each triangular opening.
  • the communication hole 92c is formed in the cylinder. It is blocked by the inner peripheral wall surface of 91c, and the communication between the inflow port 91a and the outflow port 91b is blocked.
  • the cylindrical valve body portion 92 is displaced from the other end side in the axial direction to increase the displacement L, the communication hole 92c is exposed from the cylinder portion 91c, and the outflow port 91b and the outflow port 91b pass through the communication hole 92c. Communicate through.
  • the cylinder part 91c and the cylindrical valve body part 92 of the present embodiment constitute a so-called slide valve.
  • the bellows 93 is a metal hollow cylindrical member formed to be extendable and contractible in the displacement direction of the cylindrical valve body portion 92 (the axial direction of the body 91), and is disposed on the downstream side of the refrigerant flow of the cylindrical valve body portion 92. Has been. Furthermore, the axial direction one end side of the bellows 93 is connected with the cylindrical valve body part 92, and the axial direction other end side of the bellows 93 is being fixed to the body 91 side.
  • a spring 94 is disposed in the internal space of the bellows 93.
  • the spring 94 is constituted by a cylindrical coil spring that extends in the displacement direction of the cylindrical valve body 92, and urges the cylindrical valve body 92 together with the bellows 93 in the valve closing direction (direction toward the inflow port 91a). A load is applied. The load that the bellows 93 and the spring 94 urge against the cylindrical valve body 92 can be adjusted by the adjusting screw 94a.
  • the cylindrical valve body 92 of the present embodiment includes the refrigerant pressure on the inlet 91a side (refrigerant evaporation pressure in the indoor evaporator 18), the refrigerant pressure on the outlet 91b side (the suction side refrigerant pressure of the compressor 11, that is, Refrigerant pressure in the accumulator 20) and further a load by the bellows 93 and the spring 94.
  • the tubular valve body 92 is displaced to a position where these loads are balanced, so that the refrigerant passage area in the evaporation pressure adjusting valve 19 is adjusted. More specifically, the balance of the load received by the tubular valve body portion 92 can be expressed by the following formula F1.
  • P1 * A1 + P2 * A2 K * L + P2 * A1 + F0 (F1)
  • P1 is the refrigerant pressure on the inlet 91a side
  • P2 is the refrigerant pressure on the outlet 91b side
  • A1 is the pressure receiving area of the tubular valve body 92
  • A2 is the pressure receiving area of the bellows 93
  • K is the bellows 93 and
  • L is the amount of displacement of the tubular valve body 92
  • F0 is the initial load of the bellows 93 and spring 94 adjusted by the adjusting screw 94a.
  • Equation F1 can be modified as Equation F2 below.
  • P1 K / A1 ⁇ L + F0 / A1 (F2)
  • F2 Equation F2
  • the evaporation pressure adjusting valve 19 of the present embodiment increases the refrigerant pressure P1 on the inlet 91a side as the refrigerant flow rate flowing through the indoor evaporator 18 (the refrigerant flow rate flowing through the evaporation pressure adjusting valve 19) increases. It has a configuration to let you. That is, the evaporation pressure adjusting valve 19 of the present embodiment increases the displacement L in proportion to the increase of the refrigerant pressure P1 on the inlet 91a side, and adjusts the evaporation pressure with the increase of the refrigerant pressure P1 on the inlet 91a side. The refrigerant passage area in the valve 19 is increased. In this example, the refrigerant pressure P1 on the inlet 91a side corresponds to the refrigerant evaporation pressure Pe in the indoor evaporator 18.
  • the plurality of communication holes 92c of the present embodiment are each formed in an isosceles triangle shape having a vertex on the outlet 91b side. That is, the communication hole 92c is formed in a shape that gradually decreases in the valve opening direction of the cylindrical valve body portion 92 (the direction toward the outflow port 91b).
  • the length in the circumferential direction LC of the communication hole 92c in the axial vertical cross section shown in FIG. 4 gradually increases in the valve closing direction of the cylindrical valve body 92 (the direction toward the inflow port 91a). It is formed into a shape. More specifically, in the present embodiment, the shape of the communication hole 92c is determined so that the displacement amount L of the cylindrical valve body 92 and the square root of the refrigerant passage area change in proportion.
  • the refrigerant accompanying the increase in the displacement amount L of the cylindrical valve body 92 shown by the thick solid line in FIG. 5 (that is, the rise in the refrigerant pressure P1 on the inlet 91a side).
  • the increase in the passage area linearly increases the refrigerant passage area in proportion to the increase in the displacement amount L of the cylindrical valve body 92 shown by the thick broken line in FIG. 5 (hereinafter referred to as a comparative example). It is larger over the entire area than the degree.
  • the evaporating pressure adjusting valve 19 has an inner refrigerant passage area that increases as the refrigerant evaporating pressure Pe in the indoor evaporator 18 increases.
  • the degree of increase when the refrigerant passage area increases as the refrigerant evaporation pressure Pe increases is larger than the degree of increase when the refrigerant passage area increases linearly in proportion to the increase of the refrigerant evaporation pressure Pe (comparative example). Is also getting bigger. Specifically, as shown in FIG. 5, the degree of increase is set so that the refrigerant passage area becomes larger than the degree of increase when the displacement L is linearly increased with a tangential slope at the time of zero (comparative example). Is set.
  • the increase degree of the set pressure Pset accompanying the increase in the flow rate of the refrigerant flowing through the indoor evaporator 18 is indicated by the thick broken line in FIG.
  • the set pressure Pset of the present embodiment is that the evaporation pressure adjusting valve 19 in the fully opened state (the displacement amount L is the maximum displacement amount) uses the refrigerant evaporation pressure in the indoor evaporator 18 as the reference evaporation pressure.
  • the refrigerant pressure on the inlet 91a side (the refrigerant in the indoor evaporator 18) when the reduction of the refrigerant passage area is started (when the displacement of the tubular valve body 92 in the valve closing direction is started). Evaporative pressure).
  • the displacement amount L of the cylindrical valve body portion 92 becomes the maximum displacement amount immediately after the operation is started. Become.
  • the bellows 93 and the spring are adjusted so that the refrigerant pressure P1 on the inlet 91a side is maintained above the reference evaporation pressure.
  • the cylindrical valve body 92 is displaced in the valve closing direction (direction toward the inflow port 91a) by the load of 94.
  • the refrigerant pressure P1 on the inlet 91a side when the cylindrical valve body 92 starts to be displaced in the valve closing direction becomes the set pressure Pset. Further, the set pressure Pset increases as the flow rate of the refrigerant flowing through the indoor evaporator 18 increases, as shown in FIG.
  • the indoor air conditioning unit 30 shown in FIG. 1 is for blowing out the blown air whose temperature has been adjusted by the refrigeration cycle apparatus 10 into the vehicle interior, and is disposed inside the instrument panel (instrument panel) at the forefront of the vehicle interior. Furthermore, the indoor air conditioning unit 30 is configured by housing a blower 32, the indoor evaporator 18, the indoor condenser 12, and the like in a casing 31 that forms an outer shell thereof.
  • the casing 31 forms an air passage for the blown air blown into the passenger compartment, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent in strength.
  • An inside / outside air switching device 33 as an inside / outside air switching unit that switches and introduces inside air (vehicle compartment air) and outside air (vehicle compartment outside air) into the casing 31 is arranged on the most upstream side of the blown air flow in the casing 31. ing.
  • the inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port through which the inside air is introduced into the casing 31 and the outside air introduction port through which the outside air is introduced by the inside / outside air switching door, so that the air volume of the inside air and the air volume of the outside air are adjusted.
  • the air volume ratio is continuously changed.
  • the inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning control device 40.
  • a blower 32 that blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior is disposed on the downstream side of the blowing air flow of the inside / outside air switching device 33.
  • the blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (air flow rate) is controlled by a control voltage output from the air conditioning control device 40.
  • the indoor evaporator 18 and the indoor condenser 12 are arranged in this order with respect to the flow of the blown air.
  • the indoor evaporator 18 is disposed on the upstream side of the blown air flow with respect to the indoor condenser 12.
  • a cold air bypass passage 35 is formed in which the blown air that has passed through the indoor evaporator 18 bypasses the indoor condenser 12 and flows downstream.
  • the blast air heated by the indoor condenser 12 and the blast air not heated by the indoor condenser 12 through the cold air bypass passage 35 are mixed on the downstream side of the blast air flow of the indoor condenser 12.
  • a mixing space is provided.
  • the opening hole which blows off the ventilation air (air-conditioning wind) mixed in the mixing space to the vehicle interior which is an air-conditioning object space is arrange
  • the opening hole includes a face opening hole that blows air-conditioned air toward the upper body of the passenger in the passenger compartment, a foot opening hole that blows air-conditioned air toward the feet of the passenger, and an inner surface of the front window glass of the vehicle.
  • a defroster opening hole (both not shown) for blowing the conditioned air toward is provided. The air flow downstream of these face opening holes, foot opening holes, and defroster opening holes is connected to the face air outlet, foot air outlet, and defroster air outlet provided in the vehicle interior via ducts that form air passages, respectively. Neither is shown).
  • the air mix door 34 adjusts the air volume ratio between the air volume that passes through the indoor condenser 12 and the air volume that passes through the cold air bypass passage 35, thereby adjusting the temperature of the conditioned air mixed in the mixing space.
  • the temperature of the blast air (air conditioned air) blown out from each outlet to the vehicle interior is adjusted.
  • the air mix door 34 constitutes a temperature adjustment unit that adjusts the temperature of the conditioned air blown into the vehicle interior.
  • the air mix door 34 is driven by an electric actuator for driving the air mix door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning control device 40.
  • a face door for adjusting the opening area of the face opening hole a foot door for adjusting the opening area of the foot opening hole, and a defroster opening, respectively.
  • a defroster door (both not shown) for adjusting the opening area of the hole is disposed.
  • These face doors, foot doors, and defroster doors constitute an opening hole mode switching unit that switches the opening hole mode, and are linked to an electric actuator for driving the outlet mode door via a link mechanism or the like. And rotated.
  • the operation of this electric actuator is also controlled by a control signal output from the air conditioning control device 40.
  • a face mode in which the face air outlet is fully opened and air is blown out from the face air outlet toward the upper body of the passenger in the passenger compartment, the face air outlet and the foot air outlet
  • the bi-level mode that opens both of the air outlets and blows air toward the upper body and feet of passengers in the passenger compartment, fully opens the foot outlet and opens the defroster outlet by a small opening, and mainly draws air from the foot outlet.
  • the defroster mode in which the defroster blowout port is fully opened and air is blown out from the defroster blowout port to the inner surface of the front windshield of the vehicle can be set.
  • the air conditioning control device 40 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. Then, various calculations and processes are performed based on the air conditioning control program stored in the ROM, and the compressor 11, the first expansion valve 15a, the second expansion valve 15b, and the first on-off valve connected to the output side thereof. 21, the operation of various air conditioning control devices such as the second on-off valve 22 and the blower 32 are controlled.
  • an inside air sensor 51 as an inside air temperature detector that detects a vehicle interior temperature (inside air temperature) Tr, and an outside air temperature detector that detects a vehicle outside temperature (outside air temperature) Tam.
  • An outside air sensor 52 a solar radiation sensor 53 as a solar radiation amount detector for detecting the solar radiation amount As irradiated into the vehicle interior, a discharge temperature sensor 54 for detecting the refrigerant discharge temperature Td of the refrigerant discharged from the compressor 11, and an outlet of the indoor condenser 12
  • High pressure side pressure sensor 55 for detecting the side refrigerant pressure (high pressure side refrigerant pressure) Pd
  • the evaporator temperature sensor 56 for detecting the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18, and the outlet side refrigerant of the indoor evaporator 18
  • Air conditioning such as a low pressure side pressure sensor 57 that detects pressure (low pressure side refrigerant pressure) Pe, and a blown air temperature sensor 58 that detects a blown air temperature TAV blown from the mixed space into the vehicle interior. Detection signals of patronage groups of the sensor is input.
  • the high-pressure side refrigerant pressure Pd of the present embodiment is, for example, a high-pressure side refrigerant pressure of a cycle from the discharge port side of the compressor 11 to the inlet side of the first expansion valve 15a in the heating mode or the like, and in the cooling mode, It becomes the high pressure side refrigerant pressure of the cycle from the discharge port side of the compressor 11 to the inlet side of the second expansion valve 15b.
  • the low-pressure side refrigerant pressure Pe of the present embodiment is a value corresponding to the actual refrigerant evaporation pressure in the indoor evaporator 18 in the cooling mode and the dehumidifying heating mode.
  • the evaporator temperature sensor 56 of this embodiment has detected the heat exchange fin temperature of the indoor evaporator 18, the temperature which detects the temperature of the other site
  • a detector may be employed, or a temperature detector that directly detects the temperature of the refrigerant itself flowing through the indoor evaporator 18 may be employed.
  • the ventilation air temperature sensor which detects blowing air temperature TAV is provided, the value calculated based on evaporator temperature Tefin, discharge refrigerant temperature Td, etc. is employ
  • operation signals from various air conditioning operation switches provided on the operation panel 60 disposed in the vicinity of the instrument panel in the front of the vehicle interior are input.
  • the various air conditioning operation switches provided on the operation panel 60 include an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner 1, and a cooling switch (A / C switch), an air volume setting switch for manually setting the air volume of the blower 32, a temperature setting switch for setting the vehicle interior set temperature Tset, which is a target temperature in the vehicle interior, and a blow mode switching switch for manually setting the air discharge mode.
  • the air-conditioning control device 40 is configured integrally with a control unit that controls various air-conditioning control devices connected to the output side of the air-conditioning control device 40.
  • the configuration (hardware and hardware) controls the operation of each air-conditioning control device.
  • Software constitutes a control unit that controls the operation of each air conditioning control device.
  • the configuration for controlling the operation of the compressor 11 constitutes the discharge capacity control unit 40a, and the second expansion valve 15b, the first on-off valve 21 and the second on-off valve 22 constituting the refrigerant circuit switching unit.
  • the configuration for controlling the operation of the refrigerant circuit constitutes the refrigerant circuit control unit 40b.
  • the discharge capacity control unit, the refrigerant circuit control unit, and the like may be configured as a separate control device with respect to the air conditioning control device 40.
  • the vehicle air conditioner 1 according to the present embodiment can switch the operation in the cooling mode, the heating mode, and the dehumidifying heating mode.
  • the switching between these operation modes is performed by executing an air conditioning control program stored in the air conditioning control device 40 in advance.
  • FIG. 8 is a flowchart showing a control process as a main routine of the air conditioning control program. This control process is executed when the auto switch of the operation panel 60 is turned on.
  • each control step of the flowchart shown to FIG. 8, FIG. 9 comprises the various function implementation
  • step S1 initialization such as initialization of flags and timers configured by the storage circuit of the air-conditioning control device 40 and initial positioning of the stepping motors constituting the various electric actuators described above is performed. It should be noted that in the initialization in step S1, some of the flags and the calculated values are read out from the values stored at the previous stop of the vehicle air conditioner or the end of the vehicle system.
  • step S2 detection signals from the sensor groups 51 to 58 for air conditioning control, operation signals from the operation panel 60, and the like are read.
  • step S3 based on the detection signal and operation signal read in step S2, a target blowing temperature TAO that is a target temperature of the blown air blown into the vehicle interior is calculated.
  • the target blowing temperature TAO is calculated by the following formula F3.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ As + C (F3)
  • Tr is the vehicle interior set temperature (inside air temperature) detected by the inside air sensor 51
  • Tam is the outside air temperature detected by the outside air sensor 52
  • As is the solar radiation sensor 53. Is the amount of solar radiation detected by.
  • Kset, Kr, Kam, Ks are control gains
  • C is a correction constant.
  • step S4 the operation mode is determined. More specifically, in step S4, a subroutine shown in FIG. 9 is executed.
  • step S41 it is determined whether or not the cooling switch of the operation panel 60 is turned on. When it is determined in step S41 that the cooling switch is turned on (turned on), the process proceeds to step S42.
  • step S41 when it is determined in step S41 that the cooling switch is not turned on (turned off), the process proceeds to step S45, the operation mode is determined as the heating mode, and the process proceeds to step S5.
  • step S42 if (TAO-Tam) ⁇ , the process proceeds to step S43, the operation mode is determined to be the cooling mode, and the process returns to step S5. On the other hand, if (TAO ⁇ Tam) ⁇ is not satisfied in step S42, the process proceeds to step S44, the operation mode is determined to be the dehumidifying heating mode, and the process returns to step S5.
  • step S5 the open / close state of the first and second open / close valves 21 and 22 is determined according to the operation mode determined in step 4.
  • step S6 the opening degree of the air mix door 34 is determined according to the operation mode determined in step 4.
  • step S7 the operating states of the first and second expansion valves 15a and 15b are determined according to the operation mode determined in step 4.
  • step S5 to S7 the open / close state of the first and second on-off valves 21 and 22, the opening of the air mix door 34, and the first and second The operating state of the expansion valves 15a and 15b is determined.
  • step S8 the refrigerant discharge capacity of the compressor 11 is determined as described in detail in each operation mode described later.
  • step S9 control signals or control voltages are output from the air conditioning control device 40 to the various air conditioning control devices so that the operating states of the various air conditioning control devices determined in steps S5 to S8 are obtained.
  • step S10 it waits for control period (tau), and if progress of control period (tau) is determined, it will return to step S2.
  • the operation mode is determined as described above, and the operation in each operation mode is executed.
  • the operation in each operation mode will be described below.
  • (A) Heating Mode In the heating mode, as shown in the chart of FIG. 10, the air conditioning control device 40 opens the first on-off valve 21, closes the second on-off valve 22, and exerts a pressure reducing action on the first expansion valve 15a.
  • the second expansion valve 15b is fully closed.
  • the compressor 11 in the heating mode, as indicated by the black arrow in FIG. 1, the compressor 11 ⁇ the indoor condenser 12 ⁇ the first expansion valve 15 a ⁇ the outdoor heat exchanger 16 ⁇ (the first on-off valve 21 ⁇ ) the accumulator 20 ⁇
  • a vapor compression refrigeration cycle in which refrigerant is circulated in the order of the compressor 11 is configured.
  • the air conditioning control device 40 operates the various air conditioning control devices in the heating mode (control signals output to the various air conditioning control devices). To decide.
  • the air mix door 34 fully closes the cold air bypass passage 35, and the entire blown air after passing through the indoor evaporator 18
  • the flow rate is determined so as to pass through the air passage on the indoor condenser 12 side.
  • the degree of supercooling of the refrigerant flowing into the first expansion valve 15a is such that the coefficient of performance (COP) of the cycle is substantially the maximum value. It is determined so as to approach the target subcooling degree determined to be.
  • control signal output to the electric motor of the compressor 11 determined in step S8 is determined as follows. First, the target condensing pressure PCO in the indoor condenser 12 is determined based on the target blowing temperature TAO with reference to a control map stored in the air conditioning control device 40 in advance.
  • the feedback control method is used so that the high-pressure side refrigerant pressure Pd approaches the target condensation pressure PCO.
  • a control signal output to the electric motor of the compressor 11 is determined.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12.
  • the refrigerant flowing into the indoor condenser 12 exchanges heat with the blown air that has been blown from the blower 32 and passed through the indoor evaporator 18 to dissipate heat. Thereby, blowing air is heated.
  • the refrigerant flowing out of the indoor condenser 12 flows out from the first three-way joint 13a toward the first refrigerant passage 14a and is decompressed until it becomes a low-pressure refrigerant at the first expansion valve 15a. Is done.
  • the low-pressure refrigerant decompressed by the first expansion valve 15a flows into the outdoor heat exchanger 16 and absorbs heat from the outside air blown from the blower fan.
  • the refrigerant flowing out of the outdoor heat exchanger 16 flows out from the second three-way joint 13b to the fourth refrigerant passage 14d side because the first on-off valve 21 is opened and the second expansion valve 15b is fully closed. It flows into the accumulator 20 and is separated into gas and liquid. The gas-phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed again by the compressor 11.
  • the vehicle interior can be heated by blowing the air blown by the indoor condenser 12 into the vehicle interior.
  • (B) Dehumidification heating mode In the dehumidification heating mode, as shown in the chart of FIG. 10, the air conditioning control device 40 opens the first on-off valve 21, opens the second on-off valve 22, and restricts the first expansion valve 15a. And the second expansion valve 15b is in the throttle state.
  • the refrigerant is circulated in the order of accumulator 20 ⁇ compressor 11, and compressor 11 ⁇ indoor condenser 12 ⁇ (second on-off valve 22 ⁇ ) second expansion valve 15 b ⁇ indoor evaporator 18 ⁇ evaporation pressure regulating valve 19 ⁇
  • a vapor compression refrigeration cycle in which refrigerant is circulated in the order of accumulator 20 ⁇ compressor 11 is configured.
  • the refrigerant flowing out from the indoor condenser 12 flows in the order of the first expansion valve 15a ⁇ the outdoor heat exchanger 16 ⁇ the compressor 11, and the second expansion valve 15b ⁇ the indoor evaporator 18 ⁇ the evaporation pressure adjustment.
  • the refrigerant circuit is switched in parallel in the order of the valve 19 ⁇ the compressor 11. Therefore, the refrigerant circuit in the dehumidifying heating mode corresponds to the second refrigerant circuit described in the claims.
  • the air conditioning control device 40 determines the operating state of various air conditioning control devices in the dehumidifying heating mode, as described in steps S6 to S8 above.
  • the air mix door 34 fully closes the cold air bypass passage 35 and passes through the indoor evaporator 18 as in the heating mode.
  • the total flow rate of the subsequent blown air is determined so as to pass through the air passage on the indoor condenser 12 side.
  • the degree of supercooling of the refrigerant flowing into the first expansion valve 15a is the coefficient of performance (COP) of the cycle. ) Is determined so as to approach the target degree of subcooling determined to be substantially the maximum value.
  • control signal output to the second expansion valve 15b is determined so that the flow rate of the refrigerant flowing through the indoor evaporator 18 becomes an appropriate flow rate.
  • the throttle opening degree of the second expansion valve 15b is adjusted so that the superheat degree of the refrigerant on the outlet side of the indoor evaporator 18 becomes a predetermined reference superheat degree (for example, 5 ° C.).
  • control signal output to the electric motor of the compressor 11 determined in step S8 is determined in the same manner as in the heating mode.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and is cooled by the indoor evaporator 18 to be dehumidified and exchanged heat. To dissipate heat. Thereby, blowing air is heated.
  • the flow of the refrigerant flowing out of the indoor condenser 12 is branched at the first three-way joint 13a because the second on-off valve 22 is open.
  • One refrigerant branched by the first three-way joint 13a flows out to the first refrigerant passage 14a side and is depressurized until it becomes a low-pressure refrigerant by the first expansion valve 15a.
  • the low-pressure refrigerant decompressed by the first expansion valve 15a flows into the outdoor heat exchanger 16 and absorbs heat from the outside air blown from the blower fan.
  • the other refrigerant branched by the first three-way joint 13a flows out to the second refrigerant passage 14b side.
  • the refrigerant that has flowed out to the second refrigerant passage 14b side does not flow out to the outdoor heat exchanger 16 side due to the action of the check valve 17, and the second expansion is performed via the second on-off valve 22 and the third three-way joint 13c. It flows into the valve 15b.
  • the refrigerant that has flowed into the second expansion valve 15b is depressurized until it becomes a low-pressure refrigerant.
  • the low-pressure refrigerant decompressed by the second expansion valve 15 b flows into the indoor evaporator 18, absorbs heat from the blown air blown from the blower 32, and evaporates. Thereby, blowing air is cooled.
  • the refrigerant that has flowed out of the indoor evaporator 18 is decompressed by the evaporation pressure adjusting valve 19, and becomes the same pressure as the refrigerant that has flowed out of the outdoor heat exchanger 16.
  • the refrigerant that has flowed out of the evaporating pressure adjusting valve 19 flows into the fourth three-way joint 13d and merges with the refrigerant that has flowed out of the outdoor heat exchanger 16.
  • the refrigerant merged at the fourth three-way joint 13d flows from the accumulator 20 to the suction side of the compressor 11 and is compressed again by the compressor 11.
  • the vehicle interior can be heated by heating the blown air that has been cooled and dehumidified by the indoor evaporator 18 and blown out into the vehicle interior. .
  • the refrigerant evaporation temperature in the indoor evaporator 18 is maintained at or above the reference evaporation temperature (in this embodiment, a value higher than 0 ° C.) by the action of the evaporation pressure adjusting valve 19. Can be suppressed.
  • the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be lower than the refrigerant evaporation temperature in the indoor evaporator 18, the temperature difference between the refrigerant evaporation temperature in the outdoor heat exchanger 16 and the outside air temperature is increased. The amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased.
  • the heating capacity of the blown air in the indoor condenser 12 is increased as compared with the cycle configuration in which the refrigerant evaporation temperature in the outdoor heat exchanger 16 becomes equal to or higher than the reference evaporation temperature similarly to the refrigerant evaporation temperature in the indoor evaporator 18. Can be made.
  • Cooling mode In the cooling mode, as shown in the chart of FIG. 10, the air conditioning control device 40 closes the first on-off valve 21, closes the second on-off valve 22, and fully opens the first expansion valve 15a. The second expansion valve 15b is brought into a throttled state.
  • the compressor 11 in the cooling mode, as indicated by the white arrow in FIG. 1, the compressor 11 ⁇ the indoor condenser 12 ⁇ (first expansion valve 15 a ⁇ ) outdoor heat exchanger 16 ⁇ (check valve 17 ⁇ ) second A vapor compression refrigeration cycle in which the refrigerant is circulated in the order of the expansion valve 15b ⁇ the indoor evaporator 18 ⁇ the evaporation pressure adjusting valve 19 ⁇ the accumulator 20 ⁇ the compressor 11 is configured.
  • the cooling mode refrigerant circuit corresponds to the first refrigerant circuit recited in the claims.
  • the air conditioning control device 40 determines the operating state of various air conditioning control devices in the cooling mode.
  • the air mix door 34 fully opens the cold air bypass passage 35, and the total flow rate of the blown air after passing through the indoor evaporator 18 Is determined to pass through the cold air bypass passage 35.
  • the opening degree of the air mix door 34 may be controlled so that the blown air temperature TAV approaches the target blowing temperature TAO.
  • the degree of supercooling of the refrigerant flowing into the second expansion valve 15b indicates that the coefficient of performance (COP) of the cycle is substantially the maximum value. It is determined so as to approach the target subcooling degree determined to be.
  • control signal output to the electric motor of the compressor 11 determined in step S8 is determined as follows. First, the target evaporation pressure PEO in the indoor evaporator 18 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the air conditioning controller 40.
  • control step S8 comprises the target evaporation pressure determination part described in the claim.
  • the low-pressure refrigerant pressure Pe Based on the deviation between the target evaporation pressure PEO and the low-pressure refrigerant pressure Pe detected by the low-pressure sensor 57, the low-pressure refrigerant pressure Pe approaches the target evaporation pressure PEO using a feedback control method. A control signal output to the electric motor of the compressor 11 is determined.
  • the target outlet temperature TAO described above is a value determined in order to maintain the vehicle interior temperature at the vehicle interior set temperature Tset corresponding to the desired temperature of the passenger. Therefore, in the refrigeration cycle apparatus 10 that cools the blown air by the indoor evaporator 18 as in the cooling mode of the present embodiment, the cooling heat load of the cycle increases as the target blowing temperature TAO decreases.
  • the target evaporation pressure determination unit of the present embodiment determines to decrease the target evaporation pressure PEO as the cooling capacity of the blown air required for the indoor evaporator 18 increases.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12.
  • the air mix door 34 fully closes the air passage on the indoor condenser 12 side, the refrigerant flowing into the indoor condenser 12 flows out of the indoor condenser 12 with almost no heat exchange with the blown air. .
  • the refrigerant that has flowed out of the indoor condenser 12 flows out from the first three-way joint 13a toward the first refrigerant passage 14a and flows into the first expansion valve 15a.
  • the first expansion valve 15a since the first expansion valve 15a is fully opened, the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 16 without being depressurized by the first expansion valve 15a.
  • the refrigerant flowing into the outdoor heat exchanger 16 dissipates heat to the outside air blown from the blower fan in the outdoor heat exchanger 16. Since the first on-off valve 21 is closed, the refrigerant that has flowed out of the outdoor heat exchanger 16 flows into the third refrigerant passage 14c via the second three-way joint 13b, and the low-pressure refrigerant is separated from the refrigerant at the second expansion valve 15b. The pressure is reduced until
  • the low-pressure refrigerant decompressed by the second expansion valve 15 b flows into the indoor evaporator 18, absorbs heat from the blown air blown from the blower 32, and evaporates. Thereby, blowing air is cooled.
  • the refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 20 through the evaporation pressure adjusting valve 19 and is separated into gas and liquid.
  • the gas-phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed again by the compressor 11.
  • the vehicle interior can be cooled by blowing the blown air cooled by the indoor evaporator 18 into the vehicle interior.
  • appropriate air conditioning in the passenger compartment can be realized by switching the operation of the heating mode, the dehumidifying heating mode, and the cooling mode.
  • the indoor evaporation is performed.
  • the refrigerant discharge capacity (rotation speed) of the compressor 11 is increased with an increase in the cooling capacity of the blown air required for the compressor 18.
  • the refrigerant discharge capacity of the compressor 11 is increased and the refrigerant flow rate flowing through the indoor evaporator 18 is increased as described with reference to FIG. Since the set pressure Pset of the regulating valve 19 increases, the refrigerant evaporation pressure (low-pressure side refrigerant pressure Pe) in the indoor evaporator 18 also increases.
  • the degree of increase in the refrigerant passage area with respect to the increase in the displacement L of the cylindrical valve body 92 is compared as the evaporation pressure adjusting valve 19.
  • the one that is larger than the example is adopted.
  • the degree of increase in the set pressure Pset when the flow rate of the refrigerant flowing through the indoor evaporator 18 is increased is reduced so that the set pressure Pset becomes lower than the target evaporation pressure PEO. Yes.
  • the operation of the compressor 11 is controlled so that the refrigerant evaporation pressure Pe approaches the target evaporation pressure PEO which is the higher value of the set pressure Pset and the target evaporation pressure PEO. Therefore, the above-described control interference does not occur in the refrigeration cycle apparatus 10 of the present embodiment. As a result, the cooling capacity required for the indoor evaporator 18 can be exhibited without unnecessarily increasing the power consumption of the compressor 11.
  • an unnecessary increase in power consumption of the compressor 11 is suppressed by changing the rising characteristic of the set pressure Pset with respect to the increase in the refrigerant flow rate in the evaporation pressure adjusting valve 19. Yes.
  • the refrigerating cycle apparatus provided with the evaporation pressure regulating valve 19 comprised so that suppression of the unnecessary increase of the power consumption of the compressor 11 can be suppressed is disclosed.
  • a cylinder valve is formed by the cylinder portion 91c and the cylindrical valve body portion 92, and the shape of the communication hole 92c formed in the side surface of the cylindrical valve body portion 92 is opened. The shape is gradually reduced toward the valve direction. Therefore, the degree of increase in the refrigerant passage area as shown by the solid line in FIG. 5 can be easily realized.
  • the evaporating pressure adjusting valve 19 linearly increases the refrigerant passage area in proportion to the increase in the displacement amount L of the cylindrical valve body 92 (corresponding to a comparative example of the first embodiment). Further, the determination of the operating state of the compressor 11 in the control step S8 in the cooling mode is changed with respect to the first embodiment.
  • step S8 in the cooling mode of the present embodiment, the operation mode is determined in step S81 as shown in the flowchart of FIG. If it is determined in step S81 that the operation mode is the heating mode, the process proceeds to step S82, and the refrigerant discharge capacity (operating state) of the compressor 11 is determined as in the heating mode of the first embodiment. Then, the process proceeds to step S9.
  • step S81 when it is determined in step S81 that the operation mode is the dehumidifying heating mode, the process proceeds to step S83, and the refrigerant discharge capacity (operation) of the compressor 11 is performed as in the dehumidifying heating mode of the first embodiment. State) is determined, and the process proceeds to step S9. Further, when it is determined in step S81 that the operation mode is the cooling mode, the process proceeds to step S84.
  • step S84 the target evaporation pressure PEO is determined as in the first embodiment, and in subsequent step S85, it is determined whether or not the refrigerant evaporation pressure Pe is higher than the target evaporation pressure PEO.
  • step S85 it is determined whether or not the refrigerant evaporation pressure Pe is higher than the target evaporation pressure PEO.
  • step S86 it is determined that the refrigerant evaporation pressure Pe is not higher than the target evaporation pressure PEO. If YES, go to step S87.
  • step S86 it is determined whether or not the evaporation pressure adjusting valve 19 is operating. If it is determined in step S86 that the evaporation pressure adjusting valve 19 is operating, the process proceeds to step S87, the number of rotations of the compressor 11 is decreased by a predetermined amount, and the process proceeds to step S9. On the other hand, if it is determined in step S86 that the evaporation pressure adjusting valve 19 is not in operation, the process proceeds to step S88, the rotation speed of the compressor 11 is increased by a predetermined amount, and the process proceeds to step S9. move on.
  • the determination in the control step S86 can be realized by storing the relationship between the refrigerant flow rate and the set pressure Pset in the evaporation pressure adjusting valve 19 as shown in FIG.
  • the set pressure Pset shown by the thick solid line in FIG. 12 is the set pressure shown by the thick broken line in FIG. It is equivalent to Pset.
  • air conditioning in the vehicle compartment can be realized by switching the operation in the heating mode, the dehumidifying heating mode, and the cooling mode, as in the first embodiment.
  • the operation of the compressor 11 is controlled so that the refrigerant evaporation pressure Pe approaches the higher one of the target evaporation pressure PEO and the set pressure Pset. Unnecessary increase can be suppressed.
  • control step S85 it is determined in control step S85 that the refrigerant evaporation pressure Pe in the indoor evaporator 18 is higher than the target evaporation pressure PEO, and in control step S86.
  • the rotational speed (refrigerant discharge capacity) of the compressor 11 is increased in control step S88.
  • the operation of the compressor 11 can be controlled so that the refrigerant evaporation pressure Pe approaches the target evaporation pressure PEO. Therefore, the cooling capacity required for the indoor evaporator 18 can be exhibited without unnecessarily increasing the power consumption of the compressor 11.
  • the evaporating pressure adjusting valve 19 functions to maintain the refrigerant evaporating pressure Pe in the indoor evaporator 18 at or above the reference evaporating pressure. Therefore, under the operating conditions in which the refrigerant evaporation pressure Pe is higher than the target evaporation pressure PEO and the evaporation pressure adjustment valve 19 is operating, the set pressure Pset of the evaporation pressure adjustment valve 19 is higher than the target evaporation pressure PEO. It will be.
  • the refrigerant evaporation pressure Pe is increased by reducing the rotational speed of the compressor 11 as in the present embodiment, the flow rate of the refrigerant flowing through the indoor evaporator 18 is decreased,
  • the set pressure Pset can be reduced.
  • the refrigerant evaporating pressure Pe can be brought close to the set pressure Pset in a state where the evaporating pressure adjusting valve 19 is not operated (a state where the refrigerant passage area is maximized).
  • the evaporation pressure adjustment valve 19 when the set pressure Pset is higher than the target evaporation pressure PEO, the evaporation pressure adjustment valve 19 is deactivated, that is, the evaporation pressure adjustment valve 19 is The operation of the compressor 11 is controlled so as to suppress the reduction of the internal refrigerant passage area, and the refrigerant evaporation pressure Pe is brought close to the set pressure Pset.
  • the driving force for driving the vehicle may be applied to a vehicle air conditioner mounted on a normal vehicle that obtains from the internal combustion engine (engine), or the driving force for driving from both the driving electric motor and the internal combustion engine. You may apply to the vehicle air conditioner mounted in the hybrid vehicle which obtains.
  • a heater core that heats the blown air using the cooling water of the internal combustion engine as a heat source may be provided as an auxiliary heating device for the blown air.
  • the refrigeration cycle apparatus 10 of the present disclosure is not limited to a vehicle, and may be applied to a stationary air conditioner or the like.
  • the refrigeration cycle apparatus 10 that can be switched to the refrigerant circuit in the heating mode, the dehumidifying heating mode, and the cooling mode has been described, but at least the configuration similar to the cooling mode of the above-described embodiment, If it is a refrigeration cycle apparatus that operates in the same manner, the power consumption suppression effect of the compressor 11 can be obtained.
  • the first and second on-off valves 21 and 22 are closed and switched to the refrigerant circuit similar to that in the cooling mode, and further according to the target outlet temperature TAO. You may make it operate
  • the throttle opening of the first expansion valve 15a is decreased and the throttle opening of the second expansion valve 15b is increased as the target blowing temperature TAO increases.
  • the outdoor heat exchanger 16 may be switched from a state of functioning as a radiator to a state of functioning as an evaporator, and the heating capacity of the blown air in the indoor condenser 12 may be changed.
  • the target evaporation temperature TEO in the indoor evaporator 18 is determined based on the target blowing temperature TAO with reference to a control map stored in the air conditioning control device 40 in advance, and the refrigerant evaporation detected by the evaporator temperature sensor 56 is determined.
  • the operation of the compressor may be controlled so that the temperature (evaporator temperature) Tefin approaches the target evaporation temperature TEO.
  • target evaporation temperature TEO so that it may fall with the fall of target blowing temperature TAO.
  • the relationship between the refrigerant flow rate and the set pressure Pset in the evaporating pressure adjusting valve 19 is stored in advance in the air conditioning control device 40, whereby the evaporating pressure adjusting valve 19 is activated.
  • the determination as to whether or not the evaporation pressure adjusting valve 19 is operating is not limited to this.
  • an outlet-side low pressure sensor for detecting the outlet-side refrigerant pressure Pso of the evaporation pressure adjusting valve 19 is provided, and a pressure reference (Pe ⁇ Peo) between the low-pressure side refrigerant pressure Pe and the outlet-side refrigerant pressure Pso is a predetermined reference.
  • a pressure reference Pe ⁇ Peo
  • the pressure difference is greater than or equal to the pressure difference, it may be determined that the evaporation pressure adjustment valve 19 is operating.
  • a water-refrigerant heat exchanger may be adopted as a heat radiator, and high-pressure refrigerant and blown air may be indirectly heat-exchanged via a heat medium.
  • the heat medium circulation circuit may be circulated using cooling water of the internal combustion engine as a heat medium.
  • variable capacity compressor that obtains a rotational driving force from an internal combustion engine or the like, which is an example in which an electric compressor is employed as the compressor 11, may be employed.
  • the example in which the evaporation pressure adjusting valve 19 in which each constituent member is formed of metal has been described.
  • a cylindrical valve body portion 92 formed of resin is used.
  • the bellows 93 one having a bellophram formed of a bottomed cylindrical (cup-shaped) rubber may be employed.
  • the target evaporation pressure determining unit may be configured in another control step.
  • the target evaporation pressure PEO may be determined together with the target blowing temperature TAO.
  • the target evaporation pressure determination unit is configured by the control step S3.
  • each operation mode is switched by executing the air conditioning control program.
  • the switching of each operation mode is not limited to this.
  • an operation mode setting switch for setting each operation mode may be provided on the operation panel, and the heating mode, the cooling mode, and the dehumidifying heating mode may be switched according to an operation signal of the operation mode setting switch.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

　L'invention concerne un dispositif à cycle de congélation faisant appel à une soupape de régulation de pression d'évaporation (19) dont l'étendue d'augmentation de l'aire de passage de réfrigérant par rapport à l'augmentation de la valeur de déplacement (L) d'un corps de soupape cylindrique (92) est supérieure à l'étendue d'augmentation qui serait observée dans le cas d'une augmentation linéaire proportionnellement à une augmentation de la valeur de déplacement (L); et la pression de consigne (Pset) est inférieure à la pression d'évaporation cible (PEO). En outre, le fonctionnement du compresseur (11) est commandé d'une manière telle que la pression d'évaporation de réfrigérant (Pe) dans l'évaporateur est amenée approximativement à la pression d'évaporation cible (PEO), dont la valeur est la plus élevée entre la pression de consigne (Pset) et la pression d'évaporation cible (PEO). En procédant de la sorte, une interférence de commande se produisant du fait de l'utilisation de la soupape de régulation de pression d'évaporation (19) est limitée au minimum, et la performance de refroidissement requise d'un évaporateur intérieur peut être produite, sans augmenter nécessairement la puissance consommée par le compresseur.
PCT/JP2015/000094 2014-01-21 2015-01-12 Dispositif à cycle de congélation Ceased WO2015111379A1 (fr)

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WO2017023632A1 (fr) 2015-08-03 2017-02-09 Hill Phoenix, Inc. Système de réfrigération au co2 à échange de chaleur direct de co2
WO2019044353A1 (fr) * 2017-08-31 2019-03-07 株式会社デンソー Cycle frigorifique
WO2019065013A1 (fr) * 2017-09-28 2019-04-04 株式会社デンソー Dispositif à cycle frigorifique
JP2023179585A (ja) * 2018-07-17 2023-12-19 ダイキン工業株式会社 自動車用冷凍サイクル装置
US12221577B2 (en) 2019-01-30 2025-02-11 Daikin Industries, Ltd. Composition containing refrigerant, and refrigeration method using said composition, operating method for refrigeration device, and refrigeration device

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JP6582843B2 (ja) * 2015-10-06 2019-10-02 株式会社デンソー 冷凍サイクル装置
JP6699460B2 (ja) * 2016-08-30 2020-05-27 株式会社デンソー 冷凍サイクル装置
JP7687085B2 (ja) * 2021-06-29 2025-06-03 株式会社デンソー 蒸発圧力調整弁
WO2025074520A1 (fr) * 2023-10-03 2025-04-10 三菱電機株式会社 Dispositif à cycle frigorifique

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JP2012225637A (ja) * 2011-04-04 2012-11-15 Denso Corp 冷凍サイクル装置
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WO2012118198A1 (fr) * 2011-03-03 2012-09-07 サンデン株式会社 Climatiseur utilisable sur un véhicule
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WO2013172201A1 (fr) * 2012-05-14 2013-11-21 株式会社デンソー Clapet de réglage de débit pour cycle de réfrigération

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Publication number Priority date Publication date Assignee Title
WO2017023632A1 (fr) 2015-08-03 2017-02-09 Hill Phoenix, Inc. Système de réfrigération au co2 à échange de chaleur direct de co2
EP3341662A4 (fr) * 2015-08-03 2019-03-27 Hill Phoenix Inc. Système de réfrigération au co2 à échange de chaleur direct de co2
US10502461B2 (en) 2015-08-03 2019-12-10 Hill Phoeniz, Inc. CO2 refrigeration system with direct CO2 heat exchange for building temperature control
WO2019044353A1 (fr) * 2017-08-31 2019-03-07 株式会社デンソー Cycle frigorifique
JP2019045034A (ja) * 2017-08-31 2019-03-22 株式会社デンソー 冷凍サイクル装置
WO2019065013A1 (fr) * 2017-09-28 2019-04-04 株式会社デンソー Dispositif à cycle frigorifique
JP2023179585A (ja) * 2018-07-17 2023-12-19 ダイキン工業株式会社 自動車用冷凍サイクル装置
US12221577B2 (en) 2019-01-30 2025-02-11 Daikin Industries, Ltd. Composition containing refrigerant, and refrigeration method using said composition, operating method for refrigeration device, and refrigeration device

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