WO2013001976A1 - Climatiseur - Google Patents

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Publication number
WO2013001976A1
WO2013001976A1 PCT/JP2012/064098 JP2012064098W WO2013001976A1 WO 2013001976 A1 WO2013001976 A1 WO 2013001976A1 JP 2012064098 W JP2012064098 W JP 2012064098W WO 2013001976 A1 WO2013001976 A1 WO 2013001976A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
refrigerant
heat exchanger
exchange path
path
Prior art date
Application number
PCT/JP2012/064098
Other languages
English (en)
Japanese (ja)
Inventor
道明　伸夫
利行 栗原
康介 森本
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to US14/126,684 priority Critical patent/US20140116078A1/en
Priority to KR1020147001871A priority patent/KR20140026630A/ko
Priority to CN201280032321.9A priority patent/CN103635754A/zh
Priority to EP12803614.2A priority patent/EP2741021A4/fr
Publication of WO2013001976A1 publication Critical patent/WO2013001976A1/fr

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    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F24F1/30—Refrigerant piping for use inside the separate outdoor units
    • 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
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • 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
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve

Definitions

  • the present invention relates to an air conditioner, and more particularly to an air conditioner capable of performing a heating operation.
  • a compressor, an indoor heat exchanger, and an outdoor heat exchanger are connected in order, and heating is performed by circulating a refrigerant in the order of the compressor, the indoor heat exchanger, the outdoor heat exchanger, and the compressor.
  • the refrigerant is switched in the order of the compressor, the outdoor heat exchanger, the indoor heat exchanger, and the compressor by a four-way switching valve or the like.
  • the reverse cycle defrost operation is performed to defrost the outdoor heat exchanger. For this reason, in this air conditioner, the heating operation stops during the reverse cycle defrost operation, and the comfort in the room is impaired.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2000-274780 discloses a defrost method for defrosting the outdoor heat exchanger while continuing the heating operation. And an air conditioner as shown in Patent Document 2 (Japanese Patent Laid-Open No. 2001-059994) has been proposed.
  • an electromagnetic valve is provided at each of the liquid side ends of the plurality of heat exchange paths of the outdoor heat exchanger.
  • the flow of the refrigerant in the heat exchange path is stopped by closing the electromagnetic valve of the heat exchange path arbitrarily selected. I try to drive.
  • the heating operation can be continued by defrosting an arbitrary heat exchange path with the heat of the outdoor air and evaporating the refrigerant in another heat exchange path.
  • a bypass path for sending a part of the refrigerant discharged from the compressor to the liquid side ends of the plurality of heat exchange paths of the outdoor heat exchanger without sending it to the indoor heat exchanger is provided. I am trying to provide it.
  • the outdoor heat exchanger is not sent to the indoor heat exchanger through the bypass passage, without sending a part of the refrigerant discharged from the compressor.
  • the operation is sent to any heat exchange path. With this operation, in this air conditioner, heating is performed by evaporating the refrigerant in another heat exchange path while defrosting the arbitrary heat exchange path by the heat of the refrigerant sent to the arbitrary heat exchange path through the bypass. The operation can be continued.
  • An object of the present invention is to enable an outdoor heat exchanger to be defrosted in an air-conditioning apparatus capable of performing a heating operation with almost no decrease in heating capacity.
  • An air conditioner includes a compressor that compresses a refrigerant, an indoor heat exchanger that dissipates heat of the refrigerant compressed in the compressor, and heat generated by the indoor heat exchanger that radiates heat from the outdoor air.
  • An outdoor heat exchanger that evaporates by exchange is sequentially connected.
  • This air conditioner can perform a heating operation in which refrigerant is circulated in the order of a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a compressor.
  • the outdoor heat exchanger has a plurality of heat exchange paths connected to each other in parallel.
  • the liquid side ends of the plurality of heat exchange paths are connected in parallel by a refrigerant shunt for branching the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger to the liquid side ends of the plurality of heat exchange paths.
  • the air conditioner is arbitrarily selected from a plurality of heat exchange paths without allowing the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger to flow into the refrigerant distributor, on the premise of the above configuration.
  • a defrosting flow path mechanism is used to perform a heating defrost operation for evaporating the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger while defrosting an arbitrary heat exchange path. It has become.
  • this heating defrost operation first, the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger is not allowed to flow into the refrigerant diverter by the defrost flow path mechanism, but from the gas side end of any heat exchange path. It passes through an arbitrary heat exchange path toward the side edge. Next, the refrigerant that has passed through any heat exchange path passes through the other heat exchange path from the liquid side end to the gas side end of the other heat exchange path other than the arbitrary heat exchange path through the refrigerant flow divider.
  • the entire outdoor heat exchanger can be defrosted by sequentially performing the heating defrost operation using the defrost flow path mechanism on the plurality of heat exchange paths.
  • this heating defrost operation the entire flow rate of the refrigerant compressed in the compressor is sent to the indoor heat exchanger and used for heating, and then removed by the heat of the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger.
  • Frost can be done. Thereby, defrosting of the outdoor heat exchanger can be performed while obtaining a high defrosting capacity without substantially reducing the heating capacity and also in a weather condition where the outside air temperature is 0 ° C. or less.
  • An air conditioner according to a second aspect is the air conditioner according to the first aspect, wherein the outdoor heat exchanger before the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger flows into the refrigerant distributor. It further has a subcooling path through. Then, the defrosting flow path mechanism allows the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger to pass through the supercooling path, and then the gas in the heat exchange path arbitrarily selected from the plurality of heat exchange paths. It is provided so that it can be sent to the side end.
  • An air conditioner according to a third aspect is the air conditioner according to the first aspect, wherein the outdoor heat exchanger before the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger flows into the refrigerant distributor. It further has a subcooling path through. Then, the defrosting flow path mechanism is configured such that the refrigerant sent from the indoor heat exchanger to the outdoor heat exchanger passes through the subcooling path, and the gas in the heat exchange path arbitrarily selected from the plurality of heat exchange paths. It is provided so that it can be sent to the side end.
  • the heat exchange path can be defrosted without passing the refrigerant through the supercooling path during the heating defrost operation, so the heat of the refrigerant is used only for the defrosting of the heat exchange path. Can do.
  • FIG. 1 It is a schematic structure figure of the air harmony device concerning a 1st embodiment of the present invention. It is a top view (illustrated by removing the top plate) of the outdoor unit. It is the figure which showed typically the outdoor heat exchanger of 1st Embodiment, and the structure of the vicinity. It is a control block diagram of an air conditioning apparatus. It is a figure which shows the flow of the refrigerant
  • FIG. 3 is a pressure-enthalpy diagram illustrating the refrigeration cycle during the heating defrost operation of the first embodiment.
  • FIG. 6 is a pressure-enthalpy diagram illustrating a conventional refrigeration cycle during defrost operation (Patent Document 2). It is a flowchart of the heating defrost driving
  • FIG. 6 is a pressure-enthalpy diagram illustrating a refrigeration cycle during a heating defrost operation according to a second embodiment. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 2nd Embodiment, and is a figure which shows the flow of the refrigerant
  • FIG. 1 is a schematic configuration diagram of an air-conditioning apparatus 1 according to the first embodiment of the present invention.
  • the air conditioner 1 can perform a heating operation, and a split type is adopted here.
  • the air conditioner 1 mainly includes an outdoor unit 2, an indoor unit 4, and a liquid refrigerant communication tube 5 and a gas refrigerant communication tube 6 that connect the outdoor unit 2 and the indoor unit 4.
  • the outdoor unit 2 and the indoor unit 4 constitute a refrigerant circuit 10 for performing a vapor compression refrigeration cycle by being connected via a liquid refrigerant communication tube 5 and a gas refrigerant communication tube 6.
  • the indoor unit 4 is installed indoors and constitutes a part of the refrigerant circuit 10.
  • the indoor unit 4 mainly has an indoor heat exchanger 41.
  • the indoor heat exchanger 41 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air, and functions as a refrigerant radiator during heating operation to heat indoor air.
  • a cross fin type fin-and-tube heat exchanger constituted by heat transfer tubes and a large number of fins is employed as the indoor heat exchanger 41.
  • the indoor heat exchanger 41 has a liquid side connected to the liquid refrigerant communication tube 5 and a gas side connected to the gas refrigerant communication tube 6.
  • the indoor unit 4 has an indoor control unit 49 that controls the operation of each unit constituting the indoor unit 4.
  • the indoor control unit 41 includes a microcomputer and a memory for controlling the indoor unit 4, and exchanges control signals and the like with the outdoor control unit 29 (described later) of the outdoor unit 2. Be able to.
  • the outdoor unit 2 is installed outside and constitutes a part of the refrigerant circuit 10.
  • the outdoor unit 2 mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, an outdoor fan 25, and a defrost flow path mechanism 26.
  • the outdoor unit 2 has a structure in which the inside of a substantially rectangular parallelepiped box-shaped unit casing 51 is divided into a blower chamber S ⁇ b> 1 and a machine chamber S ⁇ b> 2 by a partition plate 58 extending vertically (so-called trunk Mold structure) is adopted.
  • FIG. 2 is a plan view of the outdoor unit 2 (illustrated with the top plate removed).
  • the unit casing 51 mainly includes a bottom plate 52, a top plate, a left front plate 54, a right front plate 56, a right side plate 57, and a partition plate 58.
  • the bottom plate 52 is a horizontally long and substantially rectangular plate-like member that constitutes the bottom surface portion of the unit casing 51.
  • the bottom plate 52 functions as a drain pan for receiving drain water flowing down from the outdoor heat exchanger 23.
  • the top plate is a horizontally long and substantially rectangular plate-like member that constitutes the top surface portion of the outdoor unit 2.
  • the left front plate 54 is a plate-like member mainly constituting the left front surface portion and the left side surface portion of the unit casing 51.
  • the left front plate 54 is formed with a suction port 55a for air sucked into the unit casing 51 by the outdoor fan 25. Further, the left front plate 54 is provided with an outlet 54a for blowing out air taken in from the back side and the left side of the unit casing 51 by the outdoor fan 25 to the outside.
  • the right front plate 56 is a plate-like member that mainly constitutes the front portion of the right front surface and the right side surface of the unit casing 51.
  • the right side plate 57 is a plate-like member that mainly constitutes the rear portion and the right back portion of the right side surface of the unit casing 51.
  • the partition plate 58 is a vertically extending plate-like member disposed on the bottom plate 52, and is disposed so as to partition the internal space of the unit casing 51 into two left and right spaces (that is, the fan chamber S1 and the machine chamber S2). Yes.
  • the compressor 21 is a compressor for sucking and compressing a low-pressure gas refrigerant in the refrigeration cycle to form a high-pressure gas refrigerant in the refrigeration cycle.
  • a volumetric compression element such as a rotary type or a scroll type accommodated in a casing (not shown) is used by a compressor motor 21a also accommodated in the casing.
  • a driven hermetic compressor is employed.
  • the suction side and the discharge side of the compressor 21 are connected to the four-way switching valve 22.
  • the compressor 21 is disposed in the machine room S2.
  • the four-way switching valve 22 is a valve for switching the direction of the refrigerant flow when switching between the cooling operation and the heating operation.
  • the four-way switching valve 22 can connect the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 and can connect the gas refrigerant communication pipe 6 and the suction side of the compressor 21 during cooling operation. (Refer to the solid line of the four-way switching valve 22 in FIG. 1).
  • the four-way switching valve 22 connects the discharge side of the compressor 21 and the gas refrigerant communication pipe 6 and connects the gas side of the outdoor heat exchanger 23 and the suction side of the compressor 21 during heating operation. (Refer to the broken line of the four-way switching valve 22 in FIG. 1).
  • the four-way switching valve 22 is connected to the gas refrigerant communication pipe 6, the suction side and discharge side of the compressor 21, and the gas side of the outdoor heat exchanger 23.
  • the four-way switching valve 22 is disposed in the machine room S2.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant radiator during cooling operation and functions as a refrigerant evaporator during heating operation.
  • a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins is employed as the outdoor heat exchanger 23 .
  • the outdoor heat exchanger 23 has a liquid side connected to the expansion valve 24 via a liquid refrigerant pipe 27, and a gas side connected to the four-way switching valve 22 via a gas refrigerant pipe 28. More specifically, the outdoor heat exchanger 23 includes a large number of fins 61 and a large number of heat transfer tubes 62 attached in a state where these fins 61 are penetrated in the plate thickness direction (FIG. 2). See).
  • the heat transfer tubes 61 are divided into a plurality of (here, three) systems in the vertical direction, and these are separated from each other by a first heat exchange path 31,
  • the second heat exchange path 32 and the third heat exchange path 33 are provided.
  • FIG. 3 is the figure which showed typically the structure of the outdoor heat exchanger 23 and its vicinity.
  • the liquid side ends of the first to third heat exchange paths 31 to 33 are connected to the refrigerant distributor 64 via the first to third capillary tubes 63a to 63c, respectively.
  • the refrigerant flow divider 64 is a pipe member that joins the first to third capillary tubes 63 a to 63 c connected to the liquid side ends of the first to third heat exchange paths 31 to 33, and is connected to the liquid refrigerant pipe 27. ing.
  • the gas side ends of the first to third heat exchange paths 31 to 33 are connected to the header 66 via first to third header communication pipes 65a to 65c, respectively.
  • the header 66 is a pipe member that joins the first to third header connecting pipes 65a to 65c connected to the gas side ends of the first to third heat exchange paths 31 to 33, and is connected to the gas refrigerant pipe 28. Yes.
  • the plurality of (here, three) heat exchange paths 31 to 33 constituting the outdoor heat exchanger 23 are connected in parallel to each other via the refrigerant flow divider 64 and the header 66.
  • all the heat exchange paths 31 to 33 function as a refrigerant radiator, and during the heating operation, all the heat exchange paths 31 to 33 function as a refrigerant evaporator.
  • the outdoor heat exchanger 23 (that is, the heat exchange paths 31 to 33) has an L shape extending from the left side surface of the unit casing 51 to the back surface.
  • the pipe members 63a to 63c, 64, 65a to 65c, 66 for connecting the heat exchange paths 31 to 33 are not shown in FIG. 2, but the right end space of the outdoor heat exchanger 23, that is, the machine room. Arranged in S2.
  • the expansion valve 24 depressurizes the high-pressure liquid refrigerant radiated in the outdoor heat exchanger 23 during the cooling operation before sending it to the indoor heat exchanger 41, and the high-pressure liquid refrigerant radiated in the indoor heat exchanger 41 during the heating operation. This is an electric expansion valve that can be decompressed before being sent to the heat exchanger 23.
  • the expansion valve 24 is provided in the liquid refrigerant pipe 27, one end of which is connected to the liquid refrigerant communication pipe 5, and the other end is connected to the outdoor heat exchanger 23. Although not shown in FIG. 2, the expansion valve 24 is disposed in the machine room S2.
  • the outdoor fan 25 is a blower for sucking outdoor air into the outdoor unit 2, supplying the outdoor air to the outdoor heat exchanger 23, and then discharging the air outside the unit.
  • a propeller fan driven by an outdoor fan motor 25a is employed as the outdoor fan 25 .
  • the outdoor fan 25 is disposed on the front side of the outdoor heat exchanger 23 in the blower chamber S1.
  • the outdoor fan 23 is driven, air is taken into the interior through the suction ports 55a and 55b on the back surface and the left side surface of the unit casing 51, and after passing through the outdoor heat exchanger 23, the air outlet 54a on the front surface of the unit casing 51.
  • the air is blown out from the unit casing 51 to the outside.
  • the outdoor heat exchanger 23 is a heat exchanger that radiates the refrigerant using outdoor air as a cooling source or evaporates the refrigerant using outdoor air as a heating source.
  • the defrosting flow path mechanism 26 is arbitrarily selected from the plurality of heat exchange paths 31 to 33 without causing the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 to flow into the refrigerant flow divider 64. It is a mechanism for sending to the gas side end of the heat exchange path.
  • the defrost flow path mechanism 26 is provided to perform a heating defrost operation which will be described later. In this heating defrost operation, the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 while defrosting any heat exchange path among the heat exchange paths 31 to 33 constituting the outdoor heat exchanger 23. It is the operation which evaporates.
  • the defrost flow path mechanism 26 mainly includes a heat exchange path supply pipe 71, a plurality (here, three) of heat exchange path branch pipes 72a to 72c, and a plurality (here, three) of branch pipe side heat. There are exchange path selection valves 73a to 73c, a plurality (three in this case) of header side heat exchange path selection valves 74a to 74c, and a branch pipe side selection valve 75.
  • the defrost channel mechanism 26 (that is, the refrigerant pipes and valves 71, 72a to 72c, 73a to 73c, 74a to 74c, 75) is disposed in the machine room S2, although not shown in FIG.
  • the heat exchange path supply pipe 71 is a refrigerant pipe for branching from the liquid refrigerant pipe 27 before the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 flows into the refrigerant flow divider 64.
  • One end of the heat exchange path supply pipe 71 is connected to a portion of the liquid refrigerant pipe 27 between the expansion valve 24 and the refrigerant distributor 64, and the other end is connected to the heat exchange path branch pipes 72a to 72c.
  • the first to third heat exchange path branch pipes 72a to 72c are refrigerant pipes for supplying the refrigerant flowing through the heat exchange path supply pipe 71 to the gas side ends of the first to third heat exchange paths 31 to 33.
  • Each of the first to third heat exchange path branch pipes 72a to 72c has one end connected to the heat exchange path supply pipe 71 and the other end connected to the first to third header communication pipes 65a to 65c. Yes.
  • the first to third branch pipe side heat exchange path selection valves 73a to 73c, together with the first to third header side heat exchange path selection valves 74a to 74c, allow the refrigerant flowing through the heat exchange path supply pipe 71 to pass through the heat exchange path 31 to 33 is an electromagnetic valve for selecting which of 33 heat exchange paths to send the refrigerant to.
  • the first to third branch pipe side heat exchange path selection valves 73a to 73c are provided in the first to third heat exchange path branch pipes 72a to 72c, respectively.
  • the first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed. Further, during the heating defrost operation, the branch pipe side heat exchange path selection valve corresponding to the heat exchange path for defrosting among the first to third branch pipe side heat exchange path selection valves 73a to 73c is opened. The branch pipe side heat exchange path selection valve corresponding to the heat exchange path is closed.
  • the first to third header side heat exchange path selection valves 74a to 74c, together with the first to third branch pipe side heat exchange path selection valves 73a to 73c, transfer the refrigerant flowing through the heat exchange path supply pipe 71 to the heat exchange path 31 to 33 is an electromagnetic valve for selecting which of 33 heat exchange paths to send the refrigerant to.
  • the first to third header side heat exchange path selection valves 74a to 74c are connected to the other ends of the first to third heat exchange path branch pipes 72a to 72c among the first to third header communication pipes 65a to 65c, respectively. It is provided in a portion between the position and the header 66.
  • all of the first to third header side heat exchange path selection valves 74a to 74c are opened.
  • the header side heat exchange path selection valve corresponding to the heat exchange path for defrosting is closed among the first to third header side heat exchange path selection valves 74a to 74c, and the other heat exchanges are performed.
  • the header side heat exchange path selection valve corresponding to the path can be opened.
  • the branch pipe side selection valve 75 is an electromagnetic valve for selecting whether the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is branched from the liquid refrigerant pipe 27 before flowing into the flow divider 64. .
  • the branch pipe side selection valve 75 is provided in a portion between the position where the heat exchange path supply pipe 71 is branched in the liquid refrigerant pipe 27 and the refrigerant flow divider 64. And the shunt pipe side selection valve 75 is opened at the time of air_conditionaing
  • the outdoor unit 2 is provided with an outdoor heat exchange temperature sensor 67 that detects a saturation temperature Tsat of the refrigerant flowing through the outdoor heat exchanger 23.
  • the outdoor heat exchange temperature sensor 67 is provided in the vicinity of the liquid side end of the first heat exchange path 31 of the outdoor heat exchanger 23.
  • the outdoor unit 2 also has an outdoor control unit 29 that controls the operation of each part constituting the outdoor unit 2.
  • the outdoor control unit 29 includes a microcomputer and a memory for controlling the outdoor unit 2, and can exchange control signals and the like with the indoor control unit 49 of the indoor unit 4. It is like that.
  • FIG. 4 is a control block diagram of the air conditioner 1. (Operation) Next, operation
  • the control unit 8 performs control of various devices and various processes necessary for performing the following operations.
  • the operation of the air conditioner 1 includes a cooling operation that cools the room, a heating operation that only heats the room, and a heating defrost operation that heats the room while defrosting the outdoor heat exchanger 23. .
  • FIG. 1 is a control block diagram of the air conditioner 1.
  • FIG. 5 is a diagram illustrating the flow of the refrigerant in the air conditioner 1 during the heating operation.
  • FIG. 6 is a flowchart of the heating defrost operation.
  • FIG. 7 is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 during heating and defrosting operation (when defrosting the first heat exchange path 31).
  • FIG. 8 is a pressure-enthalpy diagram illustrating the refrigeration cycle during the heating defrost operation.
  • the cooling operation is an operation in which the refrigerant is circulated in the order of the compressor 21, the outdoor heat exchanger 23, the indoor heat exchanger 41, and the compressor 21.
  • the outdoor heat exchanger 23 functions as a refrigerant radiator
  • the indoor heat exchanger 41 functions as a refrigerant evaporator, thereby cooling indoor air.
  • the outdoor heat exchanger 23 functions as a refrigerant radiator
  • the indoor heat exchanger 41 functions as a refrigerant evaporator (that is, indicated by the solid line of the four-way switching valve 22 in FIG. 1).
  • the four-way selector valve 22 is switched so that Further, the first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed, the first to third header side heat exchange path selection valves 74a to 74c are all opened, and the branch pipe side selection valve 75 is opened. It is in an open state. That is, the refrigerant does not flow through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 26.
  • the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21 and is discharged after being compressed to a high pressure in the refrigeration cycle.
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 through the four-way switching valve 22.
  • the high-pressure refrigerant discharged from the compressor 21 passes through the four-way switching valve 22, the gas refrigerant pipe 28, the header 66, the header communication pipes 65a to 65c, and the header side heat exchange path selection valves 74a to 74c. It is sent to the gas side ends of the heat exchange paths 31 to 33 of the heat exchanger 23.
  • the high-pressure refrigerant sent to the gas side ends of the heat exchange paths 31 to 33 performs heat exchange with the outdoor air supplied by the outdoor fan 25 in the heat exchange paths 31 to 33 to radiate heat.
  • the high-pressure refrigerant radiated in the heat exchange paths 31 to 33 is selected from the liquid side ends of the heat exchange paths 31 to 33 from the capillary tubes 63a to 63c, the refrigerant flow divider 64, the liquid refrigerant pipe 27, and the branch pipe side selection. It is sent to the expansion valve 24 through the valve 75.
  • the refrigerant sent to the expansion valve 24 is depressurized to a low pressure in the refrigeration cycle.
  • the low-pressure refrigerant decompressed by the expansion valve 24 is sent to the indoor heat exchanger 41 through the liquid refrigerant communication pipe 5.
  • the low-pressure refrigerant sent to the indoor heat exchanger 41 evaporates by exchanging heat with indoor air in the indoor heat exchanger 41.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger 41 is again sucked into the compressor 21 through the gas refrigerant communication pipe 6 and the four-way switching valve 22.
  • the heating operation is an operation in which the refrigerant is circulated in the order of the compressor 21, the indoor heat exchanger 41, the outdoor heat exchanger 23, and the compressor 21.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • the outdoor heat exchanger 23 functions as a refrigerant evaporator, thereby heating indoor air.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • the outdoor heat exchanger 23 functions as a refrigerant evaporator (that is, the four-way switching valve 22 in FIGS. 1 and 5).
  • the four-way switching valve 22 is switched so as to be in a state indicated by a broken line.
  • first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed, the first to third header side heat exchange path selection valves 74a to 74c are all opened, and the branch pipe side selection valve 75 is opened. It is in an open state. That is, the refrigerant does not flow through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 26.
  • the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21 and is discharged after being compressed to a high pressure in the refrigeration cycle.
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the gas refrigerant communication pipe 6 through the four-way switching valve 22.
  • the high-pressure refrigerant sent to the indoor heat exchanger 41 radiates heat by exchanging heat with indoor air in the indoor heat exchanger 41.
  • the high-pressure refrigerant that has dissipated heat in the indoor heat exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication tube 5 and depressurized to a low pressure in the refrigeration cycle.
  • the low-pressure refrigerant decompressed by the expansion valve 24 is sent to the outdoor heat exchanger 23.
  • the low-pressure refrigerant decompressed by the expansion valve 24 passes through the liquid refrigerant pipe 27, the branch pipe side selection valve 75, the refrigerant flow divider 64, and the capillary tubes 63a to 63c, and the heat exchange path 31 of the outdoor heat exchanger 23.
  • the low-pressure refrigerant sent to the liquid side ends of the heat exchange paths 31 to 33 evaporates through heat exchange with the outdoor air supplied by the outdoor fan 25 in the heat exchange paths 31 to 33.
  • the low-pressure refrigerant evaporated in the heat exchange paths 31 to 33 flows from the gas side ends of the heat exchange paths 31 to 33 to the header communication pipes 65a to 65c, the header side heat exchange path selection valves 74a to 74c, the header 66, and the gas.
  • the refrigerant is again sucked into the compressor 21 through the refrigerant pipe 28 and the four-way switching valve 22.
  • the heating defrost operation is performed by circulating the refrigerant in the order of the compressor 21, the indoor heat exchanger 41, the outdoor heat exchanger 23, and the compressor 21.
  • the outdoor heat exchanger 23 is defrosted.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • any one of the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 23 is a refrigerant radiator.
  • the remaining heat exchange paths 31 to 33 function as a refrigerant evaporator.
  • the indoor air is heated while the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 23 are sequentially defrosted.
  • the switching state of the four-way switching valve 22 in the heating defrost operation is the same as in the heating operation. That is, the four-way switching valve 22 is in a state in which the indoor heat exchanger 41 functions as a refrigerant radiator and the outdoor heat exchanger 23 functions as a refrigerant evaporator (that is, the four-way valves in FIGS. 1 and 7). The state shown by the broken line of the switching valve 22). Further, since the defrosting of the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 23 is sequentially performed, the selection valves 73a to 73c, 74a to 74c, and 75 are different from those during the cooling operation and the heating operation. Switch to open / closed state.
  • the refrigerant flows through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 26.
  • the operation during the heating defrost operation will be described in detail including the procedure from the start to the end of the heating defrost operation.
  • step S1 it is determined whether the amount of frost formation in the outdoor heat exchanger 23 has increased due to the heating operation, and defrosting has become necessary. Although it is conceivable to determine whether or not this defrosting is necessary based on the duration of the heating operation or the temperature of the outdoor heat exchanger 23, here, the saturation temperature Tsat detected by the outdoor heat exchanger temperature sensor 67. Judgment based on. Specifically, when the saturation temperature Tsat is equal to or lower than the predetermined temperature Tm, it is determined that defrosting of the outdoor heat exchanger 23 is necessary. And when it determines with the defrosting of the outdoor heat exchanger 23 being required in step S1, it transfers to the process of step S2.
  • the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 23 are sequentially defrosted.
  • the defrosting of the first to third heat exchange paths 31 to 33 may basically be arbitrarily selected, but the flow of drain water generated by the defrosting to the bottom plate 52 of the unit casing 51 is considered. Then, it is preferable to carry out from the upper part of the outdoor heat exchanger 23 toward the lower part. For this reason, here, defrosting shall be performed in the order of the first heat exchange path 31, the second heat exchange path 32, and the third heat exchange path 33.
  • the defrosting (step S2) of the first heat exchange path 31 is performed by switching the open / close states of the selection valves 73a to 73c, 74a to 74c, 75 of the defrost flow path mechanism 26. Specifically, the first branch pipe side heat exchange path selection valve 73a is opened, the second and third branch pipe side heat exchange path selection valves 73b and 73c are closed, and the first header side heat exchange path selection valve 74a is closed. Is closed, the second and third header side heat exchange path selection valves 74b and 74c are opened, and the flow dividing pipe side selection valve 75 is switched to a closed state.
  • the first branch pipe side heat exchange path selection valve 73a is opened and the first header side heat exchange path is opened.
  • a switching operation for closing the selection valve 74a and closing the branch pipe side selection valve 75 is performed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the first heat exchange path branch pipe 72a of the defrost flow path mechanism 26.
  • the low-pressure refrigerant in the refrigeration cycle (see point A in FIGS. 7 and 8) is sucked into the compressor 21 and discharged after being compressed to a high pressure in the refrigeration cycle (See point B in FIGS. 7 and 8).
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the gas refrigerant communication pipe 6 through the four-way switching valve 22.
  • the high-pressure refrigerant sent to the indoor heat exchanger 41 radiates heat by exchanging heat with indoor air in the indoor heat exchanger 41 (see point C in FIGS. 7 and 8). Up to this point, it is the same as in the heating operation.
  • the high-pressure refrigerant that has radiated heat in the indoor heat exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication tube 5 and is reduced to a pressure between the high pressure and the low pressure (hereinafter referred to as intermediate pressure) in the refrigeration cycle. (See point D in FIGS. 7 and 8).
  • the intermediate pressure refrigerant decompressed in the expansion valve 24 is sent to the outdoor heat exchanger 23.
  • the intermediate-pressure refrigerant decompressed by the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the heat exchange path supply pipe 71.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the first heat exchange path branch pipe 72a, the first branch pipe side heat exchange path selection valve 73a, and the first header communication pipe 65a. It is sent to the gas side end of the first heat exchange path 31 of the heat exchanger 23.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is all sent to the gas side end of the first heat exchange path 31 without flowing into the refrigerant flow divider 64.
  • the intermediate-pressure refrigerant sent to the gas side end of the first heat exchange path 31 passes through the first heat exchange path 31 from the gas side end of the first heat exchange path 31 toward the liquid side end, Frost adhering to the first heat exchange path 31 of the outdoor heat exchanger 23 is melted (see point E in FIGS. 7 and 8). Thereby, defrosting of the 1st heat exchange path 31 of the outdoor heat exchanger 23 is performed.
  • the intermediate-pressure refrigerant that has passed through the first heat exchange path 31 is sent from the liquid side end of the first heat exchange path 31 to the refrigerant flow divider 64 through the first capillary tube 63a.
  • the first capillary tube 63a flows an intermediate-pressure refrigerant having a larger flow rate than that during the cooling operation or the heating operation. Therefore, the first capillary tube 63a has a pressure loss as compared with the case where the refrigerant flows during the cooling operation or the heating operation. It is greatly reduced to a pressure between the intermediate pressure in the refrigeration cycle (that is, the pressure at point E in FIGS. 7 and 8) and the low pressure (see point F in FIGS. 7 and 8).
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the second and third capillary tubes 63b, because the flow dividing pipe side selection valve 75 is closed.
  • the low-pressure refrigerant evaporated in the second and third heat exchange paths 32 and 33 is supplied from the gas side ends of the second and third heat exchange paths 32 and 33 to the second and third header communication pipes 65b, 65c,
  • the air is again sucked into the compressor 21 through the second and third header side heat exchange path selection valves 74b and 74c, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22.
  • defrosting of the first heat exchange path 31 is started while continuing the indoor heating.
  • defrosting of the 1st heat exchange path 31 is performed until defrosting of the 1st heat exchange path 31 is completed (step S3).
  • the defrosting time t1 of the first heat exchange path 31 is performed until a predetermined time set in advance (that is, a time during which the defrosting of the first heat exchange path 31 can be regarded as completed) has elapsed. .
  • the defrosting (step S4) of the second heat exchange path 32 is performed by switching the open / closed states of the selection valves 73a to 73c, 74a to 74c, 75 of the defrost flow path mechanism 26 in the same manner as the first heat exchange path 31. Done. Specifically, the second branch pipe side heat exchange path selection valve 73b is opened, the first and third branch pipe side heat exchange path selection valves 73a and 73c are closed, and the second header side heat exchange path selection valve 74b. Is closed, the first and third header side heat exchange path selection valves 74a and 74c are opened, and the branch pipe side selection valve 75 is switched to a closed state.
  • the second branch pipe side heat exchange path selection valve 73b is opened, A switching operation is performed in which the first branch pipe side heat exchange path selection valve 73a is closed, the first header side heat exchange path selection valve 74a is opened, and the second header side heat exchange path selection valve 74b is closed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the second heat exchange path branch pipe 72b of the defrost flow path mechanism 26.
  • the low-pressure refrigerant in the refrigeration cycle is compressed to the high pressure in the refrigeration cycle in the compressor 21 in the same manner as in the defrosting of the first heat exchange path 31, and in the indoor heat exchanger 41 Heat is exchanged with room air to dissipate heat, and the expansion valve 24 reduces the pressure to an intermediate pressure in the refrigeration cycle and sends it to the outdoor heat exchanger 23.
  • the intermediate-pressure refrigerant decompressed by the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the heat exchange path supply pipe 71.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the second heat exchange path branch pipe 72b, the second branch pipe side heat exchange path selection valve 73b, and the second header communication pipe 65b. It is sent to the gas side end of the second heat exchange path 32 of the heat exchanger 23.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is all sent to the gas side end of the second heat exchange path 32 without flowing into the refrigerant flow divider 64.
  • the intermediate-pressure refrigerant sent to the gas side end of the second heat exchange path 32 passes through the second heat exchange path 32 from the gas side end of the second heat exchange path 32 toward the liquid side end,
  • the frost adhering to the second heat exchange path 32 of the outdoor heat exchanger 23 is melted.
  • the 2nd heat exchange path 32 of the outdoor heat exchanger 23 is defrosted.
  • the intermediate-pressure refrigerant that has passed through the second heat exchange path 32 is sent from the liquid side end of the second heat exchange path 32 to the refrigerant flow divider 64 through the second capillary tube 63b.
  • the second capillary tube 63b has a flow rate of intermediate pressure refrigerant that is larger than that during cooling operation or heating operation.
  • the second capillary tube 63b has a pressure loss as compared with the case where the refrigerant flows during cooling operation or heating operation. It is greatly reduced to a pressure between the intermediate pressure and the low pressure in the refrigeration cycle.
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the first and third capillary tubes 63a, since the flow dividing pipe side selection valve 75 is closed. Branched to 63c and sent to the liquid side ends of the first and third heat exchange paths 31, 33. At this time, the refrigerant is depressurized to a low pressure in the refrigeration cycle by passing through the first and third capillary tubes 63a and 63c.
  • the low-pressure refrigerant sent to the liquid side ends of the first and third heat exchange paths 31 and 33 is first from the liquid side ends of the first and third heat exchange paths 31 and 33 toward the gas side end. And passes through the third heat exchange paths 31 and 33 and evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 25. Then, the low-pressure refrigerant evaporated in the first and third heat exchange paths 31 and 33 flows from the gas side ends of the first and third heat exchange paths 31 and 33 to the first and third header communication pipes 65a and 65c, The air is again sucked into the compressor 21 through the first and third header side heat exchange path selection valves 74 a and 74 c, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22.
  • defrosting of the second heat exchange path 32 is started while continuing the indoor heating. And the defrosting of the 2nd heat exchange path 32 is performed until the defrosting of the 2nd heat exchange path 32 is completed (step S5).
  • the defrosting time t2 of the second heat exchange path 32 is performed until a predetermined time set in advance (that is, a time during which the defrosting of the second heat exchange path 32 can be considered completed) has elapsed. . Since the second heat exchange path 32 and the other heat exchange paths 31 and 33 have different vertical positions, the time during which it can be considered that the defrosting has been completed is also different.
  • the predetermined time for defrosting the second heat exchange path 32 different from the predetermined time for defrosting the other heat exchange paths 31 and 33.
  • the positional relationship of the heat exchange paths 31 to 33 with respect to the outdoor fan 25 is different, and the air volume of the outdoor air passing through the heat exchange paths 31 to 33 is biased. Therefore, the heat exchange path with a larger air volume is frosted. The amount tends to increase. For this reason, it can be considered that the predetermined time for defrosting the heat exchange path with a large air volume is longer than the predetermined time for defrosting the heat exchange path with a small air volume.
  • the defrosting (step S6) of the third heat exchange path 33 is performed by opening and closing the selection valves 73a to 73c, 74a to 74c, 75 of the defrost flow path mechanism 26, as in the first and second heat exchange paths 31 and 32. This is done by switching the state. Specifically, the third branch pipe side heat exchange path selection valve 73c is opened, the first and second branch pipe side heat exchange path selection valves 73a and 73b are closed, and the third header side heat exchange path selection valve 74c is closed. Is closed, the first and second header side heat exchange path selection valves 74a and 74b are opened, and the branch pipe side selection valve 75 is switched to a closed state.
  • the third branch pipe side heat exchange path selection valve 73c is opened, A switching operation is performed in which the second branch pipe side heat exchange path selection valve 73b is closed, the second header side heat exchange path selection valve 74b is opened, and the third header side heat exchange path selection valve 74c is closed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the third heat exchange path branch pipe 72c of the defrost flow path mechanism 26.
  • the low-pressure refrigerant in the refrigeration cycle is compressed to the high pressure in the refrigeration cycle in the compressor 21 in the same way as when the first and second heat exchange paths 31 and 32 are defrosted.
  • the heat exchanger 41 exchanges heat with room air to dissipate heat, and the expansion valve 24 reduces the pressure to an intermediate pressure in the refrigeration cycle and sends the heat to the outdoor heat exchanger 23.
  • the intermediate-pressure refrigerant decompressed by the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the heat exchange path supply pipe 71.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the third heat exchange path branch pipe 72c, the third branch pipe side heat exchange path selection valve 73c, and the third header communication pipe 65c. It is sent to the gas side end of the third heat exchange path 33 of the heat exchanger 23.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is all sent to the gas side end of the third heat exchange path 33 without flowing into the refrigerant flow divider 64.
  • the intermediate pressure refrigerant sent to the gas side end of the third heat exchange path 33 passes through the third heat exchange path 33 from the gas side end of the third heat exchange path 33 toward the liquid side end,
  • the frost adhering to the third heat exchange path 33 of the outdoor heat exchanger 23 is melted.
  • the 3rd heat exchange path 33 of the outdoor heat exchanger 23 is defrosted.
  • the intermediate-pressure refrigerant that has passed through the third heat exchange path 33 is sent from the liquid side end of the third heat exchange path 33 to the refrigerant flow divider 64 through the third capillary tube 63c.
  • an intermediate pressure refrigerant having a larger flow rate than in the cooling operation or the heating operation flows, so that the pressure loss is smaller than that in the case where the refrigerant flows during the cooling operation or the heating operation. It is greatly reduced to a pressure between the intermediate pressure and the low pressure in the refrigeration cycle.
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the first and second capillary tubes 63a, because the flow dividing pipe side selection valve 75 is closed. Branched to 63 b and sent to the liquid side ends of the first and second heat exchange paths 31 and 32.
  • the refrigerant is depressurized to a low pressure in the refrigeration cycle by passing through the first and second capillary tubes 63a and 63b.
  • the low-pressure refrigerant sent to the liquid side ends of the first and second heat exchange paths 31 and 32 is first from the liquid side ends of the first and second heat exchange paths 31 and 32 toward the gas side ends. Then, it passes through the second heat exchange paths 31 and 32 and evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 25.
  • the low-pressure refrigerant evaporated in the first and second heat exchange paths 31 and 32 flows from the gas side ends of the first and second heat exchange paths 31 and 32 to the first and second header communication pipes 65a and 65b, The air is again sucked into the compressor 21 through the first and second header side heat exchange path selection valves 74a and 74b, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22. In this way, defrosting of the third heat exchange path 33 is started while continuing the indoor heating. And the defrosting of the 3rd heat exchange path 33 is performed until the defrosting of the 2nd heat exchange path 33 is completed (step S7).
  • the defrosting time t3 of the third heat exchange path 33 is performed until a predetermined time set in advance (that is, a time during which the defrosting of the third heat exchange path 33 can be considered completed) has elapsed.
  • the predetermined time for defrosting the third heat exchange path 33 is also determined in consideration of the positional relationship of the heat exchange paths 31 to 33 with respect to the outdoor fan 25 and the like. It is preferable to make them different from each other.
  • the heating operation is resumed (step S8).
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is defrosted by the defrost flow path mechanism 26 while defrosting any of the heat exchange paths 31 to 33.
  • Evaporative heating operation is performed.
  • the heating defrosting operation is sequentially performed on the plurality of heat exchange paths 31 to 33, so that the entire outdoor heat exchanger 23 is defrosted while the indoor heating is continued.
  • the air conditioner 1 of the present embodiment has the following characteristics.
  • the air conditioner 1 includes the compressor 21 that compresses the refrigerant, the indoor heat exchanger 41 that radiates the refrigerant compressed in the compressor 21, and the refrigerant that has radiated heat in the indoor heat exchanger 41.
  • An outdoor heat exchanger 23 that is evaporated by heat exchange with air is sequentially connected.
  • the air conditioner 1 can perform a heating operation in which the refrigerant is circulated in the order of the compressor 21, the indoor heat exchanger 41, the outdoor heat exchanger 23, and the compressor 21.
  • the outdoor heat exchanger 23 has a plurality (here, three) of heat exchange paths 31 to 33 connected in parallel to each other.
  • the liquid side ends of the plurality of heat exchange paths 31 to 33 are refrigerant distributors for branching the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 to the liquid side ends of the plurality of heat exchange paths 31 to 33. 64 are connected in parallel.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 does not flow into the refrigerant diverter 64, and the plurality of heat exchange paths 31 to A defrost channel mechanism 26 is further provided for sending to the gas side end of the heat exchange path arbitrarily selected from among 33.
  • the defrosting flow path mechanism 26 performs a heating defrost operation in which the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is evaporated while defrosting an arbitrary heat exchange path. To do.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is not allowed to flow into the refrigerant diverter 64 by the defrost flow path mechanism 26, and the gas in any heat exchange path. It passes through an arbitrary heat exchange path from the side end toward the liquid side end.
  • the refrigerant that has passed through the arbitrary heat exchange path passes through the refrigerant flow divider 64 in the other heat exchange path from the liquid side end of the other heat exchange path other than the arbitrary heat exchange path toward the gas side end. Let it pass.
  • the entire outdoor heat exchanger 23 can be defrosted by sequentially performing the heating defrost operation using the defrost flow path mechanism 26 on the plurality of heat exchange paths 31 to 33. It can be done.
  • an electromagnetic valve is provided at each of the liquid side ends of the plurality of heat exchange paths of the outdoor heat exchanger, and the electromagnetic valve of the arbitrarily selected heat exchange path is closed. The flow of the refrigerant in the heat exchange path is stopped, and any heat exchange path is defrosted by the heat of the outdoor air.
  • FIG. 9 is a pressure-enthalpy diagram illustrating a conventional refrigeration cycle during defrost operation (Patent Document 2).
  • the entire flow rate of the refrigerant compressed in the compressor 21 is sent to the indoor heat exchanger 41 and used for heating (FIGS. 7 and 8). Then, defrosting is performed by the heat of the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 (see point D in FIGS. 7 and 8). To the point E). Therefore, in the air conditioner 1, unlike the defrost system disclosed in Patent Document 2, the entire flow rate of the refrigerant compressed in the compressor 21 is used for indoor heating, so that the heating capacity is hardly reduced.
  • the total flow rate of the refrigerant compressed in the compressor 21 is used for defrosting an arbitrary heat exchange path of the outdoor heat exchanger 23. Therefore, a high defrosting capability can be obtained.
  • defrosting is completed in a short time, the time which is heating can be lengthened, and integral heating capability can be raised.
  • the heat of the refrigerant is used for defrosting. Therefore, the outdoor heat exchanger 23 can be used even in weather conditions where the outside air temperature is 0 ° C. or less. Defrosting can be performed.
  • the heat exchange path (here, the first heat exchange path 31) constituting the upper part of the outdoor heat exchanger 23 to the heat exchange path (here, the third heat exchange path 33) constituting the lower part. ). For this reason, drain water generated by defrosting can be smoothly drained to the bottom plate 52 of the unit casing 51.
  • the heat exchange paths 31 to 33 constituting the outdoor heat exchanger 23 are defrosted for a predetermined time set in consideration of the position of the heat exchange path.
  • a predetermined time for defrosting the heat exchange path with a large air volume is considered in consideration of the bias in the air volume of the outdoor air passing through the heat exchange paths 31 to 33 due to the difference in position of the heat exchange paths 31 to 33 with respect to the outdoor fan 25.
  • the predetermined time of defrosting of the heat exchange path where the amount of frost increases because the air volume is large is shortened, and the predetermined time of defrosting of the heat exchange path where the amount of frost decreases because the air volume is small
  • the defrosting of the heat exchange paths 31 to 33 is performed after a predetermined time in which the defrosting times t1 to t3 are set in advance.
  • the present invention is not limited to this.
  • the defrosting of the first heat exchange path 31 that performs defrosting first among the plurality (three in this case) of heat exchange paths 31 to 33 constituting the outdoor heat exchanger 23 is performed. This is performed until the saturation temperature Tsat detected by the outdoor heat exchange temperature sensor 67 rises above a predetermined temperature (step S11).
  • this predetermined temperature is set to a temperature at which defrosting of the first heat exchange path 31 can be considered completed.
  • the defrost time t1 at this time is measured, the predetermined time of the defrost of the 2nd and 3rd heat exchange paths 32 and 33 is set from this defrost time t1 (step S12), and the 2nd and 2nd The defrosting of the three heat exchange paths 32 and 33 may be performed only for the set predetermined time (steps S5 and S7).
  • FIG. 10 is a flowchart of the heating defrost operation according to this modification.
  • the heating defrost operation of the present modification is different from the heating defrost operation in which the completion of defrosting of each heat exchange path is determined only by time.
  • the completion of defrosting is detected from the temperature change, and this time is obtained from the time actually required for defrosting.
  • the completion of defrosting of the other heat exchange path is determined based on the predetermined time. For this reason, in the heating defrost operation of this modification, the time required for defrosting of each heat exchange path is set for each heating defrost operation according to the frosting state of the outdoor heat exchanger 23.
  • the predetermined time for defrosting of each heat exchange path is set for each heating defrost operation, compared to the case where the defrosting of each heat exchange path is performed until a predetermined time set in advance. It can be set appropriately.
  • the defrosting flow path mechanism 26 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a.
  • header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75 but is not limited thereto.
  • a switching valve 77 in which branch pipe side heat exchange path selection valves 73a to 73c are integrated may be used.
  • the switching valve 77 sends the refrigerant flowing through the heat exchange path supply pipe 71 to any of the heat exchange path branch pipes 72a to 72c, or does not send the refrigerant to any of the heat exchange path branch pipes 72a to 72c.
  • This is a switching valve having a function of selecting this.
  • a rotary type switching valve is used as the switching valve 77.
  • the switching valve 77 is connected to the heat exchange path supply pipe 71 and the heat exchange path branch pipes 72a to 72c.
  • a switching valve 77 is connected to the control unit 8 instead of the branch pipe side heat exchange path selection valves 73a to 73c in the control block diagram of FIG. FIG.
  • FIG. 11 is a schematic configuration diagram of the air-conditioning apparatus 1 according to this modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 during heating operation.
  • FIG. 12 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 1 during the heating defrost operation of the present modification.
  • the switching valve 77 by operating the switching valve 77 so as not to send the refrigerant to any of the heat exchange path branch pipes 72a to 72c, the same heating as in the above embodiment is performed. You can drive. Further, in the operation state of the switching valve 77 similar to that in the heating operation, the same cooling operation as in the above embodiment can be performed. Then, as shown in FIG. 12, the switching valve 77 is operated so as to send the refrigerant flowing through the heat exchange path supply pipe 71 to any one of the heat exchange path branch pipes 72a to 72c. The same heating defrost operation can be performed.
  • the defrosting flow path mechanism 26 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a. To 73c, header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75, but is not limited thereto.
  • a switching valve 78 in which a heat exchange path supply pipe 71, branch pipe side heat exchange path selection valves 73a to 73c, and a branch pipe side selection valve 75 are integrated is used. You may do it.
  • the switching valve 78 selects whether the refrigerant flowing through the liquid refrigerant pipe 27 flows to the refrigerant distribution pipe 64 or sent to any one of the heat exchange path branch pipes 72a to 72c, and the heat exchange path branch pipes 72a to 72c.
  • the switching valve has a function of selecting which one of the heat exchange path branch pipes 72a to 72c is sent with the refrigerant.
  • a rotary type switching valve is used as the switching valve 78.
  • the switching valve 78 is connected to the liquid refrigerant pipe 27, the refrigerant distribution pipe 64, and the heat exchange path branch pipes 72a to 72c.
  • a switching valve 78 is connected to the control unit 8 in place of the branch pipe side heat exchange path selection valves 73a to 73c and the branch pipe side selection valve 75 in the control block diagram of FIG. .
  • FIG. 13 is a schematic configuration diagram of the air-conditioning apparatus 1 according to this modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 during heating operation.
  • FIG. 14 is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 (when defrosting the first heat exchange path 31) during the heating defrost operation of the present modification.
  • the heating operation similar to that in the above embodiment is performed. It can be carried out. Further, in the operation state of the switching valve 78 similar to that in the heating operation, the same cooling operation as in the above embodiment can be performed. Then, as shown in FIG. 14, the switching valve 78 is operated so as to send the refrigerant flowing through the liquid refrigerant pipe 27 to any one of the heat exchange path branch pipes 72a to 72c without flowing the refrigerant into the refrigerant distribution pipe 64.
  • the heating defrost operation similar to the embodiment or the first modification can be performed.
  • the defrosting flow path mechanism 26 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a. To 73c, header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75, but is not limited thereto.
  • the heat exchange path branch pipes 72a to 72c, the branch pipe side heat exchange path selection valves 73a to 73c, the header side heat exchange path selection valves 74a to 74c, and the header 66 Alternatively, a switching valve 79 may be used.
  • the switching valve 79 selects which of the header communication pipes 65a to 65c the refrigerant flowing through the heat exchange path supply pipe 71 is sent to, and the header communication pipe to which the refrigerant flowing through the heat exchange path supply pipe 71 is sent.
  • the other header communication pipes are switching valves having a function of connecting to the gas refrigerant pipe 28 or selecting not to send the refrigerant to any of the header communication pipes 65a to 65c.
  • FIG. 15 is a schematic configuration diagram of the air-conditioning apparatus 1 according to this modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 during heating operation.
  • FIG. 16 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 1 during the heating defrost operation of the present modification.
  • the heating operation similar to the above embodiment is performed. It can be carried out.
  • the same cooling operation as in the above embodiment can be performed in the operation state of the switching valve 79 similar to that in the heating operation. Then, as shown in FIG. 16, it is selected which of the header communication pipes 65a to 65c the refrigerant flowing through the heat exchange path supply pipe 71 is sent to, and the header communication to which the refrigerant flowing through the heat exchange path supply pipe 71 is sent.
  • the heating defrost operation similar to that of the above-described embodiment or modification 1 can be performed. And in the structure of this modification, compared with the structure of the said embodiment and the modification 1, and the structure of the modifications 2, 3, the number of parts which comprise the flow-path mechanism 26 for defrost can be reduced.
  • the defrosting flow path mechanism 26 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a.
  • the header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75 but is not limited thereto.
  • a switching valve 80 in which 74a to 74c, the branch pipe side selection valve 75, and the header 66 are integrated may be used.
  • the switching valve 80 selects whether the refrigerant flowing through the liquid refrigerant pipe 27 flows to the refrigerant distribution pipe 64 or the header communication pipes 65a to 65c, and the refrigerant flowing through the liquid refrigerant pipe 27 is sent.
  • a header connecting pipe other than the header connecting pipe is a switching valve having a function of connecting to the gas refrigerant pipe 28.
  • a rotary switching valve is used as the switching valve 80. This switching valve 80 is connected to the liquid refrigerant pipe 27, the refrigerant distribution pipe 64, the header communication pipes 65 a to 65 c and the gas refrigerant pipe 28.
  • FIG. 17 is a schematic configuration diagram of the air-conditioning apparatus 1 according to this modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 1 during heating operation.
  • FIG. 18 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 1 during the heating defrost operation of the present modification.
  • the heating operation similar to the above embodiment is performed. It can be carried out. Further, the same cooling operation as in the above embodiment can be performed in the operation state of the switching valve 80 similar to that in the heating operation. Then, as shown in FIG. 18, a header other than the header communication pipe to which the refrigerant flowing through the liquid refrigerant pipe 27 is selected to be sent to any of the header communication pipes 65a to 65c and the refrigerant flowing through the liquid refrigerant pipe 27 is sent.
  • the heating defrost operation similar to that in the above embodiment or the first modification can be performed.
  • the number of parts constituting the defrost flow path mechanism 26 can be reduced as compared with the configurations of the above-described embodiment and the first modification, and further, the configurations of the second to fourth modifications.
  • the defrosting flow path mechanism 26 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a.
  • header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75 but is not limited thereto.
  • switching valves 81a to 81c in which branch pipe side heat exchange path selection valves 73a to 73c and header side heat exchange path selection valves 74a to 74c are integrated are used. Also good.
  • the switching valves 81a to 81c send the refrigerant flowing through the heat exchange path supply pipe 71 from the gas side end to the liquid side end of the heat exchange paths 31 to 33, or through the refrigerant distribution pipe 64.
  • This is a switching valve having a function of selecting whether or not the refrigerant that has passed through 31 to 33 from the liquid side end toward the gas side end is sent to the header 66.
  • three-way valves are used as the switching valves 81a to 81c.
  • These switching valves 81a to 81c are connected to the heat exchange path branch pipes 72a to 72c and the header communication pipes 65a to 65c. In the configuration of this modification, in the control block diagram of FIG.
  • FIG. 19 is a schematic configuration diagram of the air-conditioning apparatus 1 according to the present modification, and is a diagram illustrating the flow of the refrigerant in the air-conditioning apparatus 1 during the heating operation.
  • FIG. 20 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 1 during the heating defrost operation of the present modification.
  • switching is performed so that the refrigerant that has passed through the heat exchange paths 31 to 33 through the refrigerant distribution pipe 64 from the liquid side end to the gas side end is sent to the header 66.
  • the valves 81a to 81c By operating the valves 81a to 81c, the heating operation similar to that in the above embodiment can be performed. Further, the same cooling operation as in the above embodiment can be performed in the operation state of the switching valves 81a to 81c similar to that in the heating operation. Then, as shown in FIG. 20, any one of the switching valves 81a to 81c is operated so as to send the refrigerant flowing through the heat exchange path supply pipe 71 from the gas side end to the liquid side end of the heat exchange paths 31 to 33.
  • the other switching valve is operated by sending the refrigerant that has passed through the heat exchange paths 31 to 33 through the refrigerant distribution pipe 64 from the liquid side end toward the gas side end to the header 66.
  • a heating defrost operation similar to that of the first modification can be performed.
  • the configuration of the heating defrost operation according to the present invention is applied to the outdoor heat exchanger 23 having a plurality of heat exchange paths 31 to 33 connected in parallel to each other.
  • the heating defrost operation according to the present invention is applied not only to the plurality of heat exchange paths 31 to 33 but also to the outdoor heat exchanger 123 having the supercooling path 34 through which the refrigerant passes before flowing into the refrigerant distributor 64.
  • the following configuration may be applied. FIG.
  • the air conditioner 101 mainly includes an outdoor unit 102, an indoor unit 4, and a liquid refrigerant communication tube 5 and a gas refrigerant communication tube 6 that connect the outdoor unit 102 and the indoor unit 4.
  • the outdoor unit 102 and the indoor unit 4 constitute a refrigerant circuit 110 for performing a vapor compression refrigeration cycle by being connected via a liquid refrigerant communication pipe 5 and a gas refrigerant communication pipe 6.
  • the indoor unit 4 is installed indoors and constitutes a part of the refrigerant circuit 110.
  • the indoor unit 4 mainly has an indoor heat exchanger 41. Note that the configuration of the indoor unit 4 is the same as the configuration of the indoor unit 4 of the first embodiment, and a description thereof will be omitted here.
  • the outdoor unit 102 is installed outside and constitutes a part of the refrigerant circuit 110.
  • the outdoor unit 102 mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 123, an expansion valve 24, an outdoor fan 25, and a defrost channel mechanism 126.
  • the configuration of the outdoor unit 102 is the same as the configuration of the outdoor unit 2 of the first embodiment except for the configuration of the outdoor heat exchanger 123 and the defrosting flow path mechanism 126.
  • the configuration of the 123 and the defrost flow path mechanism 126 will be described in detail.
  • the outdoor heat exchanger 123 is a heat exchanger that functions as a refrigerant radiator during cooling operation and functions as a refrigerant evaporator during heating operation.
  • a cross fin type fin-and-tube heat exchanger constituted by a heat transfer tube and a large number of fins is employed as the outdoor heat exchanger 123.
  • the outdoor heat exchanger 123 has a liquid side connected to the expansion valve 24 via a liquid refrigerant pipe 27 and a gas side connected to the four-way switching valve 22 via a gas refrigerant pipe 28. More specifically, the outdoor heat exchanger 123 is attached in a state where a large number of fins 61 and these fins 61 are penetrated in the plate thickness direction, like the outdoor heat exchanger 23 of the first embodiment.
  • FIG. 22 is a diagram schematically showing the outdoor heat exchanger 123 and the structure in the vicinity thereof.
  • the liquid side ends of the first to third heat exchange paths 31 to 33 are connected to the refrigerant distributor 64 via the first to third capillary tubes 63a to 63c, respectively.
  • the refrigerant flow divider 64 is a pipe member that joins the first to third capillary tubes 63a to 63c connected to the liquid side ends of the first to third heat exchange paths 31 to 33, and is a supercooling path-heat exchange path. It is connected to the communication pipe 35.
  • the gas side ends of the first to third heat exchange paths 31 to 33 are connected to the header 66 via first to third header communication pipes 65a to 65c, respectively.
  • the header 66 is a pipe member that joins the first to third header connecting pipes 65a to 65c connected to the gas side ends of the first to third heat exchange paths 31 to 33, and is connected to the gas refrigerant pipe 28. Yes.
  • the supercooling path 34 is connected in common to the liquid side ends of the first to third heat exchange paths 31 to 33.
  • the liquid side end of the supercooling path 34 is connected to the liquid refrigerant pipe 27.
  • the gas side end of the supercooling path 34 is connected to a supercooling path-heat exchange path connecting pipe 35.
  • the plurality of (here, three) heat exchange paths 31 to 33 constituting the outdoor heat exchanger 123 are connected in parallel to each other via the refrigerant flow divider 64 and the header 66.
  • the subcooling path 34 constituting the outdoor heat exchanger 123 is connected to the liquid side ends of the heat exchange paths 31 to 33 via the refrigerant flow divider 64 and the supercooling path-heat exchange path connecting pipe 35. .
  • all the heat exchange paths 31 to 33 function as a refrigerant radiator, and the supercooling path 34 functions as a refrigerant subcooler that radiates heat in the heat exchange paths 31 to 33. Further, during the heating operation, the supercooling path 34 functions as a radiator for the refrigerant in the intermediate pressure state after passing through the expansion valve 24 to prevent frosting at the bottom of the outdoor heat exchanger 123, and The heat exchange paths 31 to 33 function as a refrigerant evaporator.
  • the defrost flow path mechanism 126 passes a plurality of heat exchange paths without allowing the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 123 to flow into the refrigerant flow divider 64 after passing through the supercooling path 34. It is a mechanism for sending to the gas side end of the heat exchange path arbitrarily selected from 31 to 33.
  • the defrost flow path mechanism 126 is provided to perform a heating defrost operation described later. In this heating defrost operation, the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 while defrosting any of the heat exchange paths 31 to 33 constituting the outdoor heat exchanger 123. It is the operation which evaporates.
  • the defrost flow path mechanism 126 mainly includes a heat exchange path supply pipe 71, a plurality (here, three) heat exchange path branch pipes 72a to 72c, and a plurality (here, three) branch pipe side heat.
  • the heat exchange path supply pipe 71 passes the supercooling path ⁇ after the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 passes through the supercooling path 34 and before flowing into the refrigerant distributor 64. It is a refrigerant pipe for branching from the heat exchange path connecting pipe 35. One end of the heat exchange path supply pipe 71 is connected to a portion of the supercooling path-heat exchange path connecting pipe 35 between the gas side end of the supercooling path 34 and the refrigerant flow divider 64, and the other end.
  • the heat exchange path branch pipes 72a to 72c are connected.
  • the first to third heat exchange path branch pipes 72a to 72c are refrigerant pipes for supplying the refrigerant flowing through the heat exchange path supply pipe 71 to the gas side ends of the first to third heat exchange paths 31 to 33.
  • Each of the first to third heat exchange path branch pipes 72a to 72c has one end connected to the heat exchange path supply pipe 71 and the other end connected to the first to third header communication pipes 65a to 65c. Yes.
  • the first to third branch pipe side heat exchange path selection valves 73a to 73c, together with the first to third header side heat exchange path selection valves 74a to 74c, allow the refrigerant flowing through the heat exchange path supply pipe 71 to pass through the heat exchange path 31 to 33 is an electromagnetic valve for selecting which of 33 heat exchange paths to send the refrigerant to.
  • the first to third branch pipe side heat exchange path selection valves 73a to 73c are provided in the first to third heat exchange path branch pipes 72a to 72c, respectively. During the cooling operation and the heating operation, the first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed.
  • the branch pipe side heat exchange path selection valve corresponding to the heat exchange path for defrosting among the first to third branch pipe side heat exchange path selection valves 73a to 73c is opened.
  • the branch pipe side heat exchange path selection valve corresponding to the heat exchange path is closed.
  • the first to third header side heat exchange path selection valves 74a to 74c, together with the first to third branch pipe side heat exchange path selection valves 73a to 73c, transfer the refrigerant flowing through the heat exchange path supply pipe 71 to the heat exchange path 31 to 33 is an electromagnetic valve for selecting which of 33 heat exchange paths to send the refrigerant to.
  • the first to third header side heat exchange path selection valves 74a to 74c are connected to the other ends of the first to third heat exchange path branch pipes 72a to 72c among the first to third header communication pipes 65a to 65c, respectively. It is provided in a portion between the position and the header 66.
  • all of the first to third header side heat exchange path selection valves 74a to 74c are opened.
  • the header side heat exchange path selection valve corresponding to the heat exchange path for defrosting is closed among the first to third header side heat exchange path selection valves 74a to 74c, and the other heat exchanges are performed.
  • the header side heat exchange path selection valve corresponding to the path can be opened.
  • the shunt pipe side selection valve 75 is configured to pass the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 after passing through the supercooling path 34 and before flowing into the refrigerant flow divider 64. It is a solenoid valve for selecting whether or not to branch from the heat exchange path connecting pipe 35.
  • the branch pipe side selection valve 75 is provided in a portion between the position where the heat exchange path supply pipe 71 is branched in the supercooling path-heat exchange path connecting pipe 35 and the refrigerant distributor 64. And the shunt pipe side selection valve 75 is opened at the time of air_conditionaing
  • the operation of the air conditioner 101 includes a cooling operation that cools the room, a heating operation that only heats the room, and a heating defrost operation that heats the room while defrosting the outdoor heat exchanger 23. .
  • FIG. 23 is a diagram illustrating the flow of the refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 24 is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during heating / defrosting operation (when defrosting the first heat exchange path 31).
  • FIG. 25 is a pressure-enthalpy diagram illustrating the refrigeration cycle during the heating defrost operation.
  • the cooling operation is an operation in which the refrigerant is circulated in the order of the compressor 21, the outdoor heat exchanger 123, the indoor heat exchanger 41, and the compressor 21.
  • the outdoor heat exchanger 123 functions as a refrigerant radiator
  • the indoor heat exchanger 41 functions as a refrigerant evaporator, thereby cooling indoor air.
  • the outdoor heat exchanger 123 functions as a refrigerant radiator and the indoor heat exchanger 41 functions as a refrigerant evaporator (that is, indicated by the solid line of the four-way switching valve 22 in FIG. 21).
  • the four-way selector valve 22 is switched so that Further, the first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed, the first to third header side heat exchange path selection valves 74a to 74c are all opened, and the branch pipe side selection valve 75 is opened. It is in an open state. That is, the refrigerant does not flow through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 126.
  • the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21 and discharged after being compressed to a high pressure in the refrigeration cycle.
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 123 through the four-way switching valve 22.
  • the high-pressure refrigerant discharged from the compressor 21 passes through the four-way switching valve 22, the gas refrigerant pipe 28, the header 66, the header communication pipes 65a to 65c, and the header side heat exchange path selection valves 74a to 74c. It is sent to the gas side ends of the heat exchange paths 31 to 33 of the heat exchanger 123.
  • the high-pressure refrigerant sent to the gas side ends of the heat exchange paths 31 to 33 performs heat exchange with the outdoor air supplied by the outdoor fan 25 in the heat exchange paths 31 to 33 to radiate heat.
  • the high-pressure refrigerant that has radiated heat in the heat exchange paths 31 to 33 flows from the liquid side ends of the heat exchange paths 31 to 33, capillary tubes 63a to 63c, refrigerant flow divider 64, supercooling path-heat exchange path connecting pipe 35, And, it is sent to the gas side end of the supercooling path 34 of the outdoor heat exchanger 123 through the branch pipe side selection valve 75.
  • the high-pressure refrigerant sent to the gas side end of the supercooling path 34 further dissipates heat by exchanging heat with the outdoor air supplied by the outdoor fan 25 in the supercooling path 34.
  • the high-pressure refrigerant supercooled in the supercooling path 34 is sent to the expansion valve 24 through the liquid refrigerant pipe 27.
  • the refrigerant sent to the expansion valve 24 is depressurized to a low pressure in the refrigeration cycle.
  • the low-pressure refrigerant decompressed by the expansion valve 24 is sent to the indoor heat exchanger 41 through the liquid refrigerant communication pipe 5.
  • the low-pressure refrigerant sent to the indoor heat exchanger 41 evaporates by exchanging heat with indoor air in the indoor heat exchanger 41.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger 41 is again sucked into the compressor 21 through the gas refrigerant communication pipe 6 and the four-way switching valve 22.
  • the heating operation is an operation in which the refrigerant is circulated in the order of the compressor 21, the indoor heat exchanger 41, the outdoor heat exchanger 123, and the compressor 21.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • the outdoor heat exchanger 123 functions as a refrigerant evaporator, thereby heating indoor air.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • the outdoor heat exchanger 123 functions as a refrigerant evaporator (that is, the four-way switching valve 22 in FIGS. 21 and 23).
  • the four-way switching valve 22 is switched so as to be in a state indicated by a broken line.
  • first to third branch pipe side heat exchange path selection valves 73a to 73c are all closed, the first to third header side heat exchange path selection valves 74a to 74c are all opened, and the branch pipe side selection valve 75 is opened. It is in an open state. That is, the refrigerant does not flow through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 126.
  • the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21 and is discharged after being compressed to a high pressure in the refrigeration cycle.
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the gas refrigerant communication pipe 6 through the four-way switching valve 22.
  • the high-pressure refrigerant sent to the indoor heat exchanger 41 radiates heat by exchanging heat with indoor air in the indoor heat exchanger 41.
  • the high-pressure refrigerant that has dissipated heat in the indoor heat exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication pipe 5 and reduced to an intermediate pressure in the refrigeration cycle.
  • the intermediate-pressure refrigerant decompressed by the expansion valve 24 is sent to the outdoor heat exchanger 123. Then, the intermediate pressure refrigerant decompressed in the expansion valve 24 is sent to the liquid side end of the supercooling path 34 of the outdoor heat exchanger 123 through the liquid refrigerant pipe 27.
  • the intermediate-pressure refrigerant sent to the liquid side end of the supercooling path 34 radiates heat by exchanging heat with the outdoor air supplied by the outdoor fan 25 in the supercooling path 34, thereby performing outdoor heat exchange. Frost formation at the bottom of the vessel 123 is prevented.
  • the low-pressure refrigerant radiated in the supercooling path 34 is supplied from the gas side end of the supercooling path 34 to the supercooling path-heat exchange path connecting pipe 35, the diversion pipe side selection valve 75, the refrigerant flow divider 64, and the capillary It is sent to the liquid side ends of the heat exchange paths 31 to 33 of the outdoor heat exchanger 23 through the tubes 63a to 63c.
  • the low-pressure refrigerant sent to the liquid side ends of the heat exchange paths 31 to 33 evaporates through heat exchange with the outdoor air supplied by the outdoor fan 25 in the heat exchange paths 31 to 33.
  • the low-pressure refrigerant evaporated in the heat exchange paths 31 to 33 flows from the gas side ends of the heat exchange paths 31 to 33 to the header communication pipes 65a to 65c, the header side heat exchange path selection valves 74a to 74c, the header 66, and the gas.
  • the refrigerant is again sucked into the compressor 21 through the refrigerant pipe 28 and the four-way switching valve 22.
  • the heating defrost operation is performed by circulating the refrigerant in the order of the compressor 21, the indoor heat exchanger 41, the outdoor heat exchanger 123, and the compressor 21, In this operation, the outdoor heat exchanger 123 is defrosted.
  • the indoor heat exchanger 41 functions as a refrigerant radiator
  • any one of the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 123 is a refrigerant radiator.
  • the remaining heat exchange paths 31 to 33 function as a refrigerant evaporator. Accordingly, the indoor air is heated while the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 123 are sequentially defrosted.
  • the switching state of the four-way switching valve 22 in the heating defrost operation is the same as in the heating operation. That is, the four-way switching valve 22 is in a state where the indoor heat exchanger 41 functions as a refrigerant radiator and the outdoor heat exchanger 123 functions as a refrigerant evaporator (that is, the four-way valves in FIGS. 21 and 24). The state shown by the broken line of the switching valve 22). Further, since the defrosting of the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 123 is sequentially performed, the selection valves 73a to 73c, 74a to 74c, and 75 are different from those during the cooling operation and the heating operation. Switch to open / closed state.
  • the refrigerant flows through the heat exchange path supply pipe 71 and the first to third heat exchange path branch pipes 72a to 72c of the defrost flow path mechanism 126.
  • the operation during the heating defrost operation will be described in detail including the procedure from the start to the end of the heating defrost operation.
  • step S1 it is determined whether or not the amount of frost formation in the outdoor heat exchanger 123 has increased due to the heating operation, and defrosting is necessary. In addition, since determination of whether this defrost is required is the same as that of step S1 of the heating defrost operation of 1st Embodiment, description is abbreviate
  • steps S2 to S7 the first to third heat exchange paths 31 to 33 of the outdoor heat exchanger 123 are sequentially defrosted.
  • the defrosting of the first to third heat exchange paths 31 to 33 may basically be arbitrarily selected, but the flow of drain water generated by the defrosting to the bottom plate 52 of the unit casing 51 is considered.
  • defrosting shall be performed in the order of the first heat exchange path 31, the second heat exchange path 32, and the third heat exchange path 33.
  • the defrosting (step S2) of the first heat exchange path 31 is performed by switching the open / close states of the selection valves 73a to 73c, 74a to 74c, 75 of the defrost flow path mechanism 126. Specifically, the first branch pipe side heat exchange path selection valve 73a is opened, the second and third branch pipe side heat exchange path selection valves 73b and 73c are closed, and the first header side heat exchange path selection valve 74a is closed. Is closed, the second and third header side heat exchange path selection valves 74b and 74c are opened, and the flow dividing pipe side selection valve 75 is switched to a closed state.
  • the first branch pipe side heat exchange path selection valve 73a is opened and the first header side heat exchange path is opened.
  • a switching operation for closing the selection valve 74a and closing the branch pipe side selection valve 75 is performed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the first heat exchange path branch pipe 72a of the defrost flow path mechanism 126.
  • the low-pressure refrigerant (see point A in FIGS. 24 and 25) in the refrigeration cycle is sucked into the compressor 21 and discharged after being compressed to a high pressure in the refrigeration cycle (See point B in FIGS. 24 and 25).
  • the high-pressure refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the gas refrigerant communication pipe 6 through the four-way switching valve 22.
  • the high-pressure refrigerant sent to the indoor heat exchanger 41 radiates heat by exchanging heat with indoor air in the indoor heat exchanger 41 (see point C in FIGS. 24 and 25). Up to this point, it is the same as in the heating operation.
  • the high-pressure refrigerant that has radiated heat in the indoor heat exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication tube 5 and is reduced to a pressure between the high pressure and the low pressure (hereinafter referred to as intermediate pressure) in the refrigeration cycle. (See point D in FIGS. 24 and 25).
  • the intermediate-pressure refrigerant decompressed by the expansion valve 24 is sent to the outdoor heat exchanger 123. Then, the intermediate pressure refrigerant decompressed in the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the liquid side end of the supercooling path 34 of the outdoor heat exchanger 123.
  • the intermediate-pressure refrigerant sent to the liquid side end of the supercooling path 34 is melted by the defrosting of the first heat exchange path 31 in the supercooling path 34 and flows down to the bottom of the outdoor heat exchanger 123. Water is heated, thereby preventing the drain water from refreezing due to the low temperature of the bottom plate 52 functioning as a drain pan (see point D ′ in FIGS. 24 and 25). Thereby, refreezing prevention of drain water in the supercooling path 34 of the outdoor heat exchanger 123 is performed.
  • the intermediate-pressure refrigerant that has passed through the supercooling path 34 is sent from the gas side end of the supercooling path 34 to the heat exchange path supply pipe 71 through the supercooling path-heat exchange path connecting pipe 35.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the first heat exchange path branch pipe 72a, the first branch pipe side heat exchange path selection valve 73a, and the first header communication pipe 65a. It is sent to the gas side end of the first heat exchange path 31 of the heat exchanger 123.
  • all the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 123 is sent to the gas side end of the first heat exchange path 31 without flowing into the refrigerant flow divider 64.
  • the intermediate-pressure refrigerant sent to the gas side end of the first heat exchange path 31 passes through the first heat exchange path 31 from the gas side end of the first heat exchange path 31 toward the liquid side end, Frost adhering to the first heat exchange path 31 of the outdoor heat exchanger 123 is melted (see point E in FIGS. 24 and 25). Thereby, defrosting of the 1st heat exchange path 31 of the outdoor heat exchanger 23 is performed.
  • the intermediate-pressure refrigerant that has passed through the first heat exchange path 31 is sent from the liquid side end of the first heat exchange path 31 to the refrigerant flow divider 64 through the first capillary tube 63a.
  • the first capillary tube 63a flows an intermediate-pressure refrigerant having a larger flow rate than that during the cooling operation or the heating operation. Therefore, the first capillary tube 63a has a pressure loss as compared with the case where the refrigerant flows during the cooling operation or the heating operation. It is greatly reduced to a pressure between the intermediate pressure in the refrigeration cycle (that is, the pressure at point E in FIGS. 24 and 25) and the low pressure (see point F in FIGS. 24 and 25).
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the second and third capillary tubes 63b, because the flow dividing pipe side selection valve 75 is closed.
  • the refrigerant is depressurized to a low pressure in the refrigeration cycle by passing through the second and third capillary tubes 63b and 63c (see point G in FIGS. 24 and 25).
  • the low-pressure refrigerant sent to the liquid side ends of the second and third heat exchange paths 32, 33 is second from the liquid side ends of the second and third heat exchange paths 32, 33 toward the gas side ends. Then, it passes through the third heat exchange paths 32 and 33 and evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 25 (see point A in FIGS. 24 and 25).
  • the low-pressure refrigerant evaporated in the second and third heat exchange paths 32 and 33 is supplied from the gas side ends of the second and third heat exchange paths 32 and 33 to the second and third header communication pipes 65b, 65c,
  • the air is again sucked into the compressor 21 through the second and third header side heat exchange path selection valves 74b and 74c, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22.
  • defrosting of the first heat exchange path 31 is started while continuing the indoor heating.
  • defrosting of the 1st heat exchange path 31 is performed until defrosting of the 1st heat exchange path 31 is completed (step S3).
  • the defrosting (step S4) of the second heat exchange path 32 is performed by switching the open / closed states of the selection valves 73a to 73c, 74a to 74c, 75 of the defrost flow path mechanism 126 in the same manner as the first heat exchange path 31. Done. Specifically, the second branch pipe side heat exchange path selection valve 73b is opened, the first and third branch pipe side heat exchange path selection valves 73a and 73c are closed, and the second header side heat exchange path selection valve 74b. Is closed, the first and third header side heat exchange path selection valves 74a and 74c are opened, and the branch pipe side selection valve 75 is switched to a closed state.
  • the second branch pipe side heat exchange path selection valve 73b is opened, A switching operation is performed in which the first branch pipe side heat exchange path selection valve 73a is closed, the first header side heat exchange path selection valve 74a is opened, and the second header side heat exchange path selection valve 74b is closed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the second heat exchange path branch pipe 72b of the defrost flow path mechanism 126.
  • the low-pressure refrigerant in the refrigeration cycle is compressed to the high pressure in the refrigeration cycle in the compressor 21 in the same manner as in the defrosting of the first heat exchange path 31, and in the indoor heat exchanger 41.
  • Heat is exchanged with room air to dissipate heat, and the expansion valve 24 reduces the pressure to an intermediate pressure in the refrigeration cycle and sends it to the outdoor heat exchanger 123.
  • the intermediate pressure refrigerant decompressed in the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the liquid side end of the supercooling path 34 of the outdoor heat exchanger 123.
  • the intermediate pressure refrigerant sent to the liquid side end of the supercooling path 34 is melted by the defrosting of the second heat exchange path 32 in the supercooling path 34 and flows down to the bottom of the outdoor heat exchanger 123.
  • the water is heated, thereby preventing the drain water from refreezing due to the low temperature of the bottom plate 52 functioning as a drain pan. Thereby, refreezing prevention of drain water in the supercooling path 34 of the outdoor heat exchanger 123 is performed.
  • the intermediate-pressure refrigerant that has passed through the supercooling path 34 is sent from the gas side end of the supercooling path 34 to the heat exchange path supply pipe 71 through the supercooling path-heat exchange path connecting pipe 35.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the second heat exchange path branch pipe 72b, the second branch pipe side heat exchange path selection valve 73b, and the second header communication pipe 65b. It is sent to the gas side end of the second heat exchange path 32 of the heat exchanger 123.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 123 is all sent to the gas side end of the second heat exchange path 32 without flowing into the refrigerant flow divider 64.
  • the intermediate-pressure refrigerant sent to the gas side end of the second heat exchange path 32 passes through the second heat exchange path 32 from the gas side end of the second heat exchange path 32 toward the liquid side end,
  • the frost attached to the second heat exchange path 32 of the outdoor heat exchanger 123 is melted.
  • defrosting of the 2nd heat exchange path 32 of the outdoor heat exchanger 123 is performed.
  • the intermediate-pressure refrigerant that has passed through the second heat exchange path 32 is sent from the liquid side end of the second heat exchange path 32 to the refrigerant flow divider 64 through the second capillary tube 63b.
  • the second capillary tube 63b has a flow rate of intermediate pressure refrigerant that is larger than that during cooling operation or heating operation.
  • the second capillary tube 63b has a pressure loss as compared with the case where the refrigerant flows during cooling operation or heating operation. It is greatly reduced to a pressure between the intermediate pressure and the low pressure in the refrigeration cycle.
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the first and third capillary tubes 63a, since the flow dividing pipe side selection valve 75 is closed. Branched to 63c and sent to the liquid side ends of the first and third heat exchange paths 31, 33. At this time, the refrigerant is depressurized to a low pressure in the refrigeration cycle by passing through the first and third capillary tubes 63a and 63c.
  • the low-pressure refrigerant sent to the liquid side ends of the first and third heat exchange paths 31 and 33 is first from the liquid side ends of the first and third heat exchange paths 31 and 33 toward the gas side end. And passes through the third heat exchange paths 31 and 33 and evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 25. Then, the low-pressure refrigerant evaporated in the first and third heat exchange paths 31 and 33 flows from the gas side ends of the first and third heat exchange paths 31 and 33 to the first and third header communication pipes 65a and 65c, The air is again sucked into the compressor 21 through the first and third header side heat exchange path selection valves 74 a and 74 c, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22. In this way, defrosting of the second heat exchange path 32 is started while continuing the indoor heating. And the defrosting of the 2nd heat exchange path 32 is performed until the defrosting of the 2nd heat exchange path 32 is completed (step S5).
  • the defrosting (step S6) of the third heat exchange path 33 is performed by opening and closing the selection valves 73a to 73c, 74a to 74c, and 75 of the defrost flow path mechanism 126, similarly to the first and second heat exchange paths 31 and 32. This is done by switching the state. Specifically, the third branch pipe side heat exchange path selection valve 73c is opened, the first and second branch pipe side heat exchange path selection valves 73a and 73b are closed, and the third header side heat exchange path selection valve 74c is closed. Is closed, the first and second header side heat exchange path selection valves 74a and 74b are opened, and the branch pipe side selection valve 75 is switched to a closed state.
  • the third branch pipe side heat exchange path selection valve 73c is opened, A switching operation is performed in which the second branch pipe side heat exchange path selection valve 73b is closed, the second header side heat exchange path selection valve 74b is opened, and the third header side heat exchange path selection valve 74c is closed.
  • the refrigerant flows into the heat exchange path supply pipe 71 and the third heat exchange path branch pipe 72c of the defrost flow path mechanism 126.
  • the low-pressure refrigerant in the refrigeration cycle is compressed to the high pressure in the refrigeration cycle in the compressor 21 in the same way as when the first and second heat exchange paths 31 and 32 are defrosted.
  • the heat exchanger 41 performs heat exchange with room air to dissipate heat, and the expansion valve 24 reduces the pressure to an intermediate pressure in the refrigeration cycle and sends the heat to the outdoor heat exchanger 123. Then, the intermediate pressure refrigerant decompressed in the expansion valve 24 is sent from the liquid refrigerant pipe 27 to the liquid side end of the supercooling path 34 of the outdoor heat exchanger 123.
  • the intermediate pressure refrigerant sent to the liquid side end of the supercooling path 34 is melted by the defrosting of the second heat exchange path 33 in the supercooling path 34 and flows down to the lowermost part of the outdoor heat exchanger 123.
  • the water is heated, thereby preventing the drain water from refreezing due to the low temperature of the bottom plate 52 functioning as a drain pan. Thereby, refreezing prevention of drain water in the supercooling path 34 of the outdoor heat exchanger 123 is performed.
  • the intermediate-pressure refrigerant that has passed through the supercooling path 34 is sent from the gas side end of the supercooling path 34 to the heat exchange path supply pipe 71 through the supercooling path-heat exchange path connecting pipe 35.
  • the intermediate-pressure refrigerant sent to the heat exchange path supply pipe 71 passes through the third heat exchange path branch pipe 72c, the third branch pipe side heat exchange path selection valve 73c, and the third header communication pipe 65c. It is sent to the gas side end of the third heat exchange path 33 of the heat exchanger 23.
  • the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 is all sent to the gas side end of the third heat exchange path 33 without flowing into the refrigerant flow divider 64.
  • the intermediate pressure refrigerant sent to the gas side end of the third heat exchange path 33 passes through the third heat exchange path 33 from the gas side end of the third heat exchange path 33 toward the liquid side end,
  • the frost attached to the third heat exchange path 33 of the outdoor heat exchanger 123 is melted. Thereby, defrosting of the 3rd heat exchange path 33 of the outdoor heat exchanger 123 is performed.
  • the intermediate-pressure refrigerant that has passed through the third heat exchange path 33 is sent from the liquid side end of the third heat exchange path 33 to the refrigerant flow divider 64 through the third capillary tube 63c.
  • an intermediate pressure refrigerant having a larger flow rate than in the cooling operation or the heating operation flows, so that the pressure loss is smaller than that in the case where the refrigerant flows during the cooling operation or the heating operation. It is greatly reduced to a pressure between the intermediate pressure and the low pressure in the refrigeration cycle.
  • the low-pressure refrigerant sent to the refrigerant flow divider 64 passes through the refrigerant flow divider 64 so that the first and second capillary tubes 63a, because the flow dividing pipe side selection valve 75 is closed. Branched to 63 b and sent to the liquid side ends of the first and second heat exchange paths 31 and 32.
  • the refrigerant is depressurized to a low pressure in the refrigeration cycle by passing through the first and second capillary tubes 63a and 63b.
  • the low-pressure refrigerant sent to the liquid side ends of the first and second heat exchange paths 31 and 32 is first from the liquid side ends of the first and second heat exchange paths 31 and 32 toward the gas side ends. Then, it passes through the second heat exchange paths 31 and 32 and evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 25.
  • the low-pressure refrigerant evaporated in the first and second heat exchange paths 31 and 32 flows from the gas side ends of the first and second heat exchange paths 31 and 32 to the first and second header communication pipes 65a and 65b, The air is again sucked into the compressor 21 through the first and second header side heat exchange path selection valves 74a and 74b, the header 66, the gas refrigerant pipe 28, and the four-way switching valve 22. In this way, defrosting of the third heat exchange path 33 is started while continuing the indoor heating. And the defrosting of the 3rd heat exchange path 33 is performed until the defrosting of the 2nd heat exchange path 33 is completed (step S7).
  • step S8 the heating operation is resumed (step S8).
  • Evaporative heating operation is performed.
  • the heating defrost operation is sequentially performed on the plurality of heat exchange paths 31 to 33, so that the entire outdoor heat exchanger 123 is defrosted while the indoor heating is continued.
  • the drain water that has melted by the defrosting of the heat exchange paths 31 to 33 and has flowed to the bottom of the outdoor heat exchanger 123 is heated.
  • the drain water is prevented from refreezing due to the low temperature of the bottom plate 52 functioning as a drain pan.
  • the entire flow rate of the refrigerant compressed in the compressor 21 is sent to the indoor heat exchanger 41 and used for heating (FIG. 24). And the process from point B to point C in FIG. 25), and then defrosting can be performed by the heat of the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 23 (see FIGS. 24 and 25). (See the process from point D to point E). For this reason, in the heating defrost operation of the air conditioner 101, the outdoor heat exchanger 123 can be defrosted with almost no reduction in heating capacity.
  • the defrosting flow path mechanism 126 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a. To 73c, header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75, but is not limited thereto. For example, as shown in FIGS.
  • the heat exchange path branch pipes 72a to 72c, the branch pipe side heat exchange path selection valves 73a to 73c, the header side heat exchange path selection valves 74a to 74c, and the header 66 Alternatively, a switching valve 82 that integrates the above may be used.
  • the switching valve 82 selects which of the header communication pipes 65a to 65c sends the refrigerant flowing through the heat exchange path supply pipe 71, and the header communication pipe through which the refrigerant flowing through the heat exchange path supply pipe 71 is sent.
  • the other header communication pipes are switching valves having a function of connecting to the gas refrigerant pipe 28 or selecting not to send the refrigerant to any of the header communication pipes 65a to 65c.
  • FIG. 26 is a schematic configuration diagram of the air-conditioning apparatus 101 according to the present modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 27 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 101 during the heating defrost operation of the present modification.
  • the heating operation similar to the above embodiment is performed. It can be carried out. Further, the same cooling operation as in the above embodiment can be performed in the operation state of the switching valve 82 as in the heating operation. Then, as shown in FIG. 27, it is selected which of the header communication pipes 65a to 65c the refrigerant flowing through the heat exchange path supply pipe 71 is sent to, and the header communication to which the refrigerant flowing through the heat exchange path supply pipe 71 is sent.
  • the heating defrost operation similar to that in the above embodiment or the first modification can be performed. And in the structure of this modification, compared with the structure of the said embodiment and the modification 1, the number of parts which comprise the flow-path mechanism 126 for defrost can be reduced.
  • the defrosting flow path mechanism 126 includes the heat exchange path supply pipe 71, the heat exchange path branch pipes 72a to 72c, and the branch pipe side heat exchange path selection valve 73a.
  • the header side heat exchange path selection valves 74a to 74c, and branch pipe side selection valve 75 are not limited thereto.
  • a switching valve 83 in which 74a to 74c, the branch pipe side selection valve 75, and the header 66 are integrated may be used.
  • the switching valve 83 selects whether the refrigerant flowing through the supercooling path-heat exchange path connecting pipe 35 flows to the refrigerant distribution pipe 64 or the header connecting pipes 65a to 65c, and the supercooling path
  • a header connecting pipe other than the header connecting pipe to which the refrigerant flowing through the heat exchange path connecting pipe 35 is sent is a switching valve having a function of connecting to the gas refrigerant pipe 28.
  • a rotary type switching valve is used as the switching valve 83.
  • the switching valve 83 is connected to the supercooling path-heat exchange path connecting pipe 35, the refrigerant branch pipe 64, the header connecting pipes 65 a to 65 c, and the gas refrigerant pipe 28.
  • switching is performed in place of the branch pipe side heat exchange path selection valves 73a to 73c, the header side heat exchange path selection valves 74a to 74c, and the branch pipe side selection valve 75 in the control block diagram of FIG.
  • a valve 83 is connected to the control unit 8.
  • FIG. 28 is a schematic configuration diagram of the air-conditioning apparatus 101 according to the present modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 29 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 101 during the heating defrost operation of the present modification.
  • the above embodiment is implemented.
  • the same heating operation can be performed.
  • the same cooling operation as that in the above embodiment can be performed in the operation state of the switching valve 83 similar to that in the heating operation.
  • the refrigerant flowing through the supercooling path-heat exchange path connecting pipe 35 is selected to be sent to any of the header connecting pipes 65a to 65c, and the refrigerant flowing through the liquid refrigerant pipe 27 is sent.
  • the heating defrost operation similar to that in the above embodiment or the first modification can be performed. And in the structure of this modification, compared with the structure of the said embodiment and the modification 1, and the structure of the modification 2, the number of parts which comprise the flow-path mechanism 126 for defrost can be reduced.
  • the defrost flow path mechanism 126 may be configured so as to obtain the above flow.
  • the heat exchange path supply pipe 71 is connected between the expansion valve 24 of the liquid refrigerant pipe 27 and the liquid side end of the supercooling path 34.
  • the electromagnetic valve 76 may be provided in the heat exchange path supply pipe 71 so as to be branched from the position.
  • the solenoid valve together with the branch pipe side heat exchange path selection valves 73a to 73c, the header side heat exchange path selection valves 74a to 74c, and the branch pipe side selection valve 75 are provided.
  • 76 is connected to the control unit 8.
  • FIG. 30 is a schematic configuration diagram of the air-conditioning apparatus 101 according to the present modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 31 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 101 during the heating defrost operation of the present modification.
  • the heating operation similar to that in the above embodiment can be performed by opening the branch pipe side selection valve 75 and closing the electromagnetic valve 76. Further, in the operation state of the branch pipe side selection valve 75 and the electromagnetic valve 76 similar to those in the heating operation, the same cooling operation as in the above embodiment can be performed. And as shown in FIG. 31, the heating defrost similar to 1st Embodiment is made without passing a refrigerant
  • the defrosting channel mechanism 126 passes the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 123 through the supercooling path 34, and then the refrigerant distributor.
  • the flow is configured to be sent to the gas side end of a heat exchange path arbitrarily selected from the plurality of heat exchange paths 31 to 33 without flowing into the heat exchange path.
  • the same refrigerant as in the heating defrost operation of the first embodiment may be configured so as to obtain the above flow.
  • FIGS. 32 and 33 in the air conditioner 101 of the second modification, the heat exchange path supply pipe 71 is connected between the expansion valve 24 of the liquid refrigerant pipe 27 and the liquid side end of the supercooling path 34. You may make it branch from the position of.
  • a switching valve 82 is connected to the control unit 8.
  • FIG. 32 is a schematic configuration diagram of the air-conditioning apparatus 101 according to the present modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 33 is a diagram showing a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 101 during the heating defrost operation of the present modification.
  • the heating operation similar to the above embodiment is performed. It can be carried out. Further, the same cooling operation as in the above embodiment can be performed in the operation state of the switching valve 82 as in the heating operation. Then, as shown in FIG.
  • the branch pipe side selection valve 75 is closed, the refrigerant flowing through the heat exchange path supply pipe 71 is selected to be sent to any one of the header communication pipes 65a to 65c, and the heat exchange is performed.
  • the switching valve 82 By operating the switching valve 82 to connect the header communication pipe other than the header communication pipe through which the refrigerant flowing through the path supply pipe 71 is connected to the gas refrigerant pipe 28, the refrigerant does not pass through the supercooling path 34.
  • a heating defrost operation similar to that of the first embodiment can be performed.
  • the defrosting flow path mechanism 126 passes the refrigerant sent from the indoor heat exchanger 41 to the outdoor heat exchanger 123 through the supercooling path 34, and then the refrigerant distributor.
  • the flow is configured to be sent to the gas side end of a heat exchange path arbitrarily selected from the plurality of heat exchange paths 31 to 33 without flowing into the heat exchange path.
  • the same refrigerant as in the heating defrost operation of the first embodiment may be configured so as to obtain the above flow.
  • FIGS. 34 and 35 in the air conditioner 101 according to the third modification, the liquid refrigerant pipe 27 is connected to the switching valve 83 instead of the supercooling path-heat exchange path connecting pipe 35. Also good.
  • a switching valve 83 is connected to the control unit 8.
  • FIG. 34 is a schematic configuration diagram of the air-conditioning apparatus 101 according to the present modification, and is a diagram illustrating the flow of refrigerant in the air-conditioning apparatus 101 during the heating operation.
  • FIG. 35 is a diagram illustrating a refrigerant flow (when defrosting the first heat exchange path 31) in the air-conditioning apparatus 101 during the heating defrost operation of the present modification.
  • the above embodiment is implemented.
  • the same heating operation can be performed.
  • the same cooling operation as that in the above embodiment can be performed in the operation state of the switching valve 83 similar to that in the heating operation.
  • it is selected which of the header communication pipes 65a to 65c the refrigerant flowing through the liquid refrigerant pipe 27 is sent to, and a header other than the header communication pipe to which the refrigerant flowing through the liquid refrigerant pipe 27 is sent.
  • the defrost flow path mechanisms 26, 126 are configured to include a heat exchange path supply pipe 71 and heat exchange path branch pipes 72a to 72c.
  • a configuration having a header 68 may be employed in place of the heat exchange path supply pipe 71 and the heat exchange path branch pipes 72a to 72c.
  • FIG. 36 shows an example in which the defrost flow path mechanism 26 having the header 68 is adopted in the configuration of the first embodiment. However, in the configuration of the second embodiment, as shown in FIG.
  • the defrosting flow path mechanism 126 in which the header 68 is directly connected to the supercooling path-heat exchange path connecting pipe 35 may be employed.
  • a configuration in which a plurality of indoor units are connected to the outdoor unit a configuration in which one indoor unit is connected to the plurality of outdoor units, or a configuration in which a plurality of indoor units are connected to the plurality of outdoor units may be employed. .
  • the said embodiment and its modification although it was an air conditioning apparatus which can switch between cooling and heating with a four-way switching valve, it is not limited to this.
  • a configuration dedicated to heating that is, a configuration in which an indoor heat exchanger is always used as a radiator without a four-way switching valve
  • a configuration dedicated to heating that is, a configuration in which an indoor heat exchanger is always used as a radiator without a four-way switching valve
  • the outdoor unit of the type which blows off outdoor air to a horizontal direction is employ
  • adopted it is not limited to this.
  • other types of outdoor units such as an outdoor unit that blows outdoor air upward by installing an outdoor fan above the outdoor heat exchanger may be used.
  • cross fin type fin and tube type heat exchanger adopted as an outdoor heat exchanger, it is not limited to this.
  • another type of heat exchanger may be used such as a laminated heat exchanger using corrugated fins.
  • the number of heat exchange paths constituting the outdoor heat exchanger is not limited to three, and may be four or more.
  • the present invention is widely applicable to an air conditioner capable of performing a heating operation.

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Abstract

Un climatiseur (1) comprend un mécanisme de dégivrage de trajet d'écoulement (26) utilisé pour le dégivrage. Le climatiseur (1) réalise une opération de chauffage/dégivrage, le réfrigérant transmis d'un échangeur de chaleur d'intérieur (41) vers un échangeur de chaleur d'extérieur (23) étant évaporé alors qu'un trajet d'échange de chaleur donné est dégivré au moyen du mécanisme de dégivrage de trajet d'écoulement (26). Dans l'opération de chauffage/dégivrage, premièrement, au moyen du mécanisme de dégivrage de trajet d'écoulement (26), le réfrigérant transmis de l'échangeur de chaleur d'intérieur (41) vers l'échangeur de chaleur d'extérieur (23) circule dans un trajet d'échange de chaleur donné de l'extrémité du côté de gaz vers l'extrémité du côté de liquide du trajet d'échange de chaleur donné sans être introduit dans un diviseur d'écoulement de réfrigérant (64). Ensuite, le réfrigérant ayant traversé le trajet d'échange de chaleur donné traverse le diviseur d'écoulement de réfrigérant (64) et circule de l'extrémité du côté de liquide vers l'extrémité du côté de gaz dans un autre trajet d'échange de chaleur que le trajet d'échange de chaleur donné.
PCT/JP2012/064098 2011-06-28 2012-05-31 Climatiseur WO2013001976A1 (fr)

Priority Applications (4)

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US14/126,684 US20140116078A1 (en) 2011-06-28 2012-05-31 Air conditioning apparatus
KR1020147001871A KR20140026630A (ko) 2011-06-28 2012-05-31 공기 조화 장치
CN201280032321.9A CN103635754A (zh) 2011-06-28 2012-05-31 空调装置
EP12803614.2A EP2741021A4 (fr) 2011-06-28 2012-05-31 Climatiseur

Applications Claiming Priority (2)

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JP2011-142599 2011-06-28
JP2011142599A JP2013011364A (ja) 2011-06-28 2011-06-28 空気調和装置

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US (1) US20140116078A1 (fr)
EP (1) EP2741021A4 (fr)
JP (1) JP2013011364A (fr)
KR (1) KR20140026630A (fr)
CN (1) CN103635754A (fr)
WO (1) WO2013001976A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103954087A (zh) * 2014-05-21 2014-07-30 珠海格力电器股份有限公司 除霜装置、热泵机以及除霜装置的除霜方法
WO2015087229A1 (fr) * 2013-12-09 2015-06-18 BSH Hausgeräte GmbH Condensateur, procédé de fabrication d'un condensateur et appareil de refroidissement équipé du condenseur
WO2017094148A1 (fr) 2015-12-02 2017-06-08 三菱電機株式会社 Dispositif de climatisation
US20220018581A1 (en) * 2020-07-20 2022-01-20 Lg Electronics Inc. Multi-air conditioner for heating and co0ling

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JP2013011364A (ja) 2013-01-17
US20140116078A1 (en) 2014-05-01
EP2741021A1 (fr) 2014-06-11
EP2741021A4 (fr) 2014-07-09
KR20140026630A (ko) 2014-03-05
CN103635754A (zh) 2014-03-12

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