US20230126980A1 - Refrigeration Cycle Apparatus - Google Patents

Refrigeration Cycle Apparatus Download PDF

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Publication number
US20230126980A1
US20230126980A1 US17/918,189 US202017918189A US2023126980A1 US 20230126980 A1 US20230126980 A1 US 20230126980A1 US 202017918189 A US202017918189 A US 202017918189A US 2023126980 A1 US2023126980 A1 US 2023126980A1
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United States
Prior art keywords
heat exchange
exchange unit
refrigerant
region
outflow passage
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Abandoned
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US17/918,189
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English (en)
Inventor
Kenta MURATA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of US20230126980A1 publication Critical patent/US20230126980A1/en
Abandoned legal-status Critical Current

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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • 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
    • F28D1/0435—Combination of units extending one behind 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
    • F28D1/0408—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
    • F28D1/0452—Combination of units extending one behind the other with units extending one beside or one above the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • Mixed refrigerants have been taken into consideration as refrigerants each having a low global warming potential (GWP).
  • GWP global warming potential
  • a zeotropic mixed refrigerant has been used in which refrigerants having different boiling points are mixed.
  • the temperature of the refrigerant is changed in accordance with a degree of dryness of the refrigerant in a gas-liquid two-phase region. That is, a temperature gradient is generated. In this temperature gradient, the temperature of the refrigerant is decreased as the degree of dryness of the refrigerant is smaller.
  • Japanese Patent Laying-Open No. 7-269985 discloses a heat exchanger of an air conditioner using a zeotropic mixed refrigerant.
  • flow passages of heat exchange pipes are located in a plurality of rows arranged on the upstream side and downstream side of air.
  • a refrigerant outlet in the upstream side row and a refrigerant inlet in the downstream side row are located side by side in a direction in which air flows.
  • the present disclosure has been made to solve the above-described problem and has an object to provide a refrigeration cycle apparatus so as to suppress a decrease in heat exchange amount while using a zeotropic mixed refrigerant having a low global warming potential.
  • a refrigeration cycle apparatus of the present disclosure comprises a refrigerant circuit and a refrigerant.
  • the refrigerant circuit comprises a compressor, a condenser, a pressure reducing valve, and an evaporator.
  • the refrigerant circulates through the refrigerant circuit in order of a compressor, a condenser, a pressure reducing valve, and an evaporator.
  • the refrigerant is a zeotropic mixed refrigerant.
  • At least one of the condenser and the evaporator comprises a first heat exchange unit located windward and a second heat exchange unit located leeward in a first direction in which air flows.
  • Each of the first heat exchange unit and the second heat exchange unit comprises an inflow passage and an outflow passage for the refrigerant that are located in a plurality of stages arranged in a second direction crossing the first direction.
  • the refrigerant flows out from the outflow passage of the second heat exchange unit into the inflow passage of the first heat exchange unit.
  • the outflow passage of the second heat exchange unit is located in the same stage as the outflow passage of the first heat exchange unit in the second direction.
  • the refrigerant is a zeotropic mixed refrigerant.
  • the outflow passage of the second heat exchanger is located in the same stage as the outflow passage of the first heat exchange unit in the second direction. Therefore, a heat exchange amount can be suppressed from being decreased while using the zeotropic mixed refrigerant having a low global warming potential.
  • FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to a first embodiment.
  • FIG. 2 is a perspective view schematically showing a configuration of a heat exchanger of the refrigeration cycle apparatus according to the first embodiment.
  • FIG. 3 is a cross sectional view schematically showing the configuration of the heat exchanger of the refrigeration cycle apparatus according to the first embodiment.
  • FIG. 4 is a graph showing respective temperatures of refrigerant and air in the heat exchanger of the refrigeration cycle apparatus according to the first embodiment.
  • FIG. 5 is a cross sectional view schematically showing a configuration of a heat exchanger according to a comparative example for the first embodiment.
  • FIG. 6 is a graph showing respective temperatures of refrigerant and air in the heat exchanger according to the comparative example for the first embodiment.
  • FIG. 7 is a perspective view schematically showing a configuration of a heat exchanger of a refrigeration cycle apparatus according to a second embodiment.
  • FIG. 8 is a cross sectional view schematically showing the configuration of the heat exchanger of the refrigeration cycle apparatus according to the second embodiment.
  • FIG. 9 is a cross sectional view schematically showing a configuration of a heat exchanger according to a comparative example for the second embodiment.
  • FIG. 10 is a cross sectional view schematically showing a configuration of a heat exchanger in a modification of the refrigeration cycle apparatus according to the second embodiment.
  • FIG. 11 is a cross sectional view schematically showing a configuration of a heat exchanger of a refrigeration cycle apparatus according to a third embodiment.
  • FIG. 12 is a diagram showing positions of a heat exchanger and a fan of a refrigeration cycle apparatus according to a fourth embodiment.
  • FIG. 13 is a cross sectional view schematically showing a configuration of a heat exchanger of a refrigeration cycle apparatus according to a fifth embodiment.
  • FIG. 14 is a cross sectional view for illustrating thermal loss in a heat exchanger according to a comparative example for the fifth embodiment.
  • Refrigeration cycle apparatus 100 includes a refrigerant circuit RC, a refrigerant, a controller CD, and blower apparatuses 6 , 7 .
  • Refrigerant circuit RC includes a compressor 1 , a four-way valve 2 , an outdoor heat exchanger 3 , a pressure reducing valve 4 , and an indoor heat exchanger 5 .
  • Compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , pressure reducing valve 4 , and indoor heat exchanger 5 are connected to one another by tubes.
  • Refrigerant circuit RC is configured to circulate the refrigerant.
  • Refrigerant circuit RC is configured to perform a refrigeration cycle in which the refrigerant circulates with the phase of the refrigerant being changed.
  • Compressor 1 four-way valve 2 , outdoor heat exchanger 3 , pressure reducing valve 4 , controller CD, and blower apparatus 6 are accommodated in outdoor unit 101 .
  • Indoor heat exchanger 5 and blower apparatus 7 are accommodated in indoor unit 102 .
  • Refrigerant circuit RC is configured to circulate the refrigerant in the order of compressor 1 , four-way valve 2 , outdoor heat exchanger (condenser) 3 , pressure reducing valve 4 , indoor heat exchanger (evaporator) 5 , and four-way valve 2 during a cooling operation. Further, refrigerant circuit RC is configured to circulate the refrigerant in the order of compressor 1 , four-way valve 2 , indoor heat exchanger (condenser) 5 , pressure reducing valve 4 , outdoor heat exchanger (evaporator) 3 , and four-way valve 2 during a heating operation.
  • the refrigerant flows through refrigerant circuit RC in the order of compressor 1 , the condenser, pressure reducing valve 4 , and the evaporator.
  • the refrigerant is a zeotropic mixed refrigerant. That is, among mixed refrigerants, the refrigerant is a zeotropic mixed refrigerant in which refrigerants having different boiling points are mixed.
  • the refrigerant is a zeotropic mixed refrigerant having a temperature gradient in which the temperature of the refrigerant is changed in accordance with a degree of dryness of the refrigerant in a gas-liquid two-phase region.
  • the refrigerant is a zeotropic mixed refrigerant having a temperature gradient in which the temperature of the refrigerant is decreased as the degree of dryness of the refrigerant is smaller.
  • the refrigerant include R407C, R454A, and the like.
  • Controller CD is configured to control each apparatus and the like of refrigeration cycle apparatus 100 by performing calculation, instruction and the like. Controller CD is electrically connected to compressor 1 , four-way valve 2 , pressure reducing valve 4 , blower apparatuses 6 , 7 , and the like, and is configured to control operations of them.
  • Compressor 1 is configured to compress the refrigerant. Compressor 1 is configured to compress and discharge the suctioned refrigerant. Compressor 1 may be variable in capacity. Compressor 1 may be variable in capacity by adjusting the rotation speed of compressor 1 based on an instruction from controller CD.
  • Four-way valve 2 is configured to switch flow of the refrigerant so as to cause the refrigerant compressed by compressor 1 to flow to outdoor heat exchanger 3 or indoor heat exchanger 5 .
  • Four-way valve 2 is configured to cause the refrigerant discharged from compressor 1 to flow to outdoor heat exchanger (condenser) 3 during the cooling operation.
  • Four-way valve 2 is configured to cause the refrigerant discharged from compressor 1 to flow to indoor heat exchanger (evaporator) 5 during the heating operation.
  • Outdoor heat exchanger 3 is configured to exchange heat between the refrigerant flowing inside outdoor heat exchanger 3 and the air flowing outside outdoor heat exchanger 3 .
  • Outdoor heat exchanger 3 is configured to function as a condenser to condense the refrigerant during the cooling operation, and function as an evaporator to evaporate the refrigerant during the heating operation.
  • Outdoor heat exchanger 3 is a fin-and-tube type heat exchanger having a plurality of fins and a heat transfer tube extending through the plurality of fins.
  • Pressure reducing valve 4 is configured to expand the refrigerant condensed by the condenser so as to reduce the pressure of the refrigerant.
  • Pressure reducing valve 4 is configured to reduce the pressure of the refrigerant condensed by outdoor heat exchanger (condenser) 3 during the cooling operation, and to reduce the pressure of the refrigerant condensed by indoor heat exchanger (evaporator) 5 during the heating operation.
  • Pressure reducing valve 4 is, for example, an electromagnetic valve.
  • Indoor heat exchanger 5 is configured to exchange heat between the refrigerant flowing inside indoor heat exchanger 5 and the air flowing outside indoor heat exchanger 5 .
  • Indoor heat exchanger 5 is configured to function as an evaporator to evaporate the refrigerant during the cooling operation, and function as a condenser to condense the refrigerant during the heating operation.
  • Indoor heat exchanger 5 is a fin-and-tube type heat exchanger having a plurality of fins and a heat transfer tube extending through the plurality of fins.
  • Blower apparatus 6 is configured to blow outdoor air to outdoor heat exchanger 3 . That is, blower apparatus 6 is configured to supply air to outdoor heat exchanger 3 . Blower apparatus 6 may be configured to adjust an amount of air flowing around outdoor heat exchanger 3 by adjusting the rotation speed of blower apparatus 6 based on an instruction from controller CD, thereby adjusting a heat exchange amount between the refrigerant and the air.
  • Blower apparatus 7 is configured to blow indoor air to indoor heat exchanger 5 . That is, blower apparatus 7 is configured to supply air to indoor heat exchanger 5 . Blower apparatus 7 may be configured to adjust an amount of air flowing around indoor heat exchanger 5 by adjusting the rotation speed of blower apparatus 7 based on an instruction from controller CD, thereby adjusting a heat exchange amount between the refrigerant and the air.
  • FIG. 1 Solid arrows in FIG. 1 indicate flow of the refrigerant during the cooling operation, and broken arrows in FIG. 1 indicate flow of the refrigerant during the heating operation.
  • Refrigeration cycle apparatus 100 can selectively perform the cooling operation and the heating operation.
  • the refrigerant circulates in refrigerant circuit RC in the order of compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , pressure reducing valve 4 , indoor heat exchanger 5 , and four-way valve 2 .
  • outdoor heat exchanger 3 functions as a condenser. Heat exchange is performed between the refrigerant flowing through outdoor heat exchanger 3 and the air blown by blower apparatus 6 .
  • indoor heat exchanger 5 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through indoor heat exchanger 5 and the air blown by blower apparatus 7 .
  • the refrigerant circulates in refrigerant circuit RC in the order of compressor 1 , four-way valve 2 , indoor heat exchanger 5 , pressure reducing valve 4 , outdoor heat exchanger 3 , and four-way valve 2 .
  • indoor heat exchanger 5 functions as a condenser. Heat exchange is performed between the refrigerant flowing through indoor heat exchanger 5 and the air blown by blower apparatus 7 .
  • outdoor heat exchanger 3 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through outdoor heat exchanger 3 and the air blown by blower apparatus 6 .
  • indoor heat exchanger 5 functions as a condenser or an evaporator in the same manner as outdoor heat exchanger 3 , and may have the same configuration as that of outdoor heat exchanger 3 .
  • at least one of outdoor heat exchanger 3 and indoor heat exchanger 5 functioning as a condenser or an evaporator may have the following configuration.
  • Outdoor heat exchanger 3 has a plurality of fins F and a heat transfer tube P extending through the plurality of fins F.
  • Heat transfer tube P includes a plurality of heat transfer portions P 1 and a plurality of connection portions P 2 .
  • the plurality of heat transfer portions P 1 are portions extending through the plurality of fins F.
  • the plurality of heat transfer portions P 1 are formed in the form of straight lines.
  • the plurality of connection portions P 2 are portions that connect heat transfer portions P 1 to each other outside the plurality of fins F.
  • Each of the plurality of connection portions P 2 is formed to have a U-shape.
  • Outdoor heat exchanger 3 has a first heat exchange unit C 1 and a second heat exchange unit C 2 .
  • First heat exchange unit C 1 is located windward in a first direction D 1 in which air flows.
  • First heat exchange unit C 1 is located in a first row in first direction D 1 .
  • Second heat exchange unit C 2 is located leeward in first direction D 1 .
  • Second heat exchange unit C 2 is located in a second row in first direction D 1 .
  • Each of first heat exchange unit C 1 and second heat exchange unit C 2 has an inflow passage IF and an outflow passage OF for the refrigerant that are located in a plurality of stages arranged in a second direction D 2 crossing first direction D 1 .
  • Outflow passage OF of second heat exchange unit C 2 is located in the same stage as outflow passage OF of first heat exchange unit C 1 in second direction D 2 .
  • Outflow passage OF of second heat exchange unit C 2 is located to overlap with outflow passage OF of first heat exchange unit C 1 in first direction D 1 .
  • outflow passage OF of second heat exchange unit C 2 is located to overlap with outflow passage OF of first heat exchange unit C 1 when viewed in first direction D 1 .
  • inflow passage IF of second heat exchange unit C 2 is located in the same stage as inflow passage IF of first heat exchange unit C 1 in second direction D 2 .
  • Inflow passage IF of second heat exchange unit C 2 is located to overlap with inflow passage IF of first heat exchange unit C 1 in first direction D 1 .
  • First direction D 1 may be orthogonal to second direction D 2 .
  • First direction D 1 may be a horizontal direction.
  • Second direction D 2 may be an upward/downward direction (vertical direction).
  • Third direction D 3 is a direction in which heat transfer portions P 1 extend in the form of straight lines. Third direction D 3 may be orthogonal to first direction D 1 and second direction D 2 .
  • the plurality of heat transfer portions P 1 are located in the plurality of stages arranged in second direction D 2 .
  • the plurality of heat transfer portions P 1 are located in four stages. That is, the plurality of heat transfer portions P 1 are located in a first stage S 1 to a fourth stage S 4 .
  • inflow passage IF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • Outflow passage OF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in fourth stage S 4 .
  • first heat exchange unit C 1 and second heat exchange unit C 2 the plurality of heat transfer portions P 1 are connected by connection portions P 2 as follows.
  • Heat transfer portion P 1 of first stage S 1 is connected to heat transfer portion P 1 of second stage S 2 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of second stage S 2 is connected to heat transfer portion P 1 of third stage S 3 on the front side by connection portion P 2 .
  • Heat transfer portion P 1 of third stage S 3 is connected to heat transfer portion P 1 of fourth stage S 4 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 is connected to heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 on the front side by connection portion P 2 .
  • the refrigerant flows into second heat exchange unit C 2 via inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 , to outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 .
  • the refrigerant flows from outflow passage OF of second heat exchange unit C 2 to inflow passage IF of first heat exchange unit C 1 .
  • the refrigerant flows into first heat exchange unit C 1 via inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 , to outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of first heat exchange unit C 1 . Thereafter, the refrigerant flows out from first heat exchange unit C 1 .
  • the refrigerant flows through first heat exchange unit C 1 and second heat exchange unit C 2 in the form of an inversed N-shape.
  • the refrigerant flows from second heat exchange unit C 2 toward first heat exchange unit C 1 .
  • the air flows from first heat exchange unit C 1 toward second heat exchange unit C 2 . Therefore, the flow of the refrigerant flowing through second heat exchange unit C 2 and first heat exchange unit C 1 is a counter flow with respect to the flow of the air flowing through first heat exchange unit C 1 and second heat exchange unit C 2 .
  • Temperatures of the refrigerant and the air in outdoor heat exchanger 3 will be described with reference to FIGS. 3 and 4 .
  • Each of solid arrows in FIG. 4 indicates a temperature of the refrigerant
  • each of broken arrows in FIG. 4 indicates a temperature of the air.
  • each of two-headed arrows indicate a temperature difference between the refrigerant and the air.
  • FIG. 4 ( a ) shows the temperatures of the refrigerant and the air at heat transfer portion P 1 of first stage S 1 of each of the first heat exchange unit and the second heat exchange unit.
  • FIG. 4 ( b ) shows the temperatures of the refrigerant and the air at heat transfer portion P 1 of fourth stage S 4 of each of the first heat exchange unit and the second heat exchange unit.
  • a temperature difference ⁇ T 1 between the refrigerant and the air at heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 and a temperature difference ⁇ T 2 between the refrigerant and the air at heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 are secured.
  • a temperature difference ⁇ T 3 between the refrigerant and the air at heat transfer portion P 1 of first stage S 1 in first heat exchange unit C 1 and a temperature difference ⁇ T 4 between the refrigerant and the air at heat transfer portion P 1 of fourth stage S 4 in second heat exchange unit C 2 are secured. It should be noted that a temperature Ta of suction air is constant.
  • FIG. 6 ( a ) shows temperatures of the refrigerant and the air at heat transfer portion P 1 of first stage S 1 of each of first heat exchange unit C 1 and second heat exchange unit C 2 .
  • FIG. 6 ( b ) shows temperatures of the refrigerant and the air at heat transfer portion P 1 of fourth stage S 4 of each of first heat exchange unit C 1 and second heat exchange unit C 2 .
  • inflow passage IF of second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • Outflow passage OF of second heat exchange unit C 2 is heat transfer portion P 1 located in fourth stage S 4 .
  • Inflow passage IF of first heat exchange unit C 1 is heat transfer portion P 1 located in fourth stage S 4 .
  • Outflow passage OF of first heat exchange unit C 1 is heat transfer portion P 1 located in first stage S 1 .
  • the refrigerant flows into second heat exchange unit C 2 via inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 , to outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 .
  • the refrigerant flows into first heat exchange unit C 1 via inflow passage IF, which is heat transfer portion P 1 of the fourth stage of first heat exchange unit C 1 .
  • first heat exchange unit C 1 the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of fourth stage S 4 , to outflow passage OF, which is heat transfer portion P 1 of first stage S 1 .
  • the refrigerant flows through first heat exchange unit C 1 and second heat exchange unit C 2 in the form of a U-shape.
  • a temperature difference ⁇ T 4 between the refrigerant and the air is small at heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 . This is due to the following factor.
  • a temperature difference ⁇ T 3 between the refrigerant and the air is large, so that a heat exchange amount is large. Accordingly, the temperature of the blown air from first heat exchange unit C 1 is increased.
  • the temperature of the blown air from first heat exchange unit C 1 is the temperature of the suctioned air in second heat exchange unit C 2
  • a temperature difference is small between the temperature of the suctioned air in second heat exchange unit C 2 and the refrigerant.
  • the heat exchange amount is decreased in outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 .
  • outflow passage OF of second heat exchange unit C 2 is located in the same stage as outflow passage OF of first heat exchange unit C 1 in second direction D 2 . Therefore, temperature difference ⁇ T 4 between the refrigerant and the air is small in outflow passage OF of second heat exchange unit C 2 . This is due to the following factor. At heat transfer portion P 1 of fourth stage S 4 of first heat exchange unit C 1 , temperature difference ⁇ T 3 between the refrigerant and the air is small, so that a heat exchange amount is small. Therefore, the temperature of the blown air from first heat exchange unit C 1 is suppressed from being increased.
  • the temperature difference is large between the temperature of the suctioned air in second heat exchange unit C 2 and the refrigerant. Therefore, temperature difference ⁇ T between the refrigerant and the air is secured. As a result, the heat exchange amount in outflow passage OF of second heat exchange unit C 2 is suppressed from being decreased. This leads to improved heat exchanger performance in outflow passage OF of second heat exchange unit C 2 .
  • the refrigerant is a zeotropic mixed refrigerant. Therefore, according to refrigeration cycle apparatus 100 of the first embodiment, the heat exchange amount can be suppressed from being decreased while using the zeotropic mixed refrigerant having a low global warming potential.
  • a refrigeration cycle apparatus 100 according to a second embodiment has the same configuration, functions, and effects as those of refrigeration cycle apparatus 100 according to the first embodiment unless otherwise stated particularly.
  • outdoor heat exchanger 3 has two paths through which the refrigerant flows. That is, outdoor heat exchanger 3 has a first path PA and a second path PB. It should be noted that outdoor heat exchanger 3 may have two or more paths.
  • Outdoor heat exchanger 3 has a first heat exchange region HF 1 and a second heat exchange region HF 2 located in second direction D 2 .
  • First heat exchange region HF 1 and second heat exchange region HF 2 are located adjacent to each other in second direction D 2 .
  • First heat exchange region HF 1 has a first path PA.
  • Second heat exchange region HF 2 has a second path PB.
  • First path PA and second path PB are configured such that the refrigerant flowing through first path PA and the refrigerant flowing through second path PB flow in parallel with each other.
  • First path PA and second path PB are located line-symmetrically with respect to each other in second direction D 2 .
  • first heat exchange region HF 1 and second heat exchange region HF 2 has an inflow passage IF and an outflow passage OF of each of first heat exchange unit C 1 and second heat exchange unit C 2 .
  • outflow passage OF of second heat exchange unit C 2 is located in the same stage as outflow passage OF of first heat exchange unit C 1 in second direction D 2 .
  • Each of first heat exchange region HF 1 and second heat exchange region HF 2 has first heat exchange unit C 1 and second heat exchange unit C 2 .
  • the plurality of heat transfer portions P 1 are located in first stage S 1 to fourth stage S 4 .
  • inflow passage IF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • Outflow passage OF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in fourth stage S 4 .
  • inflow passage IF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in fourth stage S 4 .
  • Outflow passage OF of each of first heat exchange unit C 1 and second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • first heat exchange region HF 1 in each of first heat exchange unit C 1 and second heat exchange unit C 2 , the plurality of heat transfer portions P 1 are connected by connection portions P 2 as follows.
  • Heat transfer portion P 1 of first stage S 1 is connected to heat transfer portion P 1 of second stage S 2 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of second stage S 2 is connected to heat transfer portion P 1 of third stage S 3 on the front side by connection portion P 2 .
  • Heat transfer portion P 1 of third stage S 3 is connected to heat transfer portion P 1 of fourth stage S 4 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 is connected to heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 on the front side by connection portion P 2 .
  • connection portions P 2 In second heat exchange region HF 2 , in each of first heat exchange unit C 1 and second heat exchange unit C 2 , the plurality of heat transfer portions P 1 are connected by connection portions P 2 as follows.
  • Heat transfer portion P 1 of fourth stage S 4 is connected to heat transfer portion P 1 of third stage S 3 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of third stage S 3 is connected to heat transfer portion P 1 of second stage S 2 on the front side by connection portion P 2 .
  • Heat transfer portion P 1 of second stage S 2 is connected to heat transfer portion P 1 of first stage S 1 on the back side by connection portion P 2 .
  • Heat transfer portion P 1 of fourth stage S 4 of first heat exchange unit C 1 is connected to heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 on the front side by connection portion P 2 .
  • inflow passages IF of first heat exchange unit C 1 in first heat exchange region HF 1 and second heat exchange region HF 2 are located adjacent to each other in second direction D 2 .
  • inflow passages IF of first heat exchange unit C 1 in first heat exchange region HF 1 and second heat exchange region HF 2 are located in stages adjacent to each other.
  • first heat exchange region HF 1 the refrigerant flows into second heat exchange unit C 2 via inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of second heat exchange unit C 2 , to outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 .
  • the refrigerant flows from outflow passage OF of second heat exchange unit C 2 to inflow passage IF of first heat exchange unit C 1 .
  • the refrigerant flows into first heat exchange unit C 1 via inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of first stage S 1 of first heat exchange unit C 1 , to outflow passage OF, which is heat transfer portion P 1 of fourth stage S 4 of first heat exchange unit C 1 . Thereafter, the refrigerant flows out from first heat exchange unit C 1 .
  • the refrigerant flows through first heat exchange unit C 1 and second heat exchange unit C 2 in the form of an inversed N-shape.
  • the refrigerant flows into second heat exchange unit C 2 via inflow passage IF, which is heat transfer portion P 1 of fourth stage S 4 of second heat exchange unit C 2 .
  • the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of fourth stage S 4 , to outflow passage OF, which is heat transfer portion P 1 of first stage S 1 .
  • the refrigerant flows from outflow passage OF of second heat exchange unit C 2 to inflow passage IF of first heat exchange unit C 1 .
  • the refrigerant flows into first heat exchange unit C 1 via inflow passage IF, which is heat transfer portion P 1 of fourth stage S 4 of first heat exchange unit C 1 .
  • first heat exchange unit C 1 the refrigerant flows from inflow passage IF, which is heat transfer portion P 1 of fourth stage S 4 , to outflow passage OF, which is heat transfer portion P 1 of first stage S 1 . Thereafter, the refrigerant flows out from first heat exchange unit C 1 .
  • the refrigerant flows through first heat exchange unit C 1 and second heat exchange unit C 2 in the form of an N-shape.
  • first heat exchange region HF 1 and second heat exchange region HF 2 the refrigerant flows from second heat exchange unit C 2 toward first heat exchange unit C 1 .
  • the air flows from first heat exchange unit C 1 toward second heat exchange unit C 2 . Therefore, the flow of the refrigerant flowing through second heat exchange unit C 2 and first heat exchange unit C 1 is a counter flow with respect to the flow of the air flowing through first heat exchange unit C 1 and second heat exchange unit C 2 .
  • the flow of the refrigerant flowing through first heat exchange unit C 1 and second heat exchange unit C 2 in outdoor heat exchanger 3 of the comparative example for the second embodiment is different from the flow of the refrigerant flowing through first heat exchange unit C 1 and second heat exchange unit C 2 in outdoor heat exchanger 3 of refrigeration cycle apparatus 100 according to the second embodiment.
  • each of first path PA and second path PB is located in the form of an inverted N-shape.
  • first path PA and second path PB are not located line-symmetrically with respect to each other in second direction D 2 .
  • inflow passage IF of first heat exchange unit C 1 in first heat exchange region HF 1 is located adjacent to outflow passage OF of first heat exchange unit C 1 in second heat exchange region HF 2 in second direction D 2 .
  • inflow passages IF of first heat exchange unit C 1 in first heat exchange region HF 1 and second heat exchange region HF 2 are located adjacent to each other in second direction D 2 . Therefore, a temperature difference can be small between the refrigerant flowing through inflow passage IF of first heat exchange unit C 1 in first heat exchange region HF 1 and the refrigerant flowing through inflow passage IF of first heat exchange unit C 1 in second heat exchange region HF 2 . Therefore, thermal loss between first path PA and second path PB can be small.
  • the number of stages in first heat exchange region HF 1 is different from the number of stages in second heat exchange region HF 2 . Further, in each of first heat exchange region HF 1 and second heat exchange region HF 2 , the number of stages of first heat exchange unit C 1 is different from the number of stages of second heat exchange unit C 2 .
  • First path PA and second path PB are not located line-symmetrically with respect to each other in second direction D 2 .
  • inflow passage IF of second heat exchange unit C 2 is located in a stage different from inflow passage IF of first heat exchange unit C 1 in second direction D 2 .
  • Inflow passage IF of second heat exchange unit C 2 is preferably located at a stage displaced by two stages from inflow passage IF of first heat exchange unit C 1 .
  • first heat exchange region HF 1 the plurality of heat transfer portions P 1 are located in first stage S 1 to seventh stage S 7 .
  • inflow passage IF of second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • Outflow passage OF of second heat exchange unit C 2 is heat transfer portion P 1 located in seventh stage S 7 .
  • Inflow passage IF of first heat exchange unit C 1 is heat transfer portion P 1 located in third stage S 3 .
  • Outflow passage OF of first heat exchange unit C 1 is heat transfer portion P 1 located in seventh stage S 7 .
  • second heat exchange region HF 2 the plurality of heat transfer portions P 1 are located in first stage S 1 to fifth stage S 5 .
  • inflow passage IF of second heat exchange unit C 2 is heat transfer portion P 1 located in third stage S 3 .
  • Outflow passage OF of second heat exchange unit C 2 is heat transfer portion P 1 located in first stage S 1 .
  • Inflow passage IF of first heat exchange unit C 1 is heat transfer portion P 1 located in fifth stage S 5 .
  • Outflow passage OF of first heat exchange unit C 1 is heat transfer portion P 1 located in first stage S 1 .
  • inflow passage IF of second heat exchange unit C 2 is located in a stage different from inflow passage IF of first heat exchange unit C 1 in second direction D 2 . Therefore, a degree of freedom of design can be improved.
  • a refrigeration cycle apparatus 100 according to a third embodiment has the same configuration, functions, and effects as those of refrigeration cycle apparatus 100 according to the first embodiment unless otherwise stated particularly.
  • the inner diameters of the plurality of heat transfer portions P 1 are different for each stage.
  • the inner diameters of heat transfer portions P 1 are smaller in the order of first stage S 1 to fourth stage S 4 .
  • inflow passage IF has an inner diameter larger than an inner diameter of outflow passage OF.
  • inflow passage IF has an inner diameter larger than that of outflow passage OF.
  • the temperature of the refrigerant in inflow passage IF is higher than the temperature of the refrigerant in outflow passage OF. Therefore, a temperature difference between the refrigerant and the air is large in inflow passage IF, thus resulting in a large heat exchange amount.
  • a temperature difference between the refrigerant and the air is small in outflow passage OF, thus resulting in a small heat exchange amount. Since inflow passage IF has an inner diameter larger than that of outflow passage OF, heat exchange performance can be improved.
  • a refrigeration cycle apparatus 100 according to a fourth embodiment has the same configuration, functions, and effects as those of refrigeration cycle apparatus 100 according to the second embodiment unless otherwise stated particularly.
  • blower apparatus 6 includes: a fan 6 a having a tip and a root; a boss 6 b to which the root of fan 6 a is fixed; and a motor 6 c to which boss 6 b is rotatably connected.
  • Blower apparatus 6 is, for example, a propeller fan.
  • Outflow passage OF of each of first heat exchange unit C 1 and second heat exchange unit C 2 in first heat exchange region HF 1 are located to overlap with the tip of fan 6 a in first direction D 1 .
  • outflow passages OF of first heat exchange unit C 1 and second heat exchange unit C 2 in first heat exchange region HF 1 are located to overlap with the tip of fan 6 a when viewed in first direction D 1 .
  • Outflow passages OF of first heat exchange unit C 1 and second heat exchange unit C 2 in second heat exchange region HF 2 are located to overlap with boss 6 b and motor 6 c in first direction D 1 .
  • Inflow passages IF of first heat exchange unit C 1 and second heat exchange unit C 2 in each of first heat exchange region HF 1 and second heat exchange region HF 2 are located to overlap with the center between the tip and the root of fan 6 a in first direction D 1 .
  • the center of fan 6 a is a portion that sandwiches a middle between the tip and root of fan 6 a and that falls within a range of 40% or more and 60% or less of a distance between the tip and root of fan 6 a in second direction D 2 .
  • the wind speed distribution is an average wind speed in a direction (stacking direction) of the stack of the fins. Since each of fan 6 a and boss 6 b has a substantially circular shape, when wind speeds are integrated in the direction of the stack of the fins, a wind speed at tip (outer edge portion) L 1 of fan 6 a is smaller than a wind speed at center (central portion) L 2 of fan 6 a . A wind speed in a central portion L 3 of blower apparatus 6 in which boss 6 b and motor 6 c are located is lower than a wind speed at center (central portion) L 2 of fan 6 a . That is, the wind speed at center (central portion) L 2 of fan 6 a is larger than each of the wind speeds at tip (outer edge portion) L 1 of fan 6 a and central portion L 3 of blower apparatus 6 .
  • inflow passages IF of first heat exchange unit C 1 and second heat exchange unit C 2 in each of first heat exchange region HF 1 and second heat exchange region HF 2 are located to overlap with the center between the tip and the root of fan 6 a in first direction D 1 . Therefore, inflow passages IF of first heat exchange unit C 1 and second heat exchange unit C 2 can be located to overlap with the center of fan 6 a having a large wind speed (air volume). Therefore, a temperature of blown air can be made low.
  • a refrigeration cycle apparatus 100 according to a fifth embodiment has the same configuration, functions, and effects as those of refrigeration cycle apparatus 100 according to the second embodiment unless otherwise stated particularly.
  • outdoor heat exchanger 3 further includes a sub-cool line SCL connected to outflow passage OF of first heat exchange unit C 1 in each of first heat exchange region HF 1 and second heat exchange region HF 2 .
  • Sub-cool line SCL is configured to cool the refrigerant into a super-cooling state.
  • Sub-cool line SCL is located adjacent to outflow passage OF of first heat exchange unit C 1 in first heat exchange region HF 1 in second direction D 2 .
  • outdoor heat exchanger 3 has two pairs of first heat exchange regions HF 1 and second heat exchange regions HF 2 .
  • a first set ST 1 of first heat exchange region HF 1 and second heat exchange region HF 2 and a second set ST 2 of first heat exchange region HF 1 and second heat exchange region HF 2 are located in second direction D 2 .
  • sub-cool line SCL is located opposite to second heat exchange region HF 2 with respect to first heat exchange region HF 1 in second direction D 2 .
  • Each of first set ST 1 of first heat exchange region HF 1 and second heat exchange region HF 2 and second set ST 2 of first heat exchange region HF 1 and second heat exchange region HF 2 has a portion R 1 at which the temperature of the refrigerant is high and a portion R 2 at which the temperature of the refrigerant is low.
  • Sub-cool line SCL of second set ST 2 of first heat exchange region HF 1 and second heat exchange region HF 2 is located to be interposed between portions R 2 at each of which the temperature of the refrigerant is low.
  • each of first path PA in first heat exchange region HF 1 and second path PB in second heat exchange region HF 2 is formed to have a U-shape.
  • Sub-cool line SCL is located adjacent to inflow passage IF of first heat exchange unit C 1 in first heat exchange region HF 1 in second direction D 2 . Therefore, a temperature difference in the refrigerant is large between first path PA and sub-cool line SCL. This leads to large thermal loss between first path PA and sub-cool line SCL.
  • sub-cool line SCL is located adjacent to outflow passage OF of first heat exchange unit C 1 in first heat exchange region HF 1 in second direction D 2 .

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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
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JPS6380465U (de) * 1986-11-14 1988-05-27
JPH06272998A (ja) * 1993-03-18 1994-09-27 Toshiba Corp 冷凍装置
JPH06307738A (ja) * 1993-04-21 1994-11-01 Hitachi Ltd 非共沸混合冷媒用凝縮器
JPH07269985A (ja) 1994-03-31 1995-10-20 Toshiba Corp 熱交換器
JPH07280375A (ja) * 1994-04-06 1995-10-27 Hitachi Ltd 空気調和装置
JPH10281574A (ja) * 1997-04-07 1998-10-23 Hitachi Ltd 空気調和機
JP3888000B2 (ja) * 1999-08-27 2007-02-28 株式会社日立製作所 空気調和機
JP2008111622A (ja) * 2006-10-31 2008-05-15 Toshiba Kyaria Kk 熱交換器、これを用いた空気調和機の室外機
JP2013113493A (ja) * 2011-11-29 2013-06-10 Panasonic Corp 熱交換素子とそれを用いた熱交換換気機器
JP5956743B2 (ja) * 2011-11-29 2016-07-27 日立アプライアンス株式会社 空気調和機
JP6097127B2 (ja) * 2013-04-10 2017-03-15 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和装置
JP5644889B2 (ja) * 2013-04-30 2014-12-24 ダイキン工業株式会社 空気調和機の室内ユニット
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