WO2023042588A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2023042588A1
WO2023042588A1 PCT/JP2022/030741 JP2022030741W WO2023042588A1 WO 2023042588 A1 WO2023042588 A1 WO 2023042588A1 JP 2022030741 W JP2022030741 W JP 2022030741W WO 2023042588 A1 WO2023042588 A1 WO 2023042588A1
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WIPO (PCT)
Prior art keywords
refrigerant
expansion valve
connection port
air
heat exchanger
Prior art date
Application number
PCT/JP2022/030741
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English (en)
Japanese (ja)
Inventor
憲彦 榎本
大輝 加藤
祐一 加見
淳 稲葉
Original Assignee
株式会社デンソー
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Publication of WO2023042588A1 publication Critical patent/WO2023042588A1/fr

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00Compression machines, plants or systems with non-reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/20Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00Compression machines, plants or systems, with several condenser circuits
    • F25B6/04Compression machines, plants or systems, with several condenser circuits arranged in series

Definitions

  • the present disclosure relates to a refrigeration cycle device.
  • Patent Document 1 describes a refrigeration cycle device capable of switching between a cooling mode and a heating mode.
  • a branching portion, a merging portion, and a switching valve are provided in order to enable switching between the cooling mode and the heating mode.
  • a heat exchange target fluid is a fluid (for example, air or water) that exchanges heat with a refrigerant.
  • the present disclosure aims to make it possible to adjust the degree of subcooling of the refrigerant and the pressure, temperature or flow rate of the refrigerant, or the temperature of the heat exchange target fluid with a simple configuration.
  • a refrigeration cycle device includes a refrigerant valve and a controller.
  • the refrigerant valve has a first connection port, a second connection port, a third connection port, and a valve body.
  • the first connection port is connected to a first heat exchanger that heat-exchanges the refrigerant.
  • the second connection port is connected to the inlet side of a gas-liquid separator that separates the gas-liquid refrigerant.
  • a refrigerant passage through which a refrigerant flows is connected to the third connection port.
  • the valve body switches the communication state of the first connection port, the second connection port, and the third connection port, and reduces the pressure of the refrigerant.
  • the control unit switches between the first operation mode and the second operation mode.
  • the first mode of operation after the refrigerant condenses in the first heat exchanger, it flows through the refrigerant valve into the gas-liquid separator.
  • the second operation mode after the refrigerant flows through the first heat exchanger, it flows out from the third connection port via the refrigerant valve.
  • the degree of supercooling of the refrigerant condensed in the first heat exchanger approaches the target degree of supercooling. Control the refrigerant valve so that the temperature approaches the target value.
  • the adjustment of the degree of subcooling in the first operation mode and the adjustment of the pressure, temperature or flow rate of the refrigerant in the second operation mode can be realized with one refrigerant valve. Therefore, the degree of supercooling of the refrigerant and the pressure, temperature or flow rate of the refrigerant, or the temperature of the heat exchange target fluid can be adjusted with a simple configuration.
  • a refrigeration cycle device includes a refrigerant valve and a controller.
  • the refrigerant valve has a first connection port, a second connection port, a third connection port, and a valve body.
  • the first connection port is connected to a first heat exchanger that heat-exchanges the refrigerant.
  • the second connection port is connected to the inlet side of a gas-liquid separator that separates the gas-liquid refrigerant.
  • a refrigerant passage through which a refrigerant flows is connected to the third connection port.
  • the valve body switches the communication state of the first connection port, the second connection port, and the third connection port, and reduces the pressure of the refrigerant.
  • the control unit switches between the first operation mode and the second operation mode.
  • the first mode of operation after the refrigerant condenses in the first heat exchanger, it flows through the refrigerant valve into the gas-liquid separator.
  • the second operation mode the refrigerant that has flowed into the refrigerant valve through the third connection port flows into the first heat exchanger through the first connection port.
  • the degree of supercooling of the refrigerant condensed in the first heat exchanger approaches the target degree of supercooling. Control the refrigerant valve so that the temperature approaches the target value.
  • the adjustment of the degree of subcooling in the first operation mode and the adjustment of the pressure, temperature or flow rate of the refrigerant in the second operation mode can be realized with one refrigerant valve. Therefore, the degree of supercooling of the refrigerant and the pressure, temperature or flow rate of the refrigerant, or the temperature of the heat exchange target fluid can be adjusted with a simple configuration.
  • FIG. 3 showing a state in which the second connection port is fully closed and the third connection port is fully open; It is a sectional view of the 1st three-way expansion valve of a 1st embodiment, and shows the state where the 2nd connection port is fully closed, and the 3rd connection port is made into the throttle opening. It is a sectional view of the 1st three-way expansion valve of a 1st embodiment, and shows the state where the 2nd connection port is restricted opening, and the 3rd connection port is fully closed. It is a block diagram showing an electric control part of the vehicle air conditioner of the first embodiment.
  • FIG. 4 is a Mollier diagram showing changes in the state of the refrigerant in the heating mode of the refrigeration cycle apparatus of the first embodiment; It is a Mollier diagram which shows the change of the state of a refrigerant
  • FIG. 4 is a cross-sectional view of the four-way expansion valve of the second embodiment, showing a state in which the first connection port and the third connection port 32c are communicated with each other with a small throttle opening, and the second connection port and the fourth connection port are closed; ing.
  • FIG. 4 is a cross-sectional view of the four-way expansion valve of the second embodiment, showing a state in which the first connection port and the third connection port 32c are communicated with each other with a large throttle opening, and the second connection port and the fourth connection port are closed; ing.
  • FIG. 4 is a cross-sectional view of the four-way expansion valve of the second embodiment, showing a state in which the first connection port and the third connection port 32c are communicated with each other with a large throttle opening, and the second connection port and the fourth connection port are closed; ing.
  • FIG. 4 is a cross-sectional view of the four-way expansion valve of the second embodiment, in which the first connection port and the second connection port are communicated in a throttled state, and the third connection port and the fourth connection port are communicated in a fully open state; is shown. It is a whole block diagram of the refrigerating-cycle apparatus of 3rd Embodiment. It is a whole block diagram of the refrigerating-cycle apparatus of 4th Embodiment.
  • FIG. 1 A first embodiment of a refrigeration cycle apparatus 10 according to the present disclosure will be described with reference to FIGS. 1 to 3.
  • FIG. A refrigeration cycle device 10 shown in FIG. 1 is applied to a vehicle air conditioner mounted on an electric vehicle.
  • An electric vehicle is a vehicle that obtains driving force for running from an electric motor.
  • the vehicle air conditioner of this embodiment air-conditions the interior of the vehicle, which is a space to be air-conditioned, in an electric vehicle.
  • the refrigeration cycle device 10 cools or heats the air blown into the vehicle interior in the vehicle air conditioner. Therefore, the temperature adjustment object of the refrigerating cycle device 10 is air.
  • the refrigeration cycle device 10 is configured to be able to switch refrigerant circuits in order to air-condition the interior of the vehicle.
  • the refrigeration cycle device 10 employs an HFO-based refrigerant (specifically, R1234yf) as a refrigerant.
  • the refrigeration cycle device 10 constitutes a vapor compression subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant.
  • Refrigerant oil (specifically, PAG oil) for lubricating the compressor 11 is mixed in the refrigerant. Some of the refrigerating machine oil circulates through the cycle together with the refrigerant.
  • the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10 .
  • the compressor 11 is arranged in the drive unit room on the front side of the passenger compartment.
  • the drive device chamber defines a space in which at least part of a drive device (for example, an electric motor) for outputting driving force for running is arranged.
  • the compressor 11 is an electric compressor in which a fixed displacement type compression mechanism with a fixed displacement is rotationally driven by an electric motor. Compressor 11 has its rotation speed (that is, refrigerant discharge pressure and refrigerant flow rate) controlled by a control signal output from control device 50 .
  • the refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11 .
  • the indoor condenser 12 is arranged inside the casing 41 of the indoor air conditioning unit 40, as shown in FIG.
  • the indoor condenser 12 is a heat radiating section that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and air to radiate heat from the high-pressure refrigerant.
  • the indoor condenser 12 is a heating unit that heats air using the high-pressure refrigerant discharged from the compressor 11 as a heat source.
  • the indoor condenser 12 is the first heat exchanger.
  • the refrigerant outlet of the indoor condenser 12 is connected to the first connection port 30a side of the first three-way expansion valve 30 .
  • the first three-way expansion valve 30 is a refrigerant valve and has a first connection port 30a, a second connection port 30b and a third connection port 30c that communicate with each other.
  • the inlet side of the receiver 15 is connected to the second connection port 30b of the first three-way expansion valve 30 .
  • the refrigerant inlet side of the outdoor heat exchanger 18 is connected to the third connection port 30c of the first three-way expansion valve 30 via the high-pressure refrigerant passage 21c and the first three-way joint 13a.
  • the high-pressure refrigerant passage 21c is a refrigerant passage through which high-pressure refrigerant flows.
  • the first three-way expansion valve 30 is an opening/closing section that opens and closes the second connection port 30b and the third connection port 30c.
  • the first three-way expansion valve 30 is a decompression unit that decompresses the refrigerant flowing in from the first connection port 30a and adjusts the flow rate of the refrigerant flowing out downstream.
  • the refrigeration cycle device 10 includes a first three-way joint 13a, a second three-way joint 13b, a third three-way joint 13c, and a fourth three-way joint 13d.
  • a three-way joint one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
  • the first three-way joint 13a to the fourth three-way joint 13d use one of the three inflow ports as the inflow port, and when two of the three inflow ports are used as the outflow port, the flow of the refrigerant flowing in from one inflow port is controlled. It becomes a branching part. Two of the three inlets and outlets of the first three-way joint 13a to the fourth three-way joint 13d are used as inlets. It becomes a confluence part for merging.
  • first three-way joint 13a, the second three-way joint 13b, and the third three-way joint 13c are connected so as to function as a confluence.
  • fourth three-way joint 13d is connected so as to function as a branch.
  • the third three-way joint 13c has an inlet-side passage 21a, which is a refrigerant passage extending from the second connection port 30b of the first three-way expansion valve 30 to the inlet of the receiver 15. connected to the side. Further, the outflow port of the third three-way joint 13c is connected to the inlet side of the receiver 15 in the inlet side passage 21a.
  • the receiver 15 is a gas-liquid separation unit having a gas-liquid separation function. That is, the receiver 15 separates the gas-liquid refrigerant that has flowed out of the heat exchange section that functions as a condenser that condenses the refrigerant in the refrigeration cycle device 10 .
  • the receiver 15 causes part of the separated liquid-phase refrigerant to flow downstream, and stores the remaining liquid-phase refrigerant as surplus refrigerant in the cycle.
  • the outlet side of the receiver 15 is connected to the other inlet of the first three-way joint 13a via the heating expansion valve 16a.
  • a fourth three-way joint 13d and a first check valve 17a are arranged in an outlet-side passage 21b, which is a refrigerant passage connecting the outlet of the receiver 15 and the other inlet of the first three-way joint 13a.
  • the first check valve 17a allows the refrigerant to flow from the outlet side of the receiver 15 to the heating expansion valve 16a side, and prohibits the refrigerant to flow from the heating expansion valve 16a side to the outlet side of the receiver 15.
  • the heating expansion valve 16a is a decompression unit that decompresses the refrigerant flowing out of the receiver 15 and adjusts the flow rate of the refrigerant flowing out downstream.
  • the heating expansion valve 16a is an electric variable throttle mechanism having a valve body configured to change the throttle opening and an electric actuator (specifically, a stepping motor) that displaces the valve body.
  • the operation of the heating expansion valve 16 a is controlled by a control signal (specifically, a control pulse) output from the control device 50 .
  • the heating expansion valve 16a has a full-open function that functions as a mere refrigerant passage without exhibiting a flow rate adjustment action or a refrigerant decompression action by fully opening the valve opening, and a refrigerant passage by fully closing the valve opening. It has a fully closed function to block the passage.
  • the refrigeration cycle device 10 is provided with a cooling expansion valve 16b, as will be described later.
  • the basic configuration of the cooling expansion valve 16b is the same as that of the heating expansion valve 16a.
  • the heating expansion valve 16a and the like may be formed by combining a variable throttle mechanism that does not have a fully closed function and an open/close valve.
  • the inflow port of the fourth three-way joint 13d is connected to the outlet side of the receiver 15 in the outlet side passage 21b.
  • One outflow port of the fourth three-way joint 13d is connected to the inlet side of the first check valve 17a in the outlet side passage 21b.
  • the other outflow port of the fourth three-way joint 13d is connected to the inflow port side of the cooling expansion valve 16b.
  • the refrigerant inlet side of the outdoor heat exchanger 18 is connected to the outlet of the first three-way joint 13a.
  • the outdoor heat exchanger 18 is a heat exchanger that exchanges heat between the refrigerant flowing out from the outlet of the first three-way joint 13a and the outside air blown from the outside air fan 18A.
  • the outdoor heat exchanger 18 is arranged on the front side in the driving device room. Therefore, when the vehicle is running, the outdoor heat exchanger 18 can be exposed to running wind.
  • the outdoor heat exchanger 18 is a first heat exchanger or a second heat exchanger.
  • a refrigerant outlet of the outdoor heat exchanger 18 is connected to the first connection port 31a of the second three-way expansion valve 31 .
  • the second connection port 31b of the second three-way expansion valve 31 is connected to the other inlet side of the third three-way joint 13c.
  • One inlet side of the second three-way joint 13b is connected to the third connection port 31c of the second three-way expansion valve 31 .
  • the second three-way expansion valve 31 is a refrigerant valve.
  • the second three-way expansion valve 31 is an opening/closing portion that opens and closes the second connection port 31b and the third connection port 31c.
  • the second three-way expansion valve 31 is a decompression unit that decompresses the refrigerant flowing in from the first connection port 31a and adjusts the flow rate of the refrigerant flowing out downstream.
  • the second three-way expansion valve 31 opens and closes the suction side passage 21d, which is a refrigerant passage from one outlet of the third three-way joint 13c to one inlet of the second three-way joint 13b.
  • the suction port side of the compressor 11 is connected to the outflow port of the second three-way joint 13b.
  • the inlet side of the cooling expansion valve 16b is connected to the other outlet of the fourth three-way joint 13d arranged in the outlet-side passage 21b.
  • the cooling expansion valve 16b is a decompression unit that decompresses the refrigerant flowing out of the receiver 15 and adjusts the flow rate of the refrigerant that flows downstream.
  • the refrigerant inlet side of the indoor evaporator 19 is connected to the outlet of the cooling expansion valve 16b.
  • the indoor evaporator 19 is arranged inside the casing 41 of the indoor air conditioning unit 40 .
  • the indoor evaporator 19 is an evaporator that exchanges heat with the air blown from the indoor blower 42 to evaporate the low-pressure refrigerant decompressed by the cooling expansion valve 16b.
  • the indoor evaporator 19 is an air cooling unit that cools the air by evaporating the low-pressure refrigerant and exerting an endothermic effect.
  • the refrigerant outlet of the indoor evaporator 19 is connected to the other inlet of the second three-way joint 13b.
  • the refrigerant circuit can be switched by opening and closing the refrigerant passage with the first three-way expansion valve 30 and the second three-way expansion valve 31.
  • the first three-way expansion valve 30 constitutes a first refrigerant circuit switching section that guides the refrigerant flowing out of the indoor condenser 12 to one of the receiver 15 side and the outdoor heat exchanger 18 side.
  • the second three-way expansion valve 31 constitutes a second refrigerant circuit switching unit that guides the refrigerant that has flowed out of the outdoor heat exchanger 18 to one of the suction port side of the compressor 11 and the receiver 15 side.
  • the indoor air-conditioning unit 40 is a unit for blowing out air whose temperature is appropriately adjusted to an appropriate location in the vehicle interior in the vehicle air-conditioning system.
  • the interior air-conditioning unit 40 is arranged inside the instrument panel (that is, the instrument panel) at the forefront of the vehicle interior.
  • the indoor air conditioning unit 40 has a casing 41 that forms an air passage for air.
  • An indoor fan 42, an indoor evaporator 19, an indoor condenser 12, and the like are arranged in an air passage formed in the casing 41.
  • the casing 41 is made of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.
  • An inside/outside air switching device 43 is arranged on the most upstream side of the air flow of the casing 41 .
  • the inside/outside air switching device 43 switches and introduces inside air (vehicle interior air) and outside air (vehicle exterior air) into the casing 41 .
  • the operation of the electric actuator for driving the inside/outside air switching device 43 is controlled by a control signal output from the control device 50 .
  • An indoor fan 42 is arranged downstream of the inside/outside air switching device 43 in the air flow.
  • the indoor air blower 42 blows the air sucked through the inside/outside air switching device 43 into the vehicle interior.
  • the indoor blower 42 is an electric blower that drives a centrifugal multi-blade fan with an electric motor.
  • the indoor fan 42 has its rotation speed (that is, air blowing capacity) controlled by a control voltage output from the control device 50 .
  • the indoor evaporator 19 and the indoor condenser 12 are arranged in this order with respect to the air flow on the downstream side of the indoor blower 42 in the air flow. That is, the indoor evaporator 19 is arranged upstream of the indoor condenser 12 in the air flow.
  • a cold air bypass passage 45 is formed in the casing 41 so that the air that has passed through the indoor evaporator 19 bypasses the indoor condenser 12 and flows downstream.
  • An air mix door 44 is arranged on the air flow downstream side of the indoor evaporator 19 and on the air flow upstream side of the indoor condenser 12 .
  • the air mix door 44 adjusts the ratio of the amount of air passing through the indoor condenser 12 and the amount of air passing through the cold air bypass passage 45 in the air after passing through the indoor evaporator 19 .
  • the operation of the electric actuator for driving the air mix door is controlled by a control signal output from the control device 50 .
  • a mixing space 46 in which the air heated by the indoor condenser 12 and the air not heated by the indoor condenser 12 that passes through the cold air bypass passage 45 are mixed. is provided. Furthermore, an opening hole (not shown) for blowing out the air (air-conditioned air) mixed in the mixing space 46 into the vehicle interior is arranged at the most downstream portion of the air flow of the casing 41 .
  • the temperature of the conditioned air mixed in the mixing space 46 can be adjusted by adjusting the air volume ratio between the air volume that the air mix door 44 passes through the indoor condenser 12 and the air volume that passes through the cold air bypass passage 45. can be done. Then, the temperature of the air blown into the passenger compartment from each opening can be adjusted.
  • a face opening hole, a foot opening hole, and a defroster opening hole are provided as opening holes.
  • the face opening hole is an opening hole for blowing the conditioned air toward the upper body of the passenger in the passenger compartment.
  • the foot opening hole is an opening hole for blowing the conditioned air toward the passenger's feet.
  • the defroster opening hole is an opening hole for blowing the conditioned air toward the inner surface of the vehicle front window glass.
  • a blowout mode switching door (not shown) is arranged on the upstream side of these opening holes.
  • the blow-out mode switching door switches between openings for blowing conditioned air by opening and closing each opening.
  • the operation of the electric actuator for driving the blowout mode switching door is controlled by a control signal output from the control device 50 .
  • FIGS. A basic configuration of the second three-way expansion valve 31 is similar to that of the first three-way expansion valve 30 . Therefore, reference numerals corresponding to the components of the second three-way expansion valve 31 are added in parentheses in FIGS. 3 to 6, and illustration of the second three-way expansion valve 31 is omitted.
  • the first three-way expansion valve 30 has a casing 301 in which a first connection port 30a, a second connection port 30b and a third connection port 30c are formed, and can change throttle opening degrees of the second connection port 30b and the third connection port 30c. and an electric actuator 303 (specifically, a stepping motor) for displacing the valve body.
  • the operation of the first three-way expansion valve 30 is controlled by control signals (specifically, control pulses) output from the control device 50 .
  • the first three-way expansion valve 30 has a fully open function that functions as a mere refrigerant passage without exhibiting a flow rate adjustment action or a refrigerant decompression action by fully opening the valve opening, and by fully closing the valve opening. It has a fully closed function to block the refrigerant passage.
  • FIG. 4 shows a state in which the valve body 302 fully closes the second connection port 30b and fully opens the third connection port 30c.
  • FIG. 5 shows a state in which the valve body 302 fully closes the second connection port 30b and sets the third connection port 30c to a throttle opening that exerts a refrigerant decompression action.
  • FIG. 6 shows a state in which the valve body 302 sets the second connection port 30b to a throttle opening that exhibits a refrigerant decompression action and fully closes the third connection port 30c.
  • the valve body 302 can adjust the throttle opening by adjusting the opening areas of the second connection port 30b and the third connection port 30c.
  • the valve body 302 has a spherical shape, is accommodated in a spherical space formed in the casing 301, and is rotatable around the axis of the first connection port 30a.
  • a coolant channel 302 a is formed in the valve body 302 .
  • the refrigerant flow path 302a penetrates the interior of the valve body 302 and opens at two locations on the peripheral surface of the valve body 302 .
  • One opening of the coolant channel 302a is always in communication with the first connection port 30a.
  • the other opening of the coolant channel 302a communicates or disconnects with the second connection port 30b and the third connection port 30c depending on the rotational position of the valve body 302. As shown in FIG. That is, depending on the rotational position of the valve body 302, the state of communication between the refrigerant flow path 302a and the second connection port 30b and the third connection port 30c is switched.
  • the portion of the peripheral surface of the valve body 302 where the coolant channel 302a is not open closes the second connection port 30b, and the coolant channel 302a of the peripheral surface of the valve body 302 is open.
  • the portion connected to the third connection port 30c communicates with the maximum communication area.
  • the portion of the peripheral surface of the valve body 302 where the coolant channel 302a is not open closes the second connection port 30b, and the coolant channel 302a of the peripheral surface of the valve body 302 is open.
  • the part where it is connected partially communicates with the third connection port 30c.
  • the portion of the peripheral surface of the valve body 302 where the coolant channel 302a is open partially communicates with the second connection port 30b, and the coolant channel 302a of the peripheral surface of the valve body 302 The portion where is not open blocks the third connection port 30c.
  • the second three-way expansion valve 31 like the first three-way expansion valve 30, has a first connection port 31a, a second connection port 31b, and a third connection port 31c.
  • the control device 50 is composed of a well-known microcomputer including CPU, ROM, RAM, etc. and its peripheral circuits.
  • the control device 50 performs various calculations and processes based on the air conditioning control program stored in the ROM, and controls various control target devices 11, 16a, 16b, 30, 31, 42, 43, 44, etc. connected to the output side. controls the operation of
  • Control sensors include an inside air temperature sensor 51a, an outside air temperature sensor 51b, a solar radiation sensor 51c, a high pressure sensor 51d, an air conditioning air temperature sensor 51e, an evaporator temperature sensor 51f, an evaporator pressure sensor 51g, an outdoor unit temperature sensor 51h, An outdoor unit pressure sensor 51i, a condenser temperature sensor 51j, and a condenser pressure sensor 51k are included.
  • the inside air temperature sensor 51a is an inside air temperature detection unit that detects the inside air temperature Tr, which is the temperature inside the vehicle compartment.
  • the outside air temperature sensor 51b is an outside air temperature detection unit that detects the outside air temperature Tam, which is the temperature outside the vehicle compartment.
  • the solar radiation amount sensor 51c is a solar radiation amount detection unit that detects the solar radiation amount As irradiated into the vehicle interior.
  • the high pressure sensor 51d is a high pressure detection unit that detects the high pressure Pd, which is the pressure of the high pressure refrigerant discharged from the compressor 11.
  • the air-conditioning air temperature sensor 51e is an air-conditioning air temperature detection unit that detects the temperature TAV of air blown out from the mixing space 46 into the vehicle interior.
  • the evaporator temperature sensor 51f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Te in the indoor evaporator 19.
  • the evaporator temperature sensor 51f of the present embodiment specifically detects the temperature of the outlet side refrigerant of the indoor evaporator 19 .
  • the evaporator pressure sensor 51g is an evaporator pressure detection unit that detects the refrigerant evaporation pressure Pe in the indoor evaporator 19.
  • the evaporator pressure sensor 51g of this embodiment specifically detects the pressure of the refrigerant on the outlet side of the indoor evaporator 19 .
  • the outdoor unit temperature sensor 51h is an outdoor unit temperature detection unit that detects the outdoor unit refrigerant temperature T1, which is the temperature of the refrigerant flowing through the outdoor heat exchanger 18.
  • the outdoor unit temperature sensor 51h of the present embodiment specifically detects the temperature of the refrigerant on the outlet side of the outdoor heat exchanger 18 .
  • the outdoor unit pressure sensor 51i is an outdoor unit pressure detection unit that detects the outdoor unit refrigerant pressure P1, which is the pressure of the refrigerant flowing through the outdoor heat exchanger 18.
  • the outdoor unit pressure sensor 51i of the present embodiment specifically detects the pressure of the refrigerant on the outlet side of the outdoor heat exchanger 18 .
  • the condenser temperature sensor 51j is a condenser temperature detection unit that detects a condenser refrigerant temperature T2, which is the temperature of the refrigerant flowing through the indoor condenser 12.
  • the condenser pressure sensor 51k is a condenser pressure detection unit that detects a condenser refrigerant pressure P2 that is the pressure of the refrigerant flowing through the indoor condenser 12 .
  • the input side of the control device 50 is connected to an operation panel 52 arranged near the instrument panel in the front part of the passenger compartment. Operation signals from various operation switches provided on an operation panel 52 are input to the control device 50 .
  • Various operation switches provided on the operation panel 52 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and the like.
  • the auto switch is an operation switch for setting or canceling automatic control operation of the refrigeration cycle device 10 .
  • the air conditioner switch is an operation switch for requesting that the indoor evaporator 19 cool the air.
  • the air volume setting switch is an operation switch for manually setting the air volume of the indoor fan 42 .
  • the temperature setting switch is an operation switch for setting a target temperature Tset in the passenger compartment.
  • control device 50 of the present embodiment is integrally configured with a control unit that controls various controlled devices connected to the output side thereof. Therefore, the configuration (that is, hardware and software) that controls the operation of each controlled device constitutes a control unit that controls the operation of each controlled device.
  • the configuration for controlling the operation of the first three-way expansion valve 30 and the second three-way expansion valve 31, which are refrigerant circuit switching units, constitutes a refrigerant circuit control unit 50a.
  • the refrigeration cycle device 10 is configured to be able to switch refrigerant circuits in order to air-condition the interior of the vehicle.
  • a refrigerant circuit in a heating mode in order to air-condition the vehicle interior, a refrigerant circuit in a heating mode, a refrigerant circuit in a cooling mode, a refrigerant circuit in a parallel dehumidifying and heating mode, a refrigerant circuit in a series dehumidifying and heating mode, You can switch circuits.
  • the heating mode is an operation mode in which heated air is blown into the vehicle interior.
  • Cooling mode is an operation mode in which cooled air is blown into the vehicle interior.
  • the parallel dehumidifying/heating mode and the serial dehumidifying/heating mode are operation modes in which cooled and dehumidified air is reheated and blown into the passenger compartment.
  • the switching of these operation modes is performed by executing an air conditioning control program stored in the control device 50 in advance.
  • the air conditioning control program is executed when the auto switch of the operation panel 52 is turned on.
  • the air conditioning control program switches the operation mode based on detection signals from various control sensors and operation signals from the operation panel. The operation of each operation mode will be described below.
  • the control device 50 puts the second connection port 30b of the first three-way expansion valve 30 into a throttled state that exerts a refrigerant pressure reducing action, and the third connection port 30c of the first three-way expansion valve 30. is fully closed, the second connection port 31b of the second three-way expansion valve 31 is fully closed, and the third connection port 31c of the second three-way expansion valve 31 is fully open. Further, the control device 50 puts the heating expansion valve 16a into a throttled state that exerts a refrigerant decompression expansion action (furthermore, the opening diameter is variable), and puts the cooling expansion valve 16b into a fully closed state.
  • the control device 50 controls the operation of various controlled devices.
  • the controller 50 controls the discharge capacity so that the high pressure Pd detected by the high pressure sensor 51d approaches the target high pressure PDO.
  • the target high pressure PDO is determined by referring to a heating mode control map stored in advance in the controller 50 based on the target outlet temperature TAO.
  • the target blowout temperature TAO is calculated using detection signals from various control sensors and operation signals from the operation panel.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the control device 50 controls the throttle opening so that the subcooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the predetermined target subcooling degree KSC1.
  • Degree of supercooling SC1 is calculated from condenser refrigerant temperature T2 detected by condenser temperature sensor 51j and condenser refrigerant pressure P2 detected by condenser pressure sensor 51k.
  • the degree of subcooling SC1 may be estimated and calculated from the difference between the saturation temperature of the refrigerant obtained from the value of the high pressure Pd and the temperature of the air passing through the indoor condenser 12 .
  • the control device 50 controls the throttle opening so that the degree of superheat SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches a predetermined target degree of superheat KSH.
  • the degree of superheat SH1 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.
  • the controller 50 controls the opening so that the blown air temperature TAV detected by the conditioned air temperature sensor 51e approaches the target blown temperature TAO.
  • the opening degree of the air mix door 44 may be controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the indoor condenser 12 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air.
  • the refrigerant that has flowed out of the indoor condenser 12 is decompressed by the first three-way expansion valve 30 and flows into the receiver 15 via the inlet side passage 21a.
  • the throttle opening degree of the first three-way expansion valve 30 is controlled so that the supercooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the target supercooling degree KSC1.
  • FIG. 8 is a Mollier diagram showing changes in the refrigerant state in the heating mode.
  • the heating mode the refrigerant flowing out of the indoor condenser 12 is decompressed by the first three-way expansion valve 30 , so the pressure of the refrigerant in the receiver 15 becomes lower than the pressure of the high-pressure refrigerant in the indoor condenser 12 .
  • the pressure of the refrigerant in the receiver 15 is on the saturated liquid line with a slope.
  • the refrigerant will have the degree of supercooling SC1.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • a part of the liquid-phase refrigerant separated by the receiver 15 flows into the outlet side passage 21b and the heating expansion valve 16a.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the heating expansion valve 16a is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the heating expansion valve 16a is controlled so that the degree of superheat SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18 via the first three-way joint 13a.
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, absorbs heat from the outside air, and evaporates.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 is sucked into the compressor 11 via the second three-way expansion valve 31, the suction side passage 21d and the second three-way joint 13b and compressed again.
  • the interior of the vehicle can be heated by blowing out the air heated by the indoor condenser 12 into the interior of the vehicle.
  • (b) Cooling Mode In the cooling mode, the control device 50 fully closes the second connection port 30b of the first three-way expansion valve 30, fully opens the third connection port 30c of the first three-way expansion valve 30, and The second connection port 31b of the two-three-way expansion valve 31 is set in a throttled state for exerting a refrigerant decompression effect, and the third connection port 31c of the second three-way expansion valve 31 is set in a fully open state. Further, the control device 50 brings the heating expansion valve 16a into the fully closed state and the cooling expansion valve 16b into the throttle state.
  • the control device 50 controls the operation of various controlled devices. For example, the discharge capacity of the compressor 11 is controlled so that the evaporator temperature Te detected by the evaporator temperature sensor 51f approaches the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined based on the target outlet temperature TAO with reference to a cooling mode control map stored in the controller 50 in advance.
  • the target evaporator temperature TEO is determined to rise as the target blowout temperature TAO rises. Furthermore, the target evaporator temperature TEO is determined to a value within a range (specifically, 1° C. or higher) in which frost formation on the indoor evaporator 19 can be suppressed.
  • control device 50 controls the throttle opening so that the degree of subcooling SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the predetermined target degree of subcooling KSC2.
  • the degree of supercooling SC2 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.
  • the control device 50 controls the throttle opening so that the degree of superheat SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target degree of superheat KSH.
  • the degree of superheat SH2 is calculated from the evaporator temperature Te and the refrigerant evaporation pressure Pe detected by the evaporator pressure sensor 51g.
  • the opening degree of the air mix door 44 is controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the entire amount of air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45 . Therefore, the refrigerant that has flowed into the indoor condenser 12 flows out of the indoor condenser 12 without exchanging heat with air.
  • the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 18 via the first three-way expansion valve 30 and the first three-way joint 13a.
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, releases heat to the outside air, and condenses.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 flows into the receiver 15 via the second three-way expansion valve 31, the third three-way joint 13c and the inlet side passage 21a.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target supercooling degree KSC2.
  • the control of the degree of supercooling SC2 by the second three-way expansion valve 31 is the same as the control of the degree of supercooling SC1 by the first three-way expansion valve 30 in the heating mode described with reference to FIG. 8, so a description thereof will be omitted.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 is sucked into the compressor 11 via the second three-way joint 13b and compressed again.
  • the air cooled by the indoor evaporator 19 is blown into the vehicle interior, thereby cooling the vehicle interior.
  • (c) Parallel Dehumidification and Heating Mode In the parallel dehumidification and heating mode, the controller 50 throttles the second connection port 30b of the first three-way expansion valve 30 and fully closes the third connection port 30c of the first three-way expansion valve 30. state, the second connection port 31b of the second three-way expansion valve 31 is fully closed, and the third connection port 31c of the second three-way expansion valve 31 is throttled. Further, the control device 50 places the heating expansion valve 16a in a throttled state for depressurizing the refrigerant, and places the cooling expansion valve 16b in a throttled state.
  • the refrigerant discharged from the compressor 11 flows through the indoor condenser 12 and the receiver 15 in that order, as indicated by the solid line arrows in FIG. Furthermore, as indicated by the solid line arrow in FIG. 1, it circulates in the order of the receiver 15, the heating expansion valve 16a, the outdoor heat exchanger 18, and the suction port of the compressor 11, and as indicated by the dashed line arrow in FIG. It circulates through the receiver 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11 in this order.
  • the refrigeration cycle device 10 in the parallel dehumidifying and heating mode is switched to a circuit in which the outdoor heat exchanger 18 and the indoor evaporator 19 are connected in parallel with respect to the flow of refrigerant flowing out from the receiver 15 .
  • the control device 50 controls the operation of various controlled devices.
  • the discharge capacity is controlled in the same manner as in the cooling mode.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the throttle opening is controlled so that the supercooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the target supercooling degree KSC1.
  • the throttle opening is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the controller 50 calculates a refrigerant pressure value that allows the outdoor heat exchanger 18 to obtain the required amount of heat exchange.
  • the throttle opening of the second three-way expansion valve 31 may be controlled so that the outdoor unit refrigerant temperature T1 approaches the target temperature TO1.
  • the throttle opening of the second three-way expansion valve 31 may be controlled so that the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target flow rate GO1.
  • the heating expansion valve 16a controls the throttle opening so that the degree of superheat SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target degree of superheat KSH.
  • the throttle opening is controlled so that the degree of superheat SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target degree of superheat KSH.
  • the controller 50 controls the opening so that the blown air temperature TAV detected by the conditioned air temperature sensor 51e approaches the target blown air temperature TAO.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air that has been cooled while passing through the indoor evaporator 19 .
  • the refrigerant that has flowed out of the indoor condenser 12 is decompressed by the first three-way expansion valve 30 and flows into the receiver 15 via the inlet side passage 21a.
  • the throttle opening degree of the first three-way expansion valve 30 is controlled so that the supercooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the target supercooling degree KSC1. be done.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the heating expansion valve 16a through the outlet side passage 21b.
  • Another part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed from the receiver 15 into the heating expansion valve 16a is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the heating expansion valve 16a is controlled so that the outdoor unit refrigerant temperature T1 is lower than the outside air temperature Tam.
  • the low-pressure refrigerant decompressed by the heating expansion valve 16a flows into the outdoor heat exchanger 18 via the first three-way joint 13a.
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, absorbs heat from the outside air, and evaporates.
  • the refrigerant flowing out of the outdoor heat exchanger 18 is decompressed by the second three-way expansion valve 31 and flows into the second three-way joint 13b via the suction side passage 21d.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the refrigerant that has flowed from the receiver 15 into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 flows into the second three-way joint 13b.
  • the flow of refrigerant flowing out of the outdoor heat exchanger 18 and the flow of refrigerant flowing out of the indoor evaporator 19 join.
  • the refrigerant that has flowed out of the second three-way joint 13b is sucked into the compressor 11 and compressed again.
  • dehumidifying and heating the vehicle interior can be performed by reheating the air cooled and dehumidified by the indoor evaporator 19 with the indoor condenser 12 and blowing it into the vehicle interior.
  • (d) Series Dehumidification and Heating Mode In the series dehumidification and heating mode, the control device 50 fully closes the second connection port 30b of the first three-way expansion valve 30, and closes the third connection port 30c of the first three-way expansion valve 30.
  • the throttled state for depressurizing the refrigerant is set, the second connection port 31b of the second three-way expansion valve 31 is throttled, and the third connection port 31c of the second three-way expansion valve 31 is fully closed. Further, the control device 50 brings the heating expansion valve 16a into the fully closed state and the cooling expansion valve 16b into the throttle state.
  • the control device 50 controls the operation of various controlled devices.
  • the discharge capacity is controlled in the same manner as in the cooling mode.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the throttle opening of the first three-way expansion valve 30 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the controller 50 calculates a refrigerant pressure value that allows the outdoor heat exchanger 18 to obtain the required amount of heat exchange.
  • the control device 50 calculates, as the target pressure PO1, a refrigerant pressure value that allows the amount of heat released between the indoor condenser 12 and the outdoor heat exchanger 18 to be appropriately distributed.
  • the throttle opening of the first three-way expansion valve 30 may be controlled so that the outdoor unit refrigerant temperature T1 approaches the target temperature TO1.
  • the throttle opening of the first three-way expansion valve 30 may be controlled so that the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target flow rate GO1.
  • control device 50 controls the throttle opening so that the degree of subcooling SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the predetermined target degree of subcooling KSC2.
  • the degree of supercooling SC2 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.
  • the control device 50 controls the throttle opening so that the degree of superheat SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target degree of superheat KSH.
  • the degree of superheat SH2 is calculated from the evaporator temperature Te and the refrigerant evaporation pressure Pe detected by the evaporator pressure sensor 51g.
  • the controller 50 controls the opening so that the blown air temperature TAV detected by the conditioned air temperature sensor 51e approaches the target blown temperature TAO.
  • the opening degree of the air mix door 44 may be controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the indoor condenser 12 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air.
  • the refrigerant flowing out of the indoor condenser 12 is decompressed by the first three-way expansion valve 30 and flows into the outdoor heat exchanger 18 via the first three-way joint 13a.
  • the throttle opening degree of the first three-way expansion valve 30 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, radiates heat to the outside air, and condenses.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 flows into the receiver 15 via the second three-way expansion valve 31, the third three-way joint 13c and the inlet side passage 21a.
  • the throttle opening degree of the second three-way expansion valve 31 is adjusted so that the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target supercooling degree KSC2, as shown in the Mollier diagram of FIG. controlled.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 is sucked into the compressor 11 via the second three-way joint 13b and compressed again.
  • dehumidifying and heating the vehicle interior can be performed by reheating the air cooled and dehumidified by the indoor evaporator 19 by the indoor condenser 12 and blowing it into the vehicle interior.
  • the refrigeration cycle device 10 switches the refrigerant circuit according to each operation mode, thereby realizing comfortable air conditioning in the vehicle interior.
  • the expansion valve is controlled so that the degree of supercooling approaches the target degree of supercooling.
  • the relationship between the degree of supercooling and the refrigeration efficiency in the refrigeration cycle device 10 will be described.
  • the degree of subcooling is small, the enthalpy difference of the evaporator cannot be large, so it is necessary to flow more refrigerant.
  • the pressure loss of the evaporator increases, so the suction pressure of the compressor decreases and the density of the suctioned refrigerant decreases. Therefore, it is necessary to operate the compressor at a high rotation speed to maintain the flow rate of the refrigerant, so that the compression efficiency of the compressor deteriorates and the refrigerating efficiency deteriorates.
  • the degree of supercooling is high, the ratio of the supercooled liquid in the condenser increases, so the area that can be used for condensing the refrigerant becomes narrower. Then, in order to secure the necessary heat dissipation performance, it is necessary to increase the temperature difference between the heat transfer side fluid and the refrigerant, so that the condensation pressure is balanced to increase. In this case, the higher the cycle high pressure, the higher the compression ratio in the compressor and the lower the compression efficiency.
  • the degree of supercooling that maximizes the cooling efficiency is determined as the target degree of supercooling in each operation mode, and the expansion valve is controlled so that the degree of supercooling approaches the target degree of supercooling. Therefore, refrigeration efficiency can be enhanced as much as possible.
  • the control device 50 controls the degree of subcooling of the refrigerant condensed in the indoor condenser 12 (in other words, the first heat exchanger) in the heating mode and the parallel dehumidification heating mode (in other words, the first operation mode).
  • SC1 approaches the target subcooling degree KSC1
  • the serial dehumidification heating mode in other words, the second operation mode
  • the pressure P1, the temperature T1, or the flow rate G1 flowing through the outdoor heat exchanger 18 approaches the target values PO1, TO1, GO1.
  • the first three-way expansion valve 30 is controlled as follows.
  • one expansion valve (specifically can be realized by the first three-way expansion valve 30). Therefore, it is possible to adjust the degree of supercooling SC1, the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant with a simple configuration.
  • the third connection port 30c of the first three-way expansion valve 30 is connected to the outdoor heat exchanger 18 (in other words, the second heat exchanger) via the high-pressure refrigerant passage 21c.
  • the heat dissipation capacity of the outdoor heat exchanger 18 can be adjusted by adjusting the pressure P1, temperature T1, or flow rate G1 of the refrigerant with the first three-way expansion valve 30.
  • control device 50 causes the supercooling degree SC2 of the refrigerant condensed in the outdoor heat exchanger 18 to approach the target supercooling degree KSC2 in the cooling mode and the series dehumidification heating mode, and in the parallel dehumidification heating mode, the outdoor heat exchange
  • the second three-way expansion valve 31 is controlled so that the pressure P1, temperature T1 or flow rate G1 of the refrigerant flowing through the vessel 18 approaches target values PO1, TO1 and GO1.
  • one expansion valve (specifically can be realized by the second three-way expansion valve 31). Therefore, the supercooling degree SC2, the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant can be adjusted with a simple configuration.
  • the third connection port 31c of the second three-way expansion valve 31 is connected to the compressor 11 via the suction side passage 21d.
  • the heat absorption capacity of the outdoor heat exchanger 18 can be adjusted by adjusting the pressure P1, temperature T1, or flow rate G1 of the refrigerant with the second three-way expansion valve 31.
  • a four-way expansion valve 32 is provided instead of the first three-way expansion valve 30 of the first embodiment.
  • the four-way expansion valve 32 is a refrigerant valve and has a first connection port 32a, a second connection port 32b, a third connection port 32c and a fourth connection port 32d that communicate with each other.
  • a refrigerant outlet of the indoor condenser 12 is connected to the first connection port 32 a of the four-way expansion valve 32 .
  • the inlet side of the receiver 15 is connected to the second connection port 32b of the four-way expansion valve 32 .
  • the first refrigerant inlet/outlet 18a side of the outdoor heat exchanger 18 is connected to the third connection port 32c of the four-way expansion valve 32 .
  • One inlet side of the second three-way joint 13b is connected to the fourth connection port 32d of the four-way expansion valve 32 .
  • the four-way expansion valve 32 is an opening/closing section that opens and closes the first connection port 32a, the second connection port 32b, the third connection port 32c, and the fourth connection port 32d.
  • the four-way expansion valve 32 is a decompression unit that decompresses the refrigerant flowing in from the first connection port 32a or the third connection port 32c and adjusts the flow rate of the refrigerant flowing out downstream.
  • the second refrigerant inlet/outlet 18b side of the outdoor heat exchanger 18 is connected to the first connection port 31a of the second three-way expansion valve 31 .
  • One outlet side of the fourth three-way joint 13d is connected to the third connection port 31c of the second three-way expansion valve 31 .
  • the second connection port 31b of the second three-way expansion valve 31 is connected to the other inlet side of the third three-way joint 13c.
  • the second three-way expansion valve 31 is an opening/closing part that opens and closes the second connection port 31b and the third connection port 31c.
  • the second three-way expansion valve 31 is a decompression unit that decompresses the refrigerant that has flowed in from the upstream side and adjusts the flow rate of the refrigerant that flows out downstream.
  • the refrigerant circuit can be switched by opening and closing the refrigerant passage with the four-way expansion valve 32 and the second three-way expansion valve 31.
  • the four-way expansion valve 32 constitutes a first refrigerant circuit switching unit that guides the refrigerant flowing out of the indoor condenser 12 to one of the receiver 15 side and the outdoor heat exchanger 18 side.
  • the four-way expansion valve 32 constitutes a second refrigerant circuit switching section that guides the refrigerant flowing out of the outdoor heat exchanger 18 to the suction port of the compressor 11 .
  • the four-way expansion valve 32 includes a casing 321 formed with a first connection port 32a, a second connection port 32b, a third connection port 32c and a fourth connection port 32d, a second connection port 32b, a A valve body 322 configured to be able to change the throttle opening degrees of the third connection port 32c and the fourth connection port 32d, a check valve 323 arranged in the second connection port 30b, and an electric actuator (specifically Specifically, it is an electric variable diaphragm mechanism having a stepping motor.
  • the operation of the four-way expansion valve 32 is controlled by control signals (specifically, control pulses) output from the control device 50 .
  • the four-way expansion valve 32 has a full-open function that functions as a mere refrigerant passage without exhibiting a flow rate adjustment action and a refrigerant decompression action by fully opening the valve opening, and a refrigerant passage by fully closing the valve opening. It has a fully closed function that blocks the
  • the valve body 322 is formed with a first coolant channel 322a and a second coolant channel 322b.
  • the first refrigerant flow path 322 a and the second refrigerant flow path 322 b respectively penetrate the interior of the valve body 322 and open at two locations on the peripheral surface of the valve body 322 .
  • One opening of the coolant channel 322a is always in communication with the first connection port 32a.
  • the first refrigerant flow path 322a and the second refrigerant flow path 322b are in communication with or out of communication with the first connection port 32a, the second connection port 32b, the third connection port 32c and the fourth connection port 32d depending on the rotational position of the valve element 322. It becomes communication. That is, depending on the rotational position of the valve body 322, communication between the first refrigerant flow path 322a and the second refrigerant flow path 322b and the first connection port 32a, the second connection port 32b, the third connection port 32c and the fourth connection port 32d state is switched.
  • valve body 322 connects the first connection port 32a and the third connection port 32c and closes the second connection port 32b and the fourth connection port 32d.
  • first coolant channel 322a communicates the first connection port 32a and the third connection port 32c.
  • FIG. 12 shows a state in which the third connection port 32c has a large throttle amount (in other words, a state in which the third connection port 32c has a small throttle opening).
  • FIG. 13 shows a state in which the amount of restriction of the third connection port 32c is small (in other words, a state in which the degree of restriction of the third connection port 32c is large).
  • the second refrigerant flow path 322b communicates the second connection port 32b and the fourth connection port 32d, but the pressure on the side of the second connection port 32b is higher than the pressure on the side of the fourth connection port 32d. Therefore, the check valve 323 closes the second connection port 32b.
  • FIG. 14 shows a state in which the valve body 322 communicates the first connection port 32a and the second connection port 32b in a throttled state, and communicates the third connection port 32c and the fourth connection port 32d in a fully open state. ing. Specifically, the first coolant channel 322a communicates the third connection port 32c and the fourth connection port 32d, and the second coolant channel 322b communicates the first connection port 32a and the second connection port 32b. . In the state of FIG. 14, the opening degree of the throttle can be adjusted by adjusting the communication area between the second refrigerant flow path 322b and the second connection port 32b and the fourth connection port 32d.
  • the refrigeration cycle device 10 switches between a heating mode refrigerant circuit, a cooling mode refrigerant circuit, a parallel dehumidification heating mode, and a series dehumidification heating mode refrigerant circuit in order to air-condition the vehicle interior. be able to.
  • These operation modes are switched by executing an air conditioning control program stored in the controller 50 in advance. The operation of each operation mode will be described below.
  • the control device 50 connects the first connection port 32a and the second connection port 32b of the four-way expansion valve 32 in a throttled state, and connects the third connection port 32c of the four-way expansion valve 32 and the third connection port 32c.
  • 4 connection port 32d is communicated in a fully open state
  • the first connection port 31a and the third connection port 31c of the second three-way expansion valve 31 are communicated in a throttled state
  • the second connection port 31b of the second three-way expansion valve 31 is communicated.
  • the cooling expansion valve 16b is fully closed.
  • the control device 50 controls the operation of various controlled devices.
  • the controller 50 controls the discharge capacity so that the high pressure Pd detected by the high pressure sensor 51d approaches the target high pressure PDO.
  • the target high pressure PDO is determined by referring to a heating mode control map stored in advance in the controller 50 based on the target outlet temperature TAO.
  • the target blowout temperature TAO is calculated using detection signals from various control sensors and operation signals from the operation panel.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the control device 50 controls the opening degree of the throttle so that the subcooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the predetermined target subcooling degree KSC1.
  • Degree of supercooling SC1 is calculated from condenser refrigerant temperature T2 detected by condenser temperature sensor 51j and condenser refrigerant pressure P2 detected by condenser pressure sensor 51k.
  • the controller 50 controls the throttle opening so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the controller 50 calculates a refrigerant pressure value that allows the outdoor heat exchanger 18 to obtain the required amount of heat exchange.
  • control device 50 may control the throttle opening so that the outdoor unit refrigerant temperature T1 approaches the target temperature TO1.
  • the controller 50 may control the opening degree of the throttle so that the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target flow rate GO1.
  • the controller 50 controls the opening so that the blown air temperature TAV detected by the conditioned air temperature sensor 51e approaches the target blown temperature TAO.
  • the opening degree of the air mix door 44 may be controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the indoor condenser 12 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air.
  • the refrigerant that has flowed out of the indoor condenser 12 is decompressed by the four-way expansion valve 32 and flows into the receiver 15 through the inlet side passage 21a.
  • the throttle opening degree of the four-way expansion valve 32 is controlled so that the supercooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the target supercooling degree KSC1.
  • the control of the degree of supercooling SC1 by the four-way expansion valve 32 is the same as the control of the degree of supercooling SC1 by the first three-way expansion valve 30 in the heating mode of the first embodiment described with reference to FIG. 8, so description thereof will be omitted.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the second three-way expansion valve 31 via the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the second three-way expansion valve 31 is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the low-pressure refrigerant decompressed by the second three-way expansion valve 31 flows into the outdoor heat exchanger 18 .
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, absorbs heat from the outside air, and evaporates.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 is sucked into the compressor 11 via the four-way expansion valve 32, the suction side passage 21d and the second three-way joint 13b and compressed again.
  • the interior of the vehicle can be heated by blowing out the air heated by the indoor condenser 12 into the interior of the vehicle.
  • (b) Cooling Mode In the cooling mode, the controller 50 causes the first connection port 32a and the third connection port 32c of the four-way expansion valve 32 to communicate with each other in a fully open state, and the second connection port 32b of the four-way expansion valve 32 communicates with the third connection port 32b. 4 connection port 32d is fully closed, the first connection port 31a and the second connection port 31b of the second three-way expansion valve 31 are connected in a throttled state, and the third connection port 31c of the second three-way expansion valve 31 is closed. Fully closed. Further, the control device 50 puts the cooling expansion valve 16b into the throttle state.
  • the second three-way expansion valve 31, the receiver 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11 are switched to a second circuit that circulates in this order.
  • the control device 50 controls the operation of various controlled devices. For example, the discharge capacity of the compressor 11 is controlled so that the evaporator temperature Te detected by the evaporator temperature sensor 51f approaches the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined based on the target outlet temperature TAO with reference to a cooling mode control map stored in the controller 50 in advance.
  • the target evaporator temperature TEO is determined to rise as the target blowout temperature TAO rises. Furthermore, the target evaporator temperature TEO is determined to a value within a range (specifically, 1° C. or higher) in which frost formation on the indoor evaporator 19 can be suppressed.
  • control device 50 controls the throttle opening so that the degree of subcooling SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the predetermined target degree of subcooling KSC2.
  • the degree of supercooling SC2 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.
  • the control device 50 controls the throttle opening so that the degree of superheat SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target degree of superheat KSH.
  • the degree of superheat SH2 is calculated from the evaporator temperature Te and the refrigerant evaporation pressure Pe detected by the evaporator pressure sensor 51g.
  • the opening degree of the air mix door 44 is controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the entire amount of air that has passed through the indoor evaporator 19 flows into the cold air bypass passage 45 . Therefore, the refrigerant that has flowed into the indoor condenser 12 flows out of the indoor condenser 12 without exchanging heat with air.
  • the refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchanger 18 via the four-way expansion valve 32 .
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, releases heat to the outside air, and condenses.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 flows into the receiver 15 via the second three-way expansion valve 31, the third three-way joint 13c and the inlet side passage 21a.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target supercooling degree KSC2.
  • the control of the degree of supercooling SC2 by the second three-way expansion valve 31 is the same as the control of the degree of supercooling SC2 by the second three-way expansion valve 31 in the cooling mode of the first embodiment, so a description thereof will be omitted.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the outlet side passage 21b and the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 is sucked into the compressor 11 via the second three-way joint 13b and compressed again.
  • the air cooled by the indoor evaporator 19 is blown into the vehicle interior, thereby cooling the vehicle interior.
  • the controller 50 connects the first connection port 32a and the second connection port 32b of the four-way expansion valve 32 in a throttled state, and the four-way expansion valve 32 is connected to the third connection.
  • the port 32c and the fourth connection port 32d are communicated in a throttled state, the first connection port 31a and the third connection port 31c of the second three-way expansion valve 31 are communicated in a throttled state, and the third 2
  • the connection port 31b is fully closed. Further, the cooling expansion valve 16b is throttled.
  • the refrigerant discharged from the compressor 11 flows through the indoor condenser 12, the four-way expansion valve 32, and the receiver 15 in this order, as indicated by the solid line arrows in FIG.
  • the receiver 15, the second three-way expansion valve 31, the outdoor heat exchanger 18, the four-way expansion valve 32, and the intake port of the compressor 11 are circulated in this order, and the dashed-dotted line in FIG.
  • the air circulates through the receiver 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11 in this order.
  • the refrigeration cycle device 10 in the parallel dehumidifying and heating mode is switched to a circuit in which the outdoor heat exchanger 18 and the indoor evaporator 19 are connected in parallel with respect to the flow of refrigerant flowing out from the receiver 15 .
  • the control device 50 controls the operation of various controlled devices.
  • the discharge capacity is controlled in the same manner as in the cooling mode.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the throttle opening is controlled in the same manner as in the heating mode.
  • the throttle opening is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the controller 50 calculates a refrigerant pressure value that allows the outdoor heat exchanger 18 to obtain the required amount of heat exchange.
  • the throttle opening of the second three-way expansion valve 31 may be controlled so that the outdoor unit refrigerant temperature T1 approaches the target temperature TO1.
  • the throttle opening of the second three-way expansion valve 31 may be controlled so that the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target flow rate GO1.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air that has been cooled while passing through the indoor evaporator 19 .
  • the refrigerant that has flowed out of the indoor condenser 12 is decompressed by the four-way expansion valve 32 and flows into the receiver 15 through the inlet side passage 21a.
  • the throttle opening degree of the four-way expansion valve 32 is controlled so that the supercooling degree SC1 of the refrigerant on the outlet side of the indoor condenser 12 approaches the target supercooling degree KSC1.
  • the control of the degree of supercooling SC1 by the four-way expansion valve 32 is the same as the control of the degree of supercooling SC1 by the first three-way expansion valve 30 in the heating mode of the first embodiment described with reference to FIG. 8, so description thereof will be omitted.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the second three-way expansion valve 31 via the fourth three-way joint 13d.
  • Another part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed from the receiver 15 into the second three-way expansion valve 31 is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the low-pressure refrigerant decompressed by the second three-way expansion valve 31 flows into the outdoor heat exchanger 18 .
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, absorbs heat from the outside air, and evaporates.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 is decompressed by the four-way expansion valve 32 and flows into the second three-way joint 13b.
  • the refrigerant that has flowed from the receiver 15 to the cooling expansion valve 16b via the fourth three-way joint 13d is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 flows into the second three-way joint 13b.
  • the flow of refrigerant flowing out of the outdoor heat exchanger 18 and the flow of refrigerant flowing out of the indoor evaporator 19 join.
  • the refrigerant that has flowed out of the second three-way joint 13b is sucked into the compressor 11 and compressed again.
  • dehumidifying and heating the vehicle interior can be performed by reheating the air cooled and dehumidified by the indoor evaporator 19 with the indoor condenser 12 and blowing it into the vehicle interior.
  • the control device 50 connects the first connection port 32a and the third connection port 32c of the four-way expansion valve 32 in a throttled state, and the four-way expansion valve 32 is connected to the second connection.
  • the port 32b and the fourth connection port 32d are fully closed, the first connection port 31a and the second connection port 31b of the second three-way expansion valve 31 are connected in a throttled state, and the third The connection port 31c is brought into a fully closed state.
  • the control device 50 puts the cooling expansion valve 16b into the throttle state.
  • the control device 50 controls the operation of various controlled devices.
  • the discharge capacity is controlled in the same manner as in the cooling mode.
  • the controller 50 may control the discharge capacity so that the blown air temperature TAV detected by the air conditioning air temperature sensor 51e approaches the target blown air temperature TAO.
  • the throttle opening is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the controller 50 calculates a refrigerant pressure value that allows the outdoor heat exchanger 18 to obtain the required amount of heat exchange.
  • the control device 50 calculates, as the target pressure PO1, a refrigerant pressure value that allows the amount of heat released between the indoor condenser 12 and the outdoor heat exchanger 18 to be appropriately distributed.
  • control device 50 controls the throttle opening so that the degree of subcooling SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the predetermined target degree of subcooling KSC2.
  • the degree of supercooling SC2 is calculated from the outdoor unit refrigerant temperature T1 detected by the outdoor unit temperature sensor 51h and the outdoor unit refrigerant pressure P1 detected by the outdoor unit pressure sensor 51i.
  • the control device 50 controls the throttle opening so that the degree of superheat SH2 of the refrigerant on the outlet side of the indoor evaporator 19 approaches the target degree of superheat KSH.
  • the degree of superheat SH2 is calculated from the evaporator temperature Te and the refrigerant evaporation pressure Pe detected by the evaporator pressure sensor 51g.
  • the controller 50 controls the opening so that the blown air temperature TAV detected by the conditioned air temperature sensor 51e approaches the target blown temperature TAO.
  • the opening degree of the air mix door 44 may be controlled so that the entire amount of air that has passed through the indoor evaporator 19 flows into the indoor condenser 12 .
  • the compressor 11 when the compressor 11 operates, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 .
  • the refrigerant that has flowed into the indoor condenser 12 radiates heat to the air that has passed through the indoor evaporator 19 and is condensed. This heats the air.
  • the refrigerant that has flowed out of the indoor condenser 12 is decompressed by the four-way expansion valve 32 and flows into the outdoor heat exchanger 18 .
  • the throttle opening degree of the four-way expansion valve 32 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the control of the outdoor unit refrigerant pressure P1 by the four-way expansion valve 32 is the same as the control of the outdoor unit refrigerant pressure P1 by the first three-way expansion valve 30 in the series dehumidification heating mode of the first embodiment described with reference to FIG. omitted.
  • the refrigerant that has flowed into the outdoor heat exchanger 18 exchanges heat with the outside air blown from the outside air fan, radiates heat to the outside air, and condenses.
  • the refrigerant that has flowed out of the outdoor heat exchanger 18 flows into the receiver 15 via the second three-way expansion valve 31, the third three-way joint 13c and the inlet side passage 21a.
  • the throttle opening degree of the second three-way expansion valve 31 is controlled so that the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target supercooling degree KSC2.
  • the control of the degree of supercooling SC2 by the second three-way expansion valve 31 is the same as the control of the degree of supercooling SC2 by the second three-way expansion valve 31 in the series dehumidifying heating mode of the first embodiment described with reference to FIG. omitted.
  • the refrigerant that has flowed into the receiver 15 is separated into gas and liquid at the receiver 15 .
  • Part of the liquid-phase refrigerant separated by the receiver 15 flows into the cooling expansion valve 16b via the fourth three-way joint 13d.
  • the remaining liquid-phase refrigerant separated by the receiver 15 is stored in the receiver 15 as surplus refrigerant.
  • the refrigerant that has flowed into the cooling expansion valve 16b is decompressed until it becomes a low-pressure refrigerant.
  • the throttle opening degree of the cooling expansion valve 16b is controlled so that the degree of superheat SH2 approaches the target degree of superheat KSH.
  • the low-pressure refrigerant decompressed by the cooling expansion valve 16 b flows into the indoor evaporator 19 .
  • the refrigerant that has flowed into the indoor evaporator 19 exchanges heat with the air blown from the indoor fan 42, absorbs heat from the air, and evaporates. This cools the air.
  • the refrigerant that has flowed out of the indoor evaporator 19 is sucked into the compressor 11 via the second three-way joint 13b and compressed again.
  • dehumidifying and heating the vehicle interior can be performed by reheating the air cooled and dehumidified by the indoor evaporator 19 by the indoor condenser 12 and blowing it into the vehicle interior.
  • the refrigeration cycle device 10 switches the refrigerant circuit according to each operation mode, thereby realizing comfortable air conditioning in the vehicle interior.
  • the expansion valve is controlled so that the degree of supercooling approaches the target degree of supercooling, so the refrigeration efficiency can be increased as much as possible.
  • the control device 50 causes the supercooling degree SC1 of the refrigerant condensed in the indoor condenser 12 to approach the target supercooling degree KSC1 in the heating mode and the parallel dehumidifying heating mode (in other words, the first operation mode).
  • the parallel dehumidifying heating mode in other words, the second operation mode
  • the four-way expansion valve 32 is controlled so that the pressure P1, temperature T1, or flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target values PO1, TO1, GO1. do.
  • one expansion valve (specifically can be realized by the four-way expansion valve 32). Therefore, the supercooling degree SC2, the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant can be adjusted with a simple configuration.
  • the third connection port 32c of the four-way expansion valve 32 is connected to the outdoor heat exchanger 18 via the high-pressure refrigerant passage 21c.
  • the heat dissipation capacity of the outdoor heat exchanger 18 can be adjusted by adjusting the pressure P1, temperature T1, or flow rate G1 of the refrigerant with the four-way expansion valve 32.
  • the control device 50 supercools the refrigerant condensed in the outdoor heat exchanger 18 (in other words, the first heat exchanger) in the cooling mode and the series dehumidifying and heating mode (in other words, the first operation mode).
  • degree SC2 approaches the target subcooling degree KSC2, and in the heating mode and the parallel dehumidification heating mode (in other words, the second operation mode), the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 reaches the target value.
  • the second three-way expansion valve 31 is controlled so as to approach PO1, TO1 and GO1.
  • one expansion valve ( Specifically, it can be realized by the second three-way expansion valve 31). Therefore, the supercooling degree SC2, the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant can be adjusted with a simple configuration.
  • the third connection port 31c of the second three-way expansion valve 31 is connected to the outlet side of the gas-liquid separator 15 via a refrigerant passage.
  • the heat absorption capacity of the outdoor heat exchanger 18 can be adjusted by adjusting the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant with the second three-way expansion valve 31 in the cooling mode and the serial dehumidification heating mode.
  • the four-way expansion valve 32 of the second embodiment is replaced with a fifth three-way joint 13e, a first three-way expansion valve 34 and a first variable throttle 35, and , the second three-way joint 13b is replaced with a four-way joint 36.
  • the refrigerant outlet side of the indoor condenser 12 is connected to the inlet of the fifth three-way joint 13e.
  • the inlet side of the receiver 15 is connected via the first variable throttle 35 to one outflow port of the fifth three-way joint 13e.
  • the first connection port 34a of the first three-way expansion valve 34 is connected to the other outflow port of the fifth three-way joint 13e.
  • the first inlet side of the four-way joint 36 is connected to the second connection port 34 b of the first three-way expansion valve 34 .
  • the first refrigerant inlet/outlet port 18a side of the outdoor heat exchanger 18 is connected to the third connection port 34c of the first three-way expansion valve 34 .
  • the refrigerant outlet of the indoor evaporator 19 is connected to the second inlet of the four-way joint 36 .
  • the suction port side of the compressor 11 is connected to the outflow port of the four-way joint 36 .
  • the refrigerant outlet side of the chiller 20 is connected to the third inlet of the four-way joint 36 .
  • the chiller 20 is an evaporator that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant decompressed by the chiller expansion valve 16c and the low-temperature side heat medium.
  • the low-temperature heat medium absorbed by the chiller 20 is used for cooling the battery.
  • One outlet of the sixth three-way joint 13f is connected to the refrigerant inlet of the chiller expansion valve 16c.
  • the other outlet of the fourth three-way joint 13d is connected to the inlet of the sixth three-way joint 13f.
  • the inlet side of the cooling expansion valve 16b is connected to the other outflow port of the sixth three-way joint 13f.
  • the control device 50 In the heating mode, the control device 50 fully closes the first connection port 34a of the first three-way expansion valve 34, and fully opens the second connection port 34b and the third connection port 34c of the first three-way expansion valve 34 for communication. , the first connection port 31a and the third connection port 31c of the second three-way expansion valve 31 are connected in a throttled state, and the second connection port 31b of the second three-way expansion valve 31 is fully closed. Further, the cooling expansion valve 16b is fully closed, and the first variable throttle 35 is throttled.
  • the control device 50 In the cooling mode, the control device 50 fully opens the first connection port 34a and the third connection port 34c of the first three-way expansion valve 34 and fully closes the second connection port 34b of the first three-way expansion valve 34. state, the first connection port 31a and the second connection port 31b of the second three-way expansion valve 31 are connected in a throttled state, and the third connection port 31c of the second three-way expansion valve 31 is fully closed. Further, the control device 50 brings the cooling expansion valve 16b into the throttled state and brings the first variable throttle 35 into the fully closed state.
  • the refrigerant discharged from the compressor 11 flows through the indoor condenser 12, the first three-way expansion valve 34, the outdoor heat Switched to a second circuit that circulates in the order of the exchanger 18, the second three-way expansion valve 31, the receiver 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11.
  • the control device 50 fully closes the first connection port 34a of the first three-way expansion valve 34, and throttles the second connection port 34b and the third connection port 34c of the first three-way expansion valve 34.
  • the first connection port 31a and the third connection port 31c of the second three-way expansion valve 31 are connected in a throttled state, and the second connection port 31b of the second three-way expansion valve 31 is fully closed. Further, the cooling expansion valve 16b is throttled, and the first variable throttle 35 is throttled.
  • the throttle opening of the first three-way expansion valve 34 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the throttle opening degree of the first three-way expansion valve 34 may be controlled so that the outdoor unit refrigerant temperature T1 approaches the target temperature TO1.
  • the throttle opening degree of the first three-way expansion valve 34 may be controlled so that the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target flow rate GO1.
  • the control device 50 causes the first connection port 34a and the third connection port 34c of the first three-way expansion valve 34 to communicate with each other in a throttled state, and the second connection port 34b of the first three-way expansion valve 34 to The first connection port 31a and the second connection port 31b of the second three-way expansion valve 31 are connected in a throttled state, and the third connection port 31c of the second three-way expansion valve 31 is fully closed. Further, the control device 50 brings the cooling expansion valve 16b into the throttled state and brings the first variable throttle 35 into the fully closed state.
  • the throttle opening of the first three-way expansion valve 34 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the second refrigerant inlet/outlet 18b side of the outdoor heat exchanger 18 is connected to the inlet/outlet of the seventh three-way joint 13g.
  • the first connection port 37a side of the second three-way expansion valve 37 is connected to the inlet of the seventh three-way joint 13g.
  • the other inlet side of the third three-way joint 13c is connected to the outlet of the seventh three-way joint 13g via the second check valve 17b and the second variable throttle .
  • the second connection port 37b of the second three-way expansion valve 37 is connected to one outlet side of the fourth three-way joint 13d.
  • the refrigerant inlet side of the chiller 20 is connected to the third connection port 37c of the second three-way expansion valve 37 via the chiller expansion valve 16c.
  • the control device 50 In the heating mode, the control device 50 fully closes the first connection port 34a of the first three-way expansion valve 34 and fully opens the second connection port 34b and the third connection port 34c of the first three-way expansion valve 34.
  • the first connection port 37a and the second connection port 37b of the second three-way expansion valve 37 are communicated with each other in a throttled state. Further, the cooling expansion valve 16b is fully closed, the first variable throttle 35 is throttled, and the second variable throttle 38 is fully closed.
  • the throttle opening degree of the second three-way expansion valve 37 is controlled so that the degree of superheat SH1 of the refrigerant on the outlet side of the outdoor heat exchanger 18 approaches the target degree of superheat KSH.
  • the control device 50 In the cooling mode, the control device 50 fully opens the first connection port 34a and the third connection port 34c of the first three-way expansion valve 34 and fully closes the second connection port 34b of the first three-way expansion valve 34. state, and the first connection port 37a of the second three-way expansion valve 37 is fully closed. Further, the control device 50 brings the cooling expansion valve 16b into the throttled state, the first variable throttle 35 into the fully closed state, and the second variable throttle 38 into the throttled state.
  • the refrigerant discharged from the compressor 11 flows through the indoor condenser 12, the first three-way expansion valve 34, the outdoor heat
  • the second circuit is switched to circulate in the order of the exchanger 18, the second variable throttle 38, the receiver 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11.
  • the control device 50 fully closes the first connection port 34a of the first three-way expansion valve 34, and throttles the second connection port 34b and the third connection port 34c of the first three-way expansion valve 34.
  • the first connection port 37a and the second connection port 37b of the second three-way expansion valve 37 are connected in a throttled state. Further, the cooling expansion valve 16b is throttled, the first variable throttle 35 is throttled, and the second variable throttle 38 is fully closed.
  • the throttle opening of the second three-way expansion valve 37 is controlled so that the outdoor unit refrigerant pressure P1 approaches the target pressure PO1.
  • the control device 50 causes the first connection port 34a and the third connection port 34c of the first three-way expansion valve 34 to communicate with each other in a throttled state, and the second connection port 34b of the first three-way expansion valve 34 to A fully closed state is set, and the first connection port 37a of the second three-way expansion valve 37 is set to a fully closed state. Further, the control device 50 brings the cooling expansion valve 16b into the throttled state, the first variable throttle 35 into the fully closed state, and the second variable throttle 38 into the throttled state.
  • the controller 50 controls the first three-way expansion valve so that the pressure P1, the temperature T1, or the flow rate G1 flowing through the outdoor heat exchanger 18 approaches the target values PO1, TO1, and GO1 in the series dehumidifying and heating mode.
  • the controller 50 may control the first three-way expansion valve 30 so that the blown air temperature TAV approaches the target blown air temperature TAO in the serial dehumidification heating mode.
  • the controller 50 may control the first three-way expansion valve 30 so that the temperature TAV of the fluid to be heat-exchanged in the indoor condenser 12 approaches the target outlet temperature TAO in the series dehumidifying and heating mode.
  • the adjustment of the degree of supercooling SC1 in the heating mode and the parallel dehumidifying heating mode and the adjustment of the blown air temperature TAV can be realized with one expansion valve (specifically, the first three-way expansion valve 30). Therefore, the supercooling degree SC1 of the refrigerant and the blown air temperature TAV can be adjusted with a simple configuration.
  • the controller 50 controls the four-way expansion valve so that the pressure P1, the temperature T1, or the flow rate G1 of the refrigerant flowing through the outdoor heat exchanger 18 approaches the target values PO1, TO1, and GO1 in the serial dehumidifying and heating mode.
  • the controller 50 may control the four-way expansion valve 32 so that the blow-out air temperature TAV approaches the target blow-out temperature TAO in the series dehumidifying and heating mode.
  • the controller 50 may control the four-way expansion valve 32 so that the temperature TAV of the fluid to be heat-exchanged in the indoor condenser 12 approaches the target outlet temperature TAO in the series dehumidification heating mode.
  • the adjustment of the degree of subcooling SC1 in the heating mode and the parallel dehumidifying heating mode and the adjustment of the blown air temperature TAV in the series dehumidifying heating mode are performed by one expansion valve (specifically, the four-way expansion valve 32).
  • the supercooling degree SC2 of the refrigerant and the blown air temperature TAV can be adjusted with a simple configuration.
  • the indoor condenser 12 is employed as a heating unit that heats air using the high-pressure refrigerant as a heat source, but the present invention is not limited to this.
  • the heating unit may be formed by adding a high-temperature-side heat medium circuit that circulates a high-temperature-side heat medium to the refrigeration cycle device 10 .
  • a high temperature side water pump, a heat medium refrigerant heat exchanger, a heater core, etc. may be arranged in the high temperature side heat medium circuit.
  • the heat medium-refrigerant heat exchanger is a heat radiating section that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the high-temperature side heat medium, and releases heat from the high-pressure refrigerant.
  • the high temperature side water pump is an electric pump that pressure-feeds the high temperature side heat medium circulating in the high temperature side heat medium circuit to the heat medium refrigerant heat exchanger.
  • the high-temperature side water pump has its rotational speed (that is, water pumping capacity) controlled by a control signal output from the control device 50 .
  • the heater core is a heat exchange portion that heats the air by exchanging heat between the high-temperature side heat medium heated by the heat medium-refrigerant heat exchanger and the air.
  • the controller 50 controls the temperature TW of the high-temperature side heat medium heated by the heat medium-refrigerant heat exchanger to approach the target temperature TWO in the serial dehumidifying and heating mode.
  • a three-way expansion valve 30 may be controlled.
  • the control device 50 may control the first three-way expansion valve 30 so that the temperature TW of the fluid to be heat-exchanged in the heat medium-refrigerant heat exchanger approaches the target temperature TWO in the series dehumidifying and heating mode.
  • one expansion valve (specifically, the first three-way expansion valve 30) adjusts the degree of supercooling SC1 in the heating mode and the parallel dehumidifying heating mode and the temperature TW of the high temperature side heat medium. realizable. Therefore, the supercooling degree SC1 of the refrigerant and the temperature TW of the high temperature side heat medium can be adjusted with a simple configuration.
  • the control device 50 may control the four-way expansion valve 32 so that the blown air temperature TAV approaches the target blown air temperature TAO in the series dehumidifying and heating mode.
  • the control device 50 may control the four-way expansion valve 32 so that the temperature TW of the fluid to be heat-exchanged in the heat medium refrigerant heat exchanger approaches the target outlet temperature TWO in the serial dehumidifying and heating mode.
  • the adjustment of the degree of supercooling SC1 in the heating mode and the parallel dehumidification heating mode and the adjustment of the temperature TW of the high temperature side heat medium can be realized with one expansion valve (specifically, the four-way expansion valve 32). . Therefore, the supercooling degree SC2 of the refrigerant and the temperature TW of the high temperature side heat medium can be adjusted with a simple configuration.
  • R1234yf is used as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be employed.
  • a mixed refrigerant or the like in which a plurality of these refrigerants are mixed may be adopted.
  • An internal heat exchanger may be added to the refrigeration cycle device 10.
  • the internal heat exchanger exchanges heat between the high-pressure refrigerant flowing out of the receiver 15 and the low-pressure refrigerant drawn into the compressor 11 .
  • the high-pressure refrigerant is cooled to reduce the enthalpy, and the low-pressure refrigerant is heated to increase the enthalpy.

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

Abstract

La présente invention comprend : une soupape de fluide frigorigène (30, 31, 32) ayant un premier orifice de raccordement (30a, 31a, 32a) auquel un premier échangeur de chaleur (12, 18) est relié, un deuxième orifice de raccordement (30b, 31b, 32b) auquel le côté d'entrée d'un séparateur gaz-liquide (15) est relié, un troisième orifice de raccordement (30c, 31c, 32c) auquel est relié un passage de fluide frigorigène, et un élément de soupape (302, 312, 322) qui commute l'état de communication du premier orifice de raccordement, du second orifice de raccordement et du troisième orifice de raccordement et décomprime un fluide frigorigène ; et une unité de commande (50) qui commute entre un premier mode de fonctionnement dans lequel le fluide frigorigène est condensé dans le premier échangeur de chaleur et s'écoule ensuite dans le séparateur gaz-liquide à travers la soupape de fluide frigorigène et un second mode de fonctionnement dans lequel le fluide frigorigène est condensé dans le premier échangeur de chaleur et s'écoule ensuite hors du troisième orifice de raccordement à travers la soupape de fluide frigorigène, et commande la soupape de fluide frigorigène de telle sorte que, dans le premier mode de fonctionnement, le degré de surfusion du fluide frigorigène condensé dans le premier échangeur de chaleur s'approche d'un degré de surfusion cible et, dans le second mode de fonctionnement, la pression, la température ou le débit du fluide frigorigène s'approchent d'une valeur cible.
PCT/JP2022/030741 2021-09-17 2022-08-12 Dispositif à cycle frigorifique WO2023042588A1 (fr)

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JP2021152216A JP2023044278A (ja) 2021-09-17 2021-09-17 冷凍サイクル装置
JP2021-152216 2021-09-17

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011058749A (ja) * 2009-09-11 2011-03-24 Mitsubishi Electric Corp 空気調和装置
JP2017115666A (ja) * 2015-12-24 2017-06-29 三菱日立パワーシステムズ株式会社 ガスタービン冷却系統、これを備えるガスタービン設備、ガスタービン冷却系統の制御装置及び制御方法
JP2017138028A (ja) * 2016-02-02 2017-08-10 アイシン精機株式会社 吸収式ヒートポンプ装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011058749A (ja) * 2009-09-11 2011-03-24 Mitsubishi Electric Corp 空気調和装置
JP2017115666A (ja) * 2015-12-24 2017-06-29 三菱日立パワーシステムズ株式会社 ガスタービン冷却系統、これを備えるガスタービン設備、ガスタービン冷却系統の制御装置及び制御方法
JP2017138028A (ja) * 2016-02-02 2017-08-10 アイシン精機株式会社 吸収式ヒートポンプ装置

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