WO2022157821A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2022157821A1
WO2022157821A1 PCT/JP2021/001626 JP2021001626W WO2022157821A1 WO 2022157821 A1 WO2022157821 A1 WO 2022157821A1 JP 2021001626 W JP2021001626 W JP 2021001626W WO 2022157821 A1 WO2022157821 A1 WO 2022157821A1
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WO
WIPO (PCT)
Prior art keywords
port
heat exchanger
valve
outdoor heat
switching valve
Prior art date
Application number
PCT/JP2021/001626
Other languages
English (en)
Japanese (ja)
Inventor
創一朗 越
惇 川島
雄亮 田代
雅一 近藤
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2021/001626 priority Critical patent/WO2022157821A1/fr
Priority to JP2022576247A priority patent/JP7442689B2/ja
Priority to US18/253,258 priority patent/US20230408123A1/en
Priority to EP21920938.4A priority patent/EP4283171A4/fr
Publication of WO2022157821A1 publication Critical patent/WO2022157821A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0251—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units being defrosted alternately
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0292—Control issues related to reversing valves

Definitions

  • the present disclosure relates to an air conditioner capable of simultaneous heating and defrosting operation.
  • Patent Document 1 by alternately defrosting the first heat exchange part and the second heat exchange part of the outdoor heat exchanger, it is possible to defrost the outdoor heat exchanger without stopping heating.
  • An air conditioner is disclosed.
  • a differential pressure-driven channel switching valve is used to switch the channel between the first heat exchange section and the second heat exchange section.
  • the flow path switching valve there is a problem that the differential pressure for switching the flow path and fixing the valve cannot be sufficiently secured.
  • the present disclosure is intended to solve the above-described problems, and aims to ensure a differential pressure in a flow path switching valve in an air conditioner capable of executing simultaneous heating and defrosting operation.
  • the air conditioner according to the present disclosure includes a compressor, a high-pressure pipe through which a high-pressure refrigerant discharged from the compressor flows, a low-pressure pipe through which a low-pressure refrigerant sucked into the compressor flows, and a first flow switching valve. , an indoor heat exchanger, an expansion valve, a first outdoor heat exchanger, a second outdoor heat exchanger, and a second flow switching valve, wherein the second flow switching valve is It switches the flow path of the refrigerant flowing in the first outdoor heat exchanger and the second outdoor heat exchanger, and the second flow switching valve is the first and second chambers, and the first and second chambers. and a slide valve that is moved by a differential pressure between and at least one of the first chamber and the second chamber is connected to the high pressure pipe or the low pressure pipe.
  • At least one of the first chamber and the second chamber that generates the differential pressure in the second flow path switching valve is connected to the high-pressure pipe or the low-pressure pipe, whereby the second flow path switching Sufficient differential pressure can be ensured for switching and fixing the valve.
  • FIG. 1 is a refrigerant circuit diagram showing the configuration of an air conditioner according to Embodiment 1.
  • FIG. FIG. 4 is a diagram showing the operation of the air-conditioning apparatus according to Embodiment 1 during cooling operation; 4 is a diagram showing the operation of the air-conditioning apparatus according to Embodiment 1 during heating operation;
  • FIG. 4 is a diagram showing the operation of the air-conditioning apparatus according to Embodiment 1 during the first operation during simultaneous heating and defrosting operation.
  • FIG. FIG. 7 is a diagram showing the operation of the air conditioner according to Embodiment 1 during the second operation during simultaneous heating and defrosting operation.
  • 4 is a schematic cross-sectional view showing a schematic configuration of a second flow switching valve according to Embodiment 1.
  • FIG. 2 is a ph diagram of the air conditioner according to Embodiment 1.
  • FIG. FIG. 7 is a schematic cross-sectional view showing a schematic configuration of a second flow switching valve according to Embodiment 2;
  • FIG. 11 is a schematic cross-sectional view showing a schematic configuration of a second flow path switching valve according to Embodiment 3;
  • FIG. 11 is a schematic cross-sectional view showing a schematic configuration of a second flow path switching valve according to Embodiment 4;
  • FIG. 11 is a refrigerant circuit diagram showing the configuration of an air conditioner according to Embodiment 5.
  • Embodiment 1 An air conditioner 100 according to Embodiment 1 will be described.
  • the air conditioner 100 of the present embodiment is a room air conditioner installed on the wall of the air-conditioned space or a package air conditioner installed on the ceiling of the air-conditioned space.
  • the air conditioner 100 is configured to be capable of performing cooling operation, heating operation, reverse cycle defrosting operation (hereinafter simply referred to as "defrosting operation"), and simultaneous heating and defrosting operation. .
  • FIG. 1 is a refrigerant circuit diagram showing the configuration of an air conditioner 100 according to Embodiment 1.
  • an air conditioner 100 includes a refrigerant circuit 10 and a control device 50 that controls the refrigerant circuit 10 .
  • the refrigerant circuit 10 of the present embodiment includes a compressor 1, a first flow switching valve 2, an indoor heat exchanger 3, an expansion valve 4, a first pressure reducing device 5a, a second pressure reducing device 5b, and a first outdoor heat exchanger. 6 a , a second outdoor heat exchanger 6 b , a second flow switching valve 7 , a first valve 8 and a second valve 9 .
  • the compressor 1 is a fluid machine that sucks in low-pressure gas refrigerant, compresses it, and discharges it as high-pressure gas refrigerant.
  • the compressor 1 is an inverter-driven compressor with an adjustable operating frequency. The operating frequency of the compressor 1 is controlled by the controller 50 .
  • the compressor 1 has a suction port 11a for sucking refrigerant and a discharge port 11b for discharging compressed refrigerant.
  • the suction port 11a is maintained at a suction pressure, that is, a low pressure
  • the discharge port 11b is maintained at a discharge pressure, that is, a high pressure.
  • the first channel switching valve 2 is a four-way valve that switches the channel of the refrigerant discharged from the compressor 1 .
  • the first flow path switching valve 2 has a first port A, a second port B, a third port C, and a fourth port D.
  • the first port A is a port for low pressure that is maintained at a low pressure in all of cooling operation, heating operation, defrosting operation, and simultaneous heating and defrosting operation.
  • the third port C is a port for high pressure which is maintained at a high pressure in all of cooling operation, heating operation, defrosting operation, and simultaneous heating and defrosting operation.
  • the first flow path switching valve 2 can take a first state indicated by a solid line in FIG. 1 and a second state indicated by a broken line in FIG.
  • the control device 50 sets the first flow path switching valve 2 to the first state during cooling operation and defrosting operation, and sets the first flow path switching valve 2 to the second state during heating operation and simultaneous heating and defrosting operation. set.
  • the indoor heat exchanger 3 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air blown by an indoor fan (not shown) housed in the indoor unit.
  • the indoor heat exchanger 3 functions as a condenser during heating operation, and functions as an evaporator during cooling operation.
  • the expansion valve 4 is an electronic expansion valve that reduces the pressure of the refrigerant.
  • the opening degree of the expansion valve 4 is adjusted by the controller 50 .
  • the first pressure reducing device 5a and the second pressure reducing device 5b are capillary tubes that reduce the pressure of the refrigerant flowing between the expansion valve 4 and the first outdoor heat exchanger 6a and between the second outdoor heat exchanger 6b.
  • the first pressure reducing device 5a is provided on the refrigerant outflow side of the first outdoor heat exchanger 6a during cooling operation
  • the second pressure reducing device 5b is provided on the refrigerant outflow side of the second outdoor heat exchanger 6b during cooling operation.
  • the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b exchange heat between the refrigerant flowing inside and the air blown by an outdoor fan (not shown) housed in the outdoor unit. Exchanger.
  • the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b function as evaporators during heating operation, and function as condensers during cooling operation.
  • the first outdoor heat exchanger 6 a and the second outdoor heat exchanger 6 b are connected in parallel with each other in the refrigerant circuit 10 .
  • the 1st outdoor heat exchanger 6a and the 2nd outdoor heat exchanger 6b are comprised by dividing one heat exchanger into two up and down, for example.
  • the first outdoor heat exchanger 6a is arranged below and the second outdoor heat exchanger 6b is arranged above.
  • the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b are also arranged in parallel with respect to the air flow.
  • the second flow switching valve 7 switches the flow path of the refrigerant flowing to the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b.
  • the second flow path switching valve 7 is a differential pressure driven four-way valve that operates using differential pressure.
  • the second flow switching valve 7 has a first port E, a second port F, a third port G and a fourth port H.
  • the second flow switching valve 7 can take a first state indicated by a solid line in FIG. 1 and a second state indicated by a broken line in FIG. In the first state, the first port E and the fourth port H communicate, and the second port F and the third port G communicate. In the second state, the first port E and the second port F communicate, and the third port G and the fourth port H communicate.
  • the control device 50 sets the second flow path switching valve 7 to the first state or the second state during simultaneous heating and defrosting operation.
  • the first valve 8 is an electronic expansion valve or an electromagnetic valve that adjusts the amount of refrigerant flowing from the discharge port 11b of the compressor 1 to the third port G of the second flow path switching valve 7. The degree of opening of the first valve 8 is adjusted by the controller 50 .
  • the second valve 9 is an electronic expansion valve or an electromagnetic valve that adjusts the flow rate of refrigerant flowing from the third port G of the second flow path switching valve 7 to the suction port 11 a of the compressor 1 .
  • the degree of opening of the second valve 9 is adjusted by the controller 50 .
  • the discharge port 11b of the compressor 1 and the third port C of the first flow path switching valve 2 are connected by a first high pressure pipe 12a.
  • High-pressure refrigerant discharged from the discharge port 11b of the compressor 1 flows through the first high-pressure pipe 12a in any of the cooling operation, the heating operation, the defrosting operation, and the simultaneous heating and defrosting operation.
  • a second high-pressure pipe 12b connects between the branch portion 14 provided in the middle of the first high-pressure pipe 12a and the first valve 8.
  • the high-pressure refrigerant discharged from the discharge port 11b of the compressor 1 also flows through the second high-pressure pipe 12b in any of the cooling operation, the heating operation, the defrosting operation, and the simultaneous heating and defrosting operation.
  • the first valve 8 and the third port G of the second flow switching valve 7 are connected by a first pipe 15a. That is, the third port G of the second flow switching valve 7 is connected to the discharge port 11b of the compressor 1 via the first pipe 15a, the first valve 8, the second high pressure pipe 12b, and the first high pressure pipe 12a.
  • It is A second pipe 15b connects between the branch portion 16 provided in the middle of the first pipe 15a and the second valve 9 .
  • the suction port 11a of the compressor 1 and the second valve 9 are connected by a first low-pressure pipe 13a.
  • a low-pressure refrigerant sucked into the suction port 11a of the compressor 1 flows through the first low-pressure pipe 13a in any of the cooling operation, the heating operation, the defrosting operation, and the simultaneous heating and defrosting operation.
  • a pilot pipe 713 of a second flow switching valve 7, which will be described later, is connected to the first low-pressure pipe 13a.
  • a branch portion 17 provided in the middle of the first low-pressure pipe 13a and the first port A of the first flow path switching valve 2 are connected by a second low-pressure pipe 13b.
  • a fourth port D of the first flow path switching valve 2 is connected to one inlet/outlet of the indoor heat exchanger 3 via a refrigerant pipe.
  • the other inlet/outlet of the indoor heat exchanger 3 is connected to one inlet/outlet of the expansion valve 4 via a refrigerant pipe.
  • the other inlet/outlet of the expansion valve 4 is connected to the first pressure reducing device 5a and the second pressure reducing device 5b via refrigerant pipes.
  • the first decompression device 5a and the second decompression device 5b are connected to the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b, respectively. That is, the other inlet/outlet of the expansion valve 4 is connected to one outlet/inlet of the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b via the refrigerant pipe, the first pressure reducing device 5a and the second pressure reducing device 5b. connected to one of the inlets and outlets of the One inlet/outlet of the first outdoor heat exchanger 6a is connected to one inlet/outlet of the second outdoor heat exchanger 6b via a refrigerant pipe.
  • the other outlet/inlet of the first outdoor heat exchanger 6a is connected to the fourth port H of the second flow path switching valve 7 via a refrigerant pipe.
  • the other outlet/inlet of the second outdoor heat exchanger 6b is connected to the second port F of the second flow path switching valve 7 via a refrigerant pipe.
  • a first port E of the second flow path switching valve 7 is connected to a second port B of the first flow path switching valve 2 via a refrigerant pipe.
  • the control device 50 has a microcomputer equipped with a CPU, ROM, RAM, and I/O ports.
  • the control device 50 controls each part of the air conditioner 100 based on detection signals from various sensors (not shown) provided in the air conditioner 100 and setting information input from a remote controller, and performs cooling operation and heating operation. , defrost operation and simultaneous heating and defrosting operation.
  • the control device 50 controls the operating frequency of the compressor 1 , switching of the states of the first flow switching valve 2 and the second flow switching valve 7 , expansion valve 4 , first valve 8 and second valve 9 . opening and fan speed.
  • Various sensors included in the air conditioner 100 include an indoor temperature sensor that detects the temperature of the air-conditioned space, an outdoor temperature sensor that detects the outdoor temperature, a sensor that detects the temperature or pressure of the refrigerant flowing through each heat exchanger, and an air-conditioned target. It is a sensor or the like that detects the presence or absence of a person in the space.
  • FIG. 2 is a diagram showing the operation of the air-conditioning apparatus 100 according to Embodiment 1 during cooling operation. As shown in FIG. 2, both the first flow path switching valve 2 and the second flow path switching valve 7 are set to the first state during cooling operation. Also, the first valve 8 is opened to a preset degree of opening, and the second valve 9 is closed.
  • the high-pressure gas refrigerant discharged from the compressor 1 is split at the branch portion 14 of the first high-pressure pipe 12a into the third port C of the first flow path switching valve 2 and the second high-pressure pipe 12b.
  • the gas refrigerant that has flowed into the third port C of the first flow path switching valve 2 flows through the second port B of the first flow path switching valve 2 and the first port E and the fourth port H of the second flow path switching valve 7. and flows into the first outdoor heat exchanger 6a.
  • the gas refrigerant that has flowed into the second high-pressure pipe 12b passes through the first valve 8, the first pipe 15a, the third port G and the second port F of the second flow switching valve 7, and passes through the second outdoor heat exchanger 6b.
  • both the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b function as condensers.
  • the gas refrigerant that has flowed into each of the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b is condensed into liquid refrigerant.
  • the liquid refrigerant that has flowed out of the first outdoor heat exchanger 6 a is decompressed by the first decompression device 5 a and flows into the expansion valve 4 .
  • the liquid refrigerant that has flowed out of the second outdoor heat exchanger 6b is decompressed by the second pressure reducing device 5b, joins the liquid refrigerant that has flowed out of the first outdoor heat exchanger 6a, and flows into the expansion valve 4.
  • the liquid refrigerant that has flowed into the expansion valve 4 is decompressed and becomes a low-pressure two-phase refrigerant.
  • the two-phase refrigerant that has flowed out of the expansion valve 4 flows into the indoor heat exchanger 3 .
  • the indoor heat exchanger 3 functions as an evaporator. That is, in the indoor heat exchanger 3, the heat of evaporation of the refrigerant flowing inside is absorbed from the indoor air. As a result, the two-phase refrigerant that has flowed into the indoor heat exchanger 3 evaporates and becomes a low-pressure gas refrigerant. In addition, the indoor air blown by the indoor fan is cooled by releasing heat to the refrigerant. The gas refrigerant that has flowed out of the indoor heat exchanger 3 passes through the fourth port D, the first port A, the second low-pressure pipe 13b, and the first low-pressure pipe 13a of the first flow switching valve 2 to the compressor 1. inhaled. The gas refrigerant sucked into the compressor 1 is compressed into a high-pressure gas refrigerant. During cooling operation, the above cycle is continuously repeated.
  • FIG. 3 is a diagram showing the operation of the air-conditioning apparatus 100 according to Embodiment 1 during heating operation.
  • the first flow path switching valve 2 is set to the second state
  • the second flow path switching valve 7 is set to the first state.
  • the second valve 9 is opened to a preset degree of opening, and the first valve 8 is closed.
  • the high-pressure gas refrigerant discharged from the compressor 1 flows into the indoor heat exchanger 3 via the first high-pressure pipe 12 a and the third port C and fourth port D of the first flow path switching valve 2 .
  • the indoor heat exchanger 3 functions as a condenser. That is, in the indoor heat exchanger 3, heat is exchanged between the refrigerant flowing inside and the indoor air blown by the indoor fan, and the condensation heat of the refrigerant is radiated to the indoor air. As a result, the gas refrigerant that has flowed into the indoor heat exchanger 3 is condensed into a high-pressure liquid refrigerant. Also, the indoor air blown by the indoor fan is heated by heat radiation from the refrigerant.
  • the liquid refrigerant that has flowed out of the indoor heat exchanger 3 flows into the expansion valve 4 .
  • the liquid refrigerant that has flowed into the expansion valve 4 is decompressed and becomes a low-pressure two-phase refrigerant.
  • the two-phase refrigerant flowing out of the expansion valve 4 is split between the first pressure reducing device 5a and the second pressure reducing device 5b.
  • the two-phase refrigerant that has flowed into the first pressure reducing device 5a is further depressurized and flows into the first outdoor heat exchanger 6a.
  • the two-phase refrigerant that has flowed into the second pressure reducing device 5b is further depressurized and flows into the second outdoor heat exchanger 6b.
  • both the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b function as evaporators. That is, in each of the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b, heat exchange is performed between the refrigerant flowing inside and the outdoor air blown by the outdoor fan, and the heat of evaporation of the refrigerant is transferred to the outdoor air. heat is absorbed from the air. As a result, the two-phase refrigerant that has flowed into each of the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b evaporates into low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the first outdoor heat exchanger 6a passes through the fourth port H and first port E of the second flow path switching valve 7, the second port B and first port A of the first flow path switching valve 2, It is sucked into the compressor 1 via the second low-pressure pipe 13b and the first low-pressure pipe 13a.
  • the gas refrigerant flowing out of the second outdoor heat exchanger 6b passes through the second port F, the third port G of the second flow path switching valve 7, the first pipe 15a, the second pipe 15b, the second valve 9, In the first low-pressure pipe 13a, it joins with the gas refrigerant that has flowed out from the first outdoor heat exchanger 6a and is sucked into the compressor 1.
  • the gas refrigerant sucked into the compressor 1 is compressed into a high-pressure gas refrigerant. During heating operation, the above cycle is continuously repeated.
  • the simultaneous heating/defrosting operation includes a first operation and a second operation.
  • the first outdoor heat exchanger 6a and the indoor heat exchanger 3 function as condensers
  • the second outdoor heat exchanger 6b functions as an evaporator.
  • the first outdoor heat exchanger 6a is defrosted and heating is continued.
  • the second outdoor heat exchanger 6b and the indoor heat exchanger 3 function as condensers
  • the first outdoor heat exchanger 6a functions as an evaporator.
  • the second outdoor heat exchanger 6b is defrosted and heating is continued.
  • the control device 50 performs the simultaneous heating and defrosting operation when the conditions for starting the simultaneous heating and defrosting operation are satisfied while the heating operation is being performed.
  • the condition for starting the heating and defrosting simultaneous operation is, for example, that the elapsed time from the start of the heating operation exceeds the threshold time, or that the temperature of the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b is the threshold It is below the temperature, and so on.
  • the control device 50 first performs the first operation when the conditions for starting the simultaneous heating and defrosting operation are satisfied, and when the preset time has elapsed or the temperature of the first outdoor heat exchanger 6a is higher than the threshold temperature When it becomes large, the second operation is performed.
  • FIG. 4 is a diagram showing the operation of the air conditioner 100 according to Embodiment 1 during the first operation during simultaneous heating and defrosting operation. As shown in FIG. 4, both the first flow path switching valve 2 and the second flow path switching valve 7 are set to the second state during the first operation. Also, the first valve 8 is opened to a preset degree of opening, and the second valve 9 is closed.
  • the high-pressure gas refrigerant discharged from the compressor 1 is split at the branch portion 14 of the first high-pressure pipe 12a into the third port C of the first flow path switching valve 2 and the second high-pressure pipe 12b.
  • the gas refrigerant that has flowed into the second high-pressure pipe 12b passes through the first valve 8, the first pipe 15a, the third port G and the fourth port H of the second flow switching valve 7, and the first outdoor heat exchanger 6a. flow into In the first outdoor heat exchanger 6a, the adhered frost melts due to heat radiation from the refrigerant flowing inside. As a result, defrosting of the first outdoor heat exchanger 6a is performed.
  • the gas refrigerant that has flowed into the first outdoor heat exchanger 6a is condensed into intermediate-pressure liquid refrigerant or two-phase refrigerant, flows out of the first outdoor heat exchanger 6a, and is decompressed by the first decompression device 5a.
  • the gas refrigerant that has flowed into the third port C of the first flow path switching valve 2 passes through the fourth port D of the first flow path switching valve 2, and flows into the room. It flows into heat exchanger 3 .
  • heat exchanger 3 heat is exchanged between the refrigerant flowing inside and the indoor air blown by the indoor fan, and the condensation heat of the refrigerant is radiated to the indoor air.
  • the gas refrigerant that has flowed into the indoor heat exchanger 3 is condensed into a high-pressure liquid refrigerant.
  • the indoor air blown by the indoor fan is heated by heat radiation from the refrigerant.
  • the liquid refrigerant that has flowed out of the indoor heat exchanger 3 flows into the expansion valve 4 .
  • the liquid refrigerant that has flowed into the expansion valve 4 is decompressed and becomes a low-pressure two-phase refrigerant.
  • the two-phase refrigerant flowing out of the expansion valve 4 joins the liquid refrigerant or two-phase refrigerant decompressed by the first decompression device 5a, is further decompressed by the second decompression device 5b, and flows into the second outdoor heat exchanger 6b.
  • the second outdoor heat exchanger 6b heat is exchanged between the refrigerant flowing inside and the outdoor air blown by the outdoor fan, and the evaporation heat of the refrigerant is absorbed from the outdoor air.
  • the two-phase refrigerant that has flowed into the second outdoor heat exchanger 6b evaporates and becomes low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the second outdoor heat exchanger 6b passes through the second port F and the first port E of the second flow path switching valve 7, the second port B and the first port A of the first flow path switching valve 2,
  • the air is sucked into the compressor 1 via the second low-pressure pipe 13b and the first low-pressure pipe 13a.
  • the gas refrigerant sucked into the compressor 1 is compressed into a high-pressure gas refrigerant.
  • the above cycle is continuously repeated to defrost the first outdoor heat exchanger 6a and to continue heating.
  • FIG. 5 is a diagram showing the operation of the air conditioner 100 according to Embodiment 1 during the second operation during simultaneous heating and defrosting operation.
  • the first flow switching valve 2 is set to the second state
  • the second flow switching valve 7 is set to the first state.
  • the first valve 8 is opened to a preset degree of opening, and the second valve 9 is closed.
  • the high-pressure gas refrigerant discharged from the compressor 1 is split at the branch portion 14 of the first high-pressure pipe 12a into the third port C of the first flow path switching valve 2 and the second high-pressure pipe 12b.
  • the gas refrigerant that has flowed into the second high-pressure pipe 12b passes through the first valve 8, the first pipe 15a, the third port G and the second port F of the second flow switching valve 7, and passes through the second outdoor heat exchanger 6b.
  • flow into In the second outdoor heat exchanger 6b the adhered frost is melted by heat radiation from the refrigerant flowing inside. As a result, defrosting of the second outdoor heat exchanger 6b is performed.
  • the gas refrigerant that has flowed into the second outdoor heat exchanger 6b is condensed into intermediate-pressure liquid refrigerant or two-phase refrigerant, flows out of the second outdoor heat exchanger 6b, and is decompressed by the second decompression device 5b.
  • the gas refrigerant that has flowed into the third port C of the first flow path switching valve 2 passes through the fourth port D of the first flow path switching valve 2, and flows into the room. It flows into heat exchanger 3 .
  • heat exchanger 3 heat is exchanged between the refrigerant flowing inside and the indoor air blown by the indoor fan, and the condensation heat of the refrigerant is radiated to the indoor air.
  • the gas refrigerant that has flowed into the indoor heat exchanger 3 is condensed into a high-pressure liquid refrigerant.
  • the indoor air blown by the indoor fan is heated by heat radiation from the refrigerant.
  • the liquid refrigerant that has flowed out of the indoor heat exchanger 3 flows into the expansion valve 4 .
  • the liquid refrigerant that has flowed into the expansion valve 4 is decompressed and becomes a low-pressure two-phase refrigerant.
  • the two-phase refrigerant flowing out of the expansion valve 4 joins the liquid refrigerant or two-phase refrigerant decompressed by the second decompression device 5b, is further decompressed by the first decompression device 5a, and flows into the first outdoor heat exchanger 6a.
  • heat is exchanged between the refrigerant flowing inside and the outdoor air blown by the outdoor fan, and the evaporation heat of the refrigerant is absorbed from the outdoor air.
  • the two-phase refrigerant that has flowed into the first outdoor heat exchanger 6a evaporates into low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the first outdoor heat exchanger 6a passes through the fourth port H and first port E of the second flow path switching valve 7, the second port B and first port A of the first flow path switching valve 2,
  • the air is sucked into the compressor 1 via the second low-pressure pipe 13b and the first low-pressure pipe 13a.
  • the gas refrigerant sucked into the compressor 1 is compressed into a high-pressure gas refrigerant.
  • the above cycle is continuously repeated to defrost the second outdoor heat exchanger 6b and to continue heating.
  • the control device 50 performs the defrosting operation when the conditions for starting the defrosting operation are satisfied while the heating operation is being performed.
  • Conditions for starting the defrosting operation include, for example, conditions for starting the simultaneous heating and defrosting operation, that the heating load is small, or that there are no people in the air-conditioned space.
  • the operation of the air conditioner 100 during the defrosting operation is the same as that during the cooling operation shown in FIG. During the defrosting operation, both the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b function as condensers.
  • FIG. 6 is a schematic cross-sectional view showing a schematic configuration of the second flow path switching valve 7 according to Embodiment 1. As shown in FIG. As shown in FIG. 6 , the second flow switching valve 7 has a main valve 70 and a pilot valve 71 .
  • the main valve 70 has a cylinder 701, a slide base 702 formed on a part of the inner wall of the cylinder 701, and a slide valve 703 that slides on the slide base 702 along the central axis direction of the cylinder 701. ing.
  • a first port E is provided in the central portion of the slide base 702 in the central axis direction of the cylinder 701 .
  • a second port F and a fourth port H are provided on both sides of the first port E in the central axis direction of the cylinder 701 .
  • a third port G is provided at a position facing the first port E across the central axis of the cylinder 701 .
  • the slide valve 703 has a dome shape that opens toward the slide base 702 .
  • a piston 704 connected to the slide valve 703 is provided on one end side of the slide valve 703 in the central axis direction of the cylinder 701 .
  • a first chamber 706 is formed between one end of the cylinder 701 and the piston 704 .
  • a piston 705 connected to the slide valve 703 is provided on the other end side of the slide valve 703 in the central axis direction of the cylinder 701 .
  • a second chamber 707 is formed between the other end of the cylinder 701 and the piston 705 .
  • Pistons 704 and 705 are slidably provided along the inner wall surface of cylinder 701 . The pistons 704 and 705 move along the central axis of the cylinder 701 together with the slide valve 703 .
  • the pilot valve 71 has four pilot pipes 710, 711, 712, and 713. Pilot pipe 710 is connected to third port G of main valve 70 . Pilot pipe 711 is connected to first chamber 706 of main valve 70 . Pilot pipe 712 is connected to second chamber 707 of main valve 70 . The pilot pipe 713 is connected to the first low pressure pipe 13a.
  • the pilot valve 71 is switched between the first state and the second state by the control device 50 .
  • pilot pipe 710 and pilot pipe 711 communicate inside pilot valve 71
  • pilot pipe 713 and pilot pipe 712 communicate inside pilot valve 71 . Therefore, in the first state, the pressure in the first chamber 706 becomes substantially the same as the pressure in the third port G by communicating the third port G and the first chamber 706 .
  • the communication between the first low-pressure pipe 13a and the second chamber 707 makes the pressure in the second chamber 707 substantially the same as that in the first low-pressure pipe 13a.
  • Slide valve 703 is moved by the differential pressure between first chamber 706 and second chamber 707 .
  • the slide valve 703 moves toward the second chamber 707 having a lower pressure than the first chamber 706 .
  • the first port E and the fourth port H communicate with each other
  • the third port G communicates with the second port F
  • the second flow switching valve 7 is switched to the first state.
  • the pilot pipes 710 and 712 communicate inside the pilot valve 71
  • the pilot pipes 711 and 713 communicate inside the pilot valve 71 . Therefore, in the first state, the pressure in the second chamber 707 becomes substantially the same as the pressure in the third port G by communicating the third port G and the second chamber 707 . Further, the communication between the first low-pressure pipe 13a and the first chamber 706 makes the pressure of the first chamber 706 substantially the same as that of the first low-pressure pipe 13a.
  • the slide valve 703 moves toward the first chamber 706 having a lower pressure than the second chamber 707 . As a result, the first port E and the second port F communicate, the third port G communicates with the fourth port H, and the second flow switching valve 7 is switched to the second state.
  • FIG. 7 is a ph diagram of the air conditioner 100 according to Embodiment 1.
  • FIG. in the conventional differential pressure driven four-way valve the pilot pipe 713 of the pilot valve 71 is connected to the first port E of the main valve 70 .
  • high-pressure refrigerant flows into both the third port G and the first port E. Therefore, as shown in FIG. P0 becomes pressure loss in the second flow path switching valve 7 and becomes smaller.
  • a sufficient differential pressure for moving and fixing the slide valve 703 cannot be secured, and problems such as the slide valve 703 not being able to switch or the position of the slide valve 703 moving during operation may occur. .
  • the first chamber 706 or the second chamber 707 of the second flow switching valve 7 can be connected via the pilot valve 71 to the first low-pressure pipe 13a through which the low-pressure refrigerant flows. , the minimum operating differential pressure in the second flow path switching valve 7 can be ensured. As a result, the second flow path switching valve 7 can be operated normally.
  • Embodiment 2 An air conditioner 100 according to Embodiment 2 will be described. An air conditioner 100 according to Embodiment 2 differs from Embodiment 1 in the configuration of the second flow path switching valve 7 . Other configurations and controls of the air conditioner 100 are the same as in the first embodiment.
  • FIG. 8 is a schematic cross-sectional view showing a schematic configuration of a second flow path switching valve 7A according to Embodiment 2.
  • the pilot pipe 713 of the second flow path switching valve 7A of this embodiment is connected to the first port E.
  • the second chamber 707 of the main valve 70 of the second flow path switching valve 7A in this embodiment is connected to the first low-pressure pipe 13a via a pipe 721 and a third valve 722 . That is, the second chamber 707 of the second flow path switching valve 7A of this embodiment is directly connected to the first low-pressure pipe 13a without the pilot valve 71 interposed therebetween.
  • the third valve 722 is an electromagnetic valve or an electronic expansion valve that adjusts the amount of refrigerant flowing from the first low-pressure pipe 13a to the second chamber 707, and its opening degree is controlled by the controller 50.
  • the control device 50 opens the third valve 722
  • the first low-pressure pipe 13a and the second chamber 707 are communicated with each other, so that the pressure in the second chamber 707 becomes substantially the same as that in the first low-pressure pipe 13a.
  • the slide valve 703 is moved by the differential pressure between the first chamber 706 and the second chamber 707, and the second flow switching valve 7A is switched.
  • the second chamber 707 is directly connected to the first low-pressure pipe 13a without going through the pilot valve 71.
  • the minimum operating differential pressure in the second flow path switching valve 7A can be ensured, and the slide valve 703 can be reliably moved and fixed. As a result, the second flow switching valve 7A can be operated normally.
  • FIG. 8 shows an example in which the second chamber 707 is connected to the first low-pressure pipe 13a without the pilot valve 71 interposed therebetween, the present invention is not limited to this.
  • the first chamber 706 is connected to the first low pressure pipe 13a without the pilot valve 71, or both the first chamber 706 and the second chamber 707 are connected to the first low pressure pipe 13a without the pilot valve 71. may be connected.
  • Embodiment 3 An air conditioner 100 according to Embodiment 3 will be described. An air conditioner 100 according to Embodiment 3 differs from Embodiment 1 in the configuration of the second flow path switching valve 7 . Other configurations and controls of the air conditioner 100 are the same as in the first embodiment.
  • FIG. 9 is a schematic cross-sectional view showing a schematic configuration of a second flow path switching valve 7B according to Embodiment 3.
  • FIG. 9 the pilot pipe 713 of the second flow path switching valve 7B of this embodiment is connected to the first port E.
  • the pilot pipe 710 of the second flow path switching valve 7B of the present embodiment is connected to the second high pressure pipe 12b of the refrigerant circuit 10 .
  • Low-pressure refrigerant flows into both the third port G and the first port E during heating operation of the air conditioner 100 .
  • the pilot pipe 710 of the pilot valve 71 is connected to the third port G of the main valve 70 .
  • the differential pressure between the third port G and the first port E is only the difference in pressure loss in the second flow path switching valve 7, and a sufficient differential pressure for moving and fixing the slide valve 703 cannot be secured.
  • the first chamber 706 or the second chamber 707 of the second flow switching valve 7B is connected to the first low-pressure pipe 13a via the pilot valve 71.
  • a large differential pressure can be obtained between the first port E and the second high-pressure pipe 12b.
  • the differential pressure between the first chamber 706 and the second chamber 707 can be ensured, and the slide valve 703 can be reliably moved and fixed.
  • the second flow path switching valve 7B can be operated normally.
  • Embodiment 4 An air conditioner 100 according to Embodiment 4 will be described.
  • An air conditioner 100 according to Embodiment 4 differs from Embodiment 1 in the configuration of the second flow path switching valve 7 .
  • Other configurations and controls of the air conditioner 100 are the same as in the first embodiment.
  • FIG. 10 is a cross-sectional schematic diagram showing a schematic configuration of a second flow path switching valve 7C according to Embodiment 4.
  • the pilot pipe 710 of the second flow path switching valve 7C of this embodiment is connected to the third port G, and the pilot pipe 713 is connected to the first port E.
  • the first chamber 706 of the main valve 70 of the second flow path switching valve 7C of this embodiment is connected to the second high-pressure pipe 12b via a pipe 731 and a fourth valve 732.
  • the first chamber 706 of the second flow path switching valve 7C of this embodiment is connected to the second high-pressure pipe 12b without the pilot valve 41 interposed therebetween.
  • the fourth valve 732 is an electromagnetic valve or an electronic expansion valve that adjusts the amount of refrigerant flowing from the second high-pressure pipe 12b to the first chamber 706, and its opening is controlled by the controller 50.
  • the fourth valve 732 is opened by the controller 50, the second high-pressure pipe 12b and the first chamber 706 communicate with each other, so that the pressure in the first chamber 706 becomes substantially the same as that in the second high-pressure pipe 12b.
  • the slide valve 703 is moved by the differential pressure between the first chamber 706 and the second chamber 707, and the second flow switching valve 7C is switched.
  • the first chamber 706 is directly connected to the second high pressure pipe 12b without going through the pilot valve 71.
  • the minimum operating differential pressure in the second flow path switching valve 7C can be ensured, and the slide valve 703 can be reliably moved and fixed. As a result, the second flow switching valve 7C can be operated normally.
  • FIG. 9 shows an example in which the first chamber 706 of the second flow path switching valve 7C is connected to the second high-pressure pipe 12b without the pilot valve 71 interposed therebetween, the present invention is not limited to this.
  • the second chamber 707 is connected to the second high-pressure pipe 12b without passing through the pilot valve 71, or both the first chamber 706 and the second chamber 707 are connected to the second high-pressure pipe 12b without passing through the pilot valve 71. may be connected.
  • Embodiment 5 An air conditioner 100A according to Embodiment 5 will be described.
  • An air conditioner 100A according to Embodiment 5 differs from Embodiment 1 in the configuration of the second flow path switching valve 7 .
  • Other configurations and controls of the air conditioner 100A are the same as in the first embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing the configuration of an air conditioner 100A according to Embodiment 5.
  • the air conditioner 100A of the present embodiment does not include the second valve 9.
  • the suction port 11a of the compressor 1 and the first port A of the first flow path switching valve 2 are connected by a first low-pressure pipe 13a.
  • the air conditioner 100A also includes a second flow switching valve 7D that switches the flow path of the refrigerant flowing to the first outdoor heat exchanger 6a and the second outdoor heat exchanger 6b.
  • the second flow path switching valve 7D is a differential pressure driven four-way valve that operates using differential pressure, as in the first to fourth embodiments.
  • the second flow switching valve 7D has a first port E, a second port F, a third port G and a fourth port H.
  • the second flow switching valve 7D of the present embodiment can take a first state, a second state, and a third state. In the first state, the first port E, the second port F, and the fourth port H communicate with each other, and the third port G is closed. In the second state, the first port E and the second port F communicate, and the third port G and the fourth port H communicate. In the third state, the second port F and the third port G communicate with each other, and the first port E and the fourth port H communicate with each other.
  • the control device 50 sets the second flow path switching valve 7D to the first state during cooling operation, defrosting operation, and heating operation, and sets the second flow path switching valve 7D during the first operation of simultaneous heating and defrosting operation. is set to the second state, and the second flow switching valve 7D is set to the third state during the second operation of simultaneous heating and defrosting operation.
  • the second flow path switching valve 7D at least one of the first chamber 706 and the second chamber 707 that generate differential pressure is connected to the first low-pressure pipe 13a or the second high-pressure pipe 12b.
  • the pilot pipe 713 of the second flow switching valve 7D is connected to the first low pressure pipe 13a, or the second chamber 707 of the second flow switching valve 7D is connected to the first low pressure pipe 13a.
  • the pilot pipe 710 of the second flow path switching valve 7D is connected to the second high pressure pipe 12b, or the first chamber 706 of the second flow path switching valve 7D is connected to the second high pressure pipe 12b.
  • the second flow switching valve 7D takes three states as in this embodiment, at least one of the first chamber 706 and the second chamber 707 is connected to the first low pressure pipe 13a or the second high pressure pipe. 12b, it is possible to secure the minimum operating differential pressure in the second flow path switching valve 7D. As a result, the second flow switching valve 7D can be operated normally.
  • the pilot pipe 713 of Embodiment 1 and the second chamber 707 of Embodiment 2 may be connected to a low-pressure portion in any operation in the refrigerant circuit 10, instead of the first low-pressure pipe 13a. may be connected to the second low-pressure line 13b or other low-pressure line.
  • the pilot pipe 710 of Embodiment 3 and the first chamber 706 of Embodiment 4 need only be connected to the low-pressure portion in any operation in the refrigerant circuit 10, and the second high-pressure pipe 12b can be replaced. may be connected to the first high pressure line 12a or other high pressure line.
  • the second flow path switching valve 7 may have a configuration in which the pilot pipe 713 is connected to the first low pressure pipe 13a and the pilot pipe 710 is connected to the second high pressure pipe 12b.
  • the second flow path switching valve 7 may be configured such that the second chamber 707 is connected to the first low-pressure pipe 13a and the first chamber 706 is connected to the second high-pressure pipe 12b.
  • the second flow switching valve 7 may be configured such that the pilot pipe 713 is connected to the first low-pressure pipe 13a and the first chamber 706 is connected to the second high-pressure pipe 12b.
  • the second flow path switching valve 7 may be configured such that the second chamber 707 is connected to the first low-pressure pipe 13a and the pilot pipe 710 is connected to the second high-pressure pipe 12b. That is, the second flow switching valve 7 may be connected to at least one of the low-pressure pipe and the high-pressure pipe of the refrigerant circuit 10 at a portion other than the port.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif de climatisation comprenant un circuit de fluide frigorigène ayant un compresseur, un tuyau haute pression à travers lequel circule du fluide frigorigène haute pression évacué par le compresseur, un tuyau basse pression à travers lequel circule le fluide frigorigène basse pression aspiré dans le compresseur, une première vanne de commutation de trajet d'écoulement, un échangeur de chaleur intérieur, un détendeur, un premier échangeur de chaleur extérieur, un second échangeur de chaleur extérieur et un seconde vanne de commutation de trajet d'écoulement. La seconde vanne de commutation de trajet d'écoulement commute le trajet d'écoulement pour le fluide frigorigène circulant vers le premier échangeur de chaleur extérieur et le second échangeur de chaleur extérieur, la seconde vanne de commutation de trajet d'écoulement comprend une première chambre, une seconde chambre, et une vanne coulissante qui se déplace en raison d'une différence de pression entre la première chambre et la seconde chambre, et au moins une parmi la première chambre et de la seconde chambre est reliée au tuyau haute pression ou au tuyau basse pression.
PCT/JP2021/001626 2021-01-19 2021-01-19 Dispositif de climatisation WO2022157821A1 (fr)

Priority Applications (4)

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PCT/JP2021/001626 WO2022157821A1 (fr) 2021-01-19 2021-01-19 Dispositif de climatisation
JP2022576247A JP7442689B2 (ja) 2021-01-19 2021-01-19 空気調和装置
US18/253,258 US20230408123A1 (en) 2021-01-19 2021-01-19 Air-conditioning apparatus
EP21920938.4A EP4283171A4 (fr) 2021-01-19 2021-01-19 Dispositif de climatisation

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115950121A (zh) * 2022-12-02 2023-04-11 珠海格力电器股份有限公司 一种毛细管结构及空调器

Citations (3)

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Publication number Priority date Publication date Assignee Title
JPH0531489Y2 (fr) * 1987-12-07 1993-08-12
WO2019003291A1 (fr) 2017-06-27 2019-01-03 三菱電機株式会社 Climatiseur
WO2020261387A1 (fr) * 2019-06-25 2020-12-30 三菱電機株式会社 Climatiseur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6478585B2 (ja) * 2014-11-26 2019-03-06 株式会社不二工機 流路切換弁
EP3385646B1 (fr) * 2015-12-02 2022-08-10 Mitsubishi Electric Corporation Dispositif de climatisation

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0531489Y2 (fr) * 1987-12-07 1993-08-12
WO2019003291A1 (fr) 2017-06-27 2019-01-03 三菱電機株式会社 Climatiseur
WO2020261387A1 (fr) * 2019-06-25 2020-12-30 三菱電機株式会社 Climatiseur

Non-Patent Citations (1)

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Title
See also references of EP4283171A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115950121A (zh) * 2022-12-02 2023-04-11 珠海格力电器股份有限公司 一种毛细管结构及空调器

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US20230408123A1 (en) 2023-12-21
JPWO2022157821A1 (fr) 2022-07-28
EP4283171A1 (fr) 2023-11-29
EP4283171A4 (fr) 2024-03-06
JP7442689B2 (ja) 2024-03-04

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