US20240288202A1 - Heat exchanger and refrigeration cycle apparatus - Google Patents

Heat exchanger and refrigeration cycle apparatus Download PDF

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Publication number
US20240288202A1
US20240288202A1 US18/567,529 US202118567529A US2024288202A1 US 20240288202 A1 US20240288202 A1 US 20240288202A1 US 202118567529 A US202118567529 A US 202118567529A US 2024288202 A1 US2024288202 A1 US 2024288202A1
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United States
Prior art keywords
heat transfer
heat exchanger
refrigerant
transfer tubes
heat
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Abandoned
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US18/567,529
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English (en)
Inventor
Takuya Matsuda
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUDA, TAKUYA
Publication of US20240288202A1 publication Critical patent/US20240288202A1/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
    • 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
    • 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
    • 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
    • F25B41/40—Fluid line 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • 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
    • F28D1/053—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 straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • 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
    • F28D2021/007—Condensers
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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

Definitions

  • the present disclosure relates to a heat exchanger and a refrigeration cycle apparatus.
  • Arranging heat transfer tubes in multiple lines has been proposed in order to enhance the performance of a heat exchanger of a refrigeration cycle apparatus. Since a heat exchanger is mounted in a limited space, arranging heat transfer tubes in multiple lines can lead to an increase in mounting density of the heat transfer tubes and an increase in heat transfer area.
  • a heat exchanger of an indoor unit of an air conditioning apparatus described in Japanese Patent Laying-Open No. 2014-40983 (PTL 1) has heat transfer tubes arranged in multiple lines.
  • the present disclosure has been made in light of the above-described problem, and an object thereof is to provide a heat exchanger and a refrigeration cycle apparatus that make it possible to averagely ensure the heat exchange efficiency in a condenser and an evaporator, while using a zeotropic refrigerant.
  • a heat exchanger of the present disclosure includes: a first heat transfer portion having a plurality of first heat transfer tubes; and a zeotropic refrigerant flowing through the plurality of first heat transfer tubes of the first heat transfer portion.
  • the plurality of first heat transfer tubes are arranged in a line.
  • the first heat transfer portion has the plurality of first heat transfer tubes arranged to allow flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes to be orthogonal to flow of air flowing across the first heat transfer portion.
  • the heat exchanger of the present disclosure it is possible to averagely ensure the heat exchange efficiency in a condenser and an evaporator, while using a zeotropic refrigerant.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a first embodiment.
  • FIG. 2 shows a heat exchanger according to the first embodiment and a blowout temperature distribution.
  • FIG. 3 is a perspective view schematically showing the heat exchanger according to the first embodiment.
  • FIG. 4 is a cross-sectional view schematically showing a first heat transfer tube and a second heat transfer tube of the heat exchanger according to the first embodiment.
  • FIG. 5 is a perspective view schematically showing a capillary tube of the heat exchanger according to the first embodiment.
  • FIG. 6 is a cross-sectional view schematically showing a modification of the first heat transfer tube and the second heat transfer tube of the heat exchanger according to the first embodiment.
  • FIG. 7 is a cross-sectional view schematically showing a first modification of the heat exchanger according to the first embodiment.
  • FIG. 8 is a front view schematically showing a second modification of the heat exchanger according to the first embodiment.
  • FIG. 9 shows the heat exchange efficiency of a counter flow, a parallel flow and an orthogonal flow in each of a condenser and an evaporator.
  • FIG. 10 shows a relationship between a refrigerant flow and a refrigerant temperature in each of the condenser and the evaporator of the heat exchanger according to the first embodiment.
  • FIG. 11 shows a heat exchanger according to a second embodiment and a blowout temperature distribution.
  • FIG. 12 is a cross-sectional view schematically showing a modification of the heat exchanger according to the second embodiment.
  • FIG. 13 shows a relationship between a refrigerant flow and a refrigerant temperature in each of a condenser and an evaporator of the heat exchanger according to the second embodiment.
  • FIG. 14 shows a heat exchanger according to a third embodiment and a blowout temperature distribution.
  • FIG. 15 is a cross-sectional view schematically showing a first modification of the heat exchanger according to the third embodiment.
  • FIG. 16 is a cross-sectional view schematically showing a second modification of the heat exchanger according to the third embodiment.
  • FIG. 17 shows a relationship between a refrigerant flow and a refrigerant temperature in each of a condenser and an evaporator of the heat exchanger according to the third embodiment.
  • FIG. 1 A configuration of a refrigeration cycle apparatus 100 according to a first embodiment will be described with reference to FIG. 1 .
  • an air conditioner is described as an example of refrigeration cycle apparatus 100 .
  • a solid arrow in FIG. 1 indicates a flow of refrigerant during cooling operation.
  • a dashed arrow in FIG. 1 indicates a flow of refrigerant during heating operation.
  • refrigeration cycle apparatus 100 includes a compressor 1 , a four-way valve 2 , an outdoor heat exchanger 3 , an expansion valve 4 , an indoor heat exchanger 5 , an outdoor blower 6 , an indoor blower 7 , and a controller 8 .
  • a heat exchanger HE according to the first embodiment is applied to outdoor heat exchanger 3 .
  • Refrigeration cycle apparatus 100 includes an outdoor unit 101 , and an indoor unit 102 connected to outdoor unit 101 .
  • a refrigerant circuit 10 includes compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , expansion valve 4 , and indoor heat exchanger 5 .
  • Compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , expansion valve 4 , and indoor heat exchanger 5 are connected by a pipe 20 .
  • Refrigerant circuit 10 is configured to circulate the refrigerant.
  • the refrigerant is a zeotropic refrigerant.
  • the zeotropic refrigerant includes R32, and may include R1234yf as another refrigerant.
  • the zeotropic refrigerant may include R1123 or R1234ze as another refrigerant.
  • the zeotropic refrigerant may be a mixture of three or more types of refrigerant.
  • Compressor 1 four-way valve 2 , outdoor heat exchanger 3 , expansion valve 4 , outdoor blower 6 , and controller 8 are housed in outdoor unit 101 .
  • Indoor heat exchanger 5 and indoor blower 7 are housed in indoor unit 102 .
  • Outdoor unit 101 and indoor unit 102 are connected by a gas pipe 21 and a liquid pipe 22 .
  • a part of pipe 20 forms gas pipe 21 and liquid pipe 22 .
  • Refrigerant circuit 10 is configured such that the refrigerant circulates in the order of compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , expansion valve 4 , indoor heat exchanger 5 , and four-way valve 2 during the cooling operation.
  • refrigerant circuit 10 is configured such that the refrigerant circulates in the order of compressor 1 , four-way valve 2 , indoor heat exchanger 5 , expansion valve 4 , outdoor heat exchanger 3 , and four-way valve 2 during the heating operation.
  • Compressor 1 is configured to compress the refrigerant.
  • Compressor 1 is for compressing the zeotropic refrigerant flowing into heat exchanger HE.
  • Compressor 1 is configured to compress and discharge the suctioned refrigerant.
  • Compressor 1 may be configured to be capacity-variable.
  • Compressor 1 may be configured such that a capacity thereof varies through the adjustment of the rotation speed of compressor 1 based on an instruction from controller 8 .
  • Four-way valve 2 is configured to switch the flow of the refrigerant to allow the refrigerant compressed by compressor 1 to flow to outdoor heat exchanger 3 or indoor heat exchanger 5 .
  • Four-way valve 2 has a first port P 1 to a fourth port P 4 .
  • First port P 1 is connected to the discharge side of compressor 1 .
  • Second port P 2 is connected to the suction side of compressor 1 .
  • Third port P 3 is connected to outdoor heat exchanger 3 .
  • Fourth port P 4 is connected to indoor heat exchanger 5 .
  • Four-way valve 2 is configured to allow the refrigerant discharged from compressor 1 to flow to outdoor heat exchanger 3 during the cooling operation.
  • third port P 3 is connected to first port P 1 and fourth port P 4 is connected to second port P 2 in four-way valve 2 .
  • four-way valve 2 is configured to allow the refrigerant discharged from compressor 1 to flow to indoor heat exchanger 5 during the heating operation.
  • fourth port P 4 is connected to first port P 1 and third port P 3 is connected to second port P 2 in four-way valve 2 .
  • Outdoor heat exchanger 3 is configured to perform heat exchange 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 that condenses the refrigerant during the cooling operation, and to function as an evaporator that evaporates the refrigerant during the heating operation.
  • Expansion valve 4 is configured to expand the refrigerant condensed by the condenser to decompress the refrigerant. Expansion valve 4 is configured to decompress the refrigerant condensed by outdoor heat exchanger 3 during the cooling operation, and to decompress the refrigerant condensed by indoor heat exchanger 5 during the heating operation. Expansion valve 4 is, for example, a solenoid expansion valve.
  • Indoor heat exchanger 5 is configured to perform heat exchange 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 that evaporates the refrigerant during the cooling operation, and to function as a condenser that condenses the refrigerant during the heating operation.
  • Outdoor blower 6 is configured to blow the outdoor air to outdoor heat exchanger 3 . That is, outdoor blower 6 is configured to supply the air to outdoor heat exchanger 3 .
  • Indoor blower 7 is configured to blow the indoor air to indoor heat exchanger 5 . That is, indoor blower 7 is configured to supply the air to indoor heat exchanger 5 .
  • Controller 8 is configured to control the devices of refrigeration cycle apparatus 100 by, for example, performing calculations or providing instructions. Controller 8 is electrically connected to compressor 1 , four-way valve 2 , expansion valve 4 , outdoor blower 6 , indoor blower 7 and the like to control the operation of these components.
  • FIG. 2 shows a relationship between a structure of heat exchanger HE and a blowout temperature distribution of the air.
  • a solid arrow in FIG. 3 indicates a refrigerant flow, and a hollow arrow in FIG. 3 indicates an air flow.
  • outdoor heat exchanger 3 has a heat exchange portion 31 , a header distributor 32 , a gas-liquid two-phase distributor 33 , and the zeotropic refrigerant.
  • Heat exchange portion 31 includes a first heat exchange portion 31 a and a second heat exchange portion 31 b .
  • First heat exchange portion 31 a is arranged on the windward side in an air flow direction D 1 .
  • First heat exchange portion 31 a is arranged in a first row in air flow direction D 1 .
  • Second heat exchange portion 31 b is arranged on the leeward side in air flow direction D 1 .
  • Second heat exchange portion 31 b is arranged in a second row in air flow direction D 1 .
  • First heat exchange portion 31 a includes a first heat transfer portion HP 1 .
  • first heat exchange portion 31 a includes a plurality of first heat transfer portions HP 1 .
  • Second heat exchange portion 31 b includes a second heat transfer portion HP 2 .
  • second heat exchange portion 31 b includes a plurality of second heat transfer portions HP 2 .
  • First heat exchange portion 31 a has a plurality of first fins F 1 , a plurality of first heat transfer tubes T 1 , and a plurality of first connection portions C 1 .
  • Each of the plurality of first fins F 1 is formed like a plate.
  • the plurality of first fins F 1 are arranged to overlap with each other.
  • the plurality of first fins F 1 are made of, for example, aluminum.
  • the plurality of first heat transfer tubes T 1 pass through the plurality of first fins F 1 .
  • the plurality of first heat transfer tubes T 1 are configured to extend linearly in an orthogonal direction D 2 that is orthogonal to air flow direction D 1 .
  • the plurality of first connection portions C 1 are portions that connect first heat transfer tubes T 1 outside the plurality of first fins F 1 .
  • Each of the plurality of first heat transfer tubes T 1 is connected by each of the plurality of first connection portions C 1 , such that the plurality of first heat transfer tubes T 1 and the plurality of first connection portions C 1 are configured to meander as a whole.
  • the plurality of first heat transfer tubes T 1 and the plurality of first connection portions C 1 are made of, for example, copper or aluminum.
  • First heat transfer portion HP 1 has the plurality of first heat transfer tubes T 1 .
  • the plurality of first heat transfer tubes T 1 are arranged in a line.
  • the plurality of first heat transfer tubes T 1 are aligned in a column direction D 3 that intersects with air flow direction D 1 and orthogonal direction D 2 .
  • First heat transfer portion HP 1 has the plurality of first heat transfer tubes T 1 arranged to allow a flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 to be orthogonal to a flow of air flowing across first heat transfer portion HP 1 .
  • Second heat exchange portion 31 b has a plurality of second fins F 2 , a plurality of second heat transfer tubes T 2 , and a plurality of second connection portions C 2 .
  • Each of the plurality of second fins F 2 is formed like a plate.
  • the plurality of second fins F 2 are arranged to overlap with each other.
  • the plurality of second fins F 2 are made of, for example, aluminum.
  • the plurality of second heat transfer tubes T 2 pass through the plurality of second fins F 2 .
  • the plurality of second heat transfer tubes T 2 are configured to extend linearly in orthogonal direction D 2 that is orthogonal to air flow direction D 1 .
  • the plurality of second connection portions C 2 are portions that connect second heat transfer tubes T 2 outside the plurality of second fins F 2 .
  • Each of the plurality of second heat transfer tubes T 2 is connected by each of the plurality of second connection portions C 2 , such that the plurality of second heat transfer tubes T 2 and the plurality of second connection portions C 2 are configured to meander as a whole.
  • the plurality of second heat transfer tubes T 2 and the plurality of second connection portions C 2 are made of, for example, copper or aluminum.
  • Second heat transfer portion HP 2 has the plurality of second heat transfer tubes T 2 .
  • Second heat transfer portion HP 2 is arranged adjacent to first heat transfer portion HP 1 .
  • the plurality of second heat transfer tubes T 2 are arranged in a line.
  • the plurality of second heat transfer tubes T 2 are aligned along the direction in which the plurality of first heat transfer tubes T 1 are arranged.
  • the plurality of second heat transfer tubes T 2 are aligned in column direction D 3 that intersects with air flow direction D 1 and orthogonal direction D 2 .
  • the zeotropic refrigerant flows through the plurality of first heat transfer tubes T 1 of first heat transfer portion HP 1 .
  • the zeotropic refrigerant continuously flows through the plurality of first heat transfer tubes T 1 and the plurality of first connection portions C 1 .
  • the zeotropic refrigerant flows through the plurality of second heat transfer tubes T 2 of second heat transfer portion HP 2 .
  • the zeotropic refrigerant continuously flows through the plurality of second heat transfer tubes T 2 and the plurality of second connection portions C 2 .
  • header distributor 32 is provided at a heat exchanger inlet (condenser inlet), and gas-liquid two-phase distributor 33 is provided at a heat exchanger outlet (condenser outlet).
  • Gas-liquid two-phase distributor 33 is configured to be capable of evenly distributing a gas-liquid two-phase flow.
  • Gas-liquid two-phase distributor 33 has a distributor 33 a and a capillary tube 34 .
  • each of the plurality of first heat transfer tubes T 1 and the plurality of first connection portions C 1 is a circular tube.
  • Each of the plurality of second heat transfer tubes T 2 and the plurality of second connection portions C 2 is a circular tube.
  • capillary tube 34 includes a first capillary tube 34 a connected to first heat exchange portion 31 a in the first row, and a second capillary tube 34 b connected to second heat exchange portion 31 b in the second row.
  • An inner diameter of first capillary tube 34 a may be larger than an inner diameter of second capillary tube 34 b .
  • a length of first capillary tube 34 a may be longer than a length of second capillary tube 34 b.
  • each of first heat transfer tube T 1 and second heat transfer tube T 2 is a flat tube.
  • Refrigeration cycle apparatus 100 can selectively perform the cooling operation and the heating operation.
  • the refrigerant circulates in refrigerant circuit 10 in the order of compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , expansion 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 outdoor blower 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 indoor blower 7 .
  • the high-pressure gas refrigerant discharged from compressor 1 flows through header distributor 32 of heat exchanger HE into first heat transfer tubes T 1 of first heat exchange portion 31 a in the first row and second heat transfer tubes T 2 of second heat exchange portion 31 b in the second row, and flows orthogonally to the air flow.
  • first capillary tube 34 a placed on the outlet side of first heat exchange portion 31 a smaller than a flow path resistance of second capillary tube 34 b placed on the outlet side of second heat exchange portion 31 b
  • a larger amount of the refrigerant flows through first capillary tube 34 a than second capillary tube 34 b .
  • Heat exchange between the high-pressure gas refrigerant and the air is performed through the plurality of first fins F 1 , the plurality of first heat transfer tubes T 1 , the plurality of second fins F 2 , and the plurality of second heat transfer tubes T 2 , and as a result, the high-pressure gas refrigerant changes into high-pressure liquid refrigerant.
  • the refrigerant circulates in refrigerant circuit 10 in the order of compressor 1 , four-way valve 2 , indoor heat exchanger 5 , expansion 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 indoor blower 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 outdoor blower 6 .
  • the low-pressure gas-liquid two-phase refrigerant having a low degree of dryness is decompressed and stirred in distributor 33 a of gas-liquid two-phase distributor 33 of heat exchanger HE, and thus, is distributed at an equal degree of dryness in a gas-liquid two-phase atomized state.
  • Heat exchange between the low-pressure gas-liquid two-phase refrigerant having a low degree of dryness and the air is performed through the plurality of first fins F 1 , the plurality of first heat transfer tubes T 1 , the plurality of first fins F 1 , and the plurality of second heat transfer tubes T 2 , and as a result, the low-pressure gas-liquid two-phase refrigerant having a low degree of dryness changes into low-pressure gas refrigerant.
  • a plurality of header distributors 32 and a plurality of gas-liquid two-phase distributors 33 are arranged for the respective rows.
  • two header distributors 32 and two gas-liquid two-phase distributors 33 are arranged.
  • Two electronic expansion valves 35 are arranged downstream of two gas-liquid two-phase distributors 33 , respectively.
  • first capillary tube 34 a connected to first heat exchange portion 31 a in the first row is made larger than the inner diameter of second capillary tube 34 b connected to second heat exchange portion 31 b in the second row. Furthermore, the length of first capillary tube 34 a connected to first heat exchange portion 31 a in the first row is made longer than the length of second capillary tube 34 b connected to second heat exchange portion 31 b in the second row.
  • first heat exchange portion 31 a is shown for convenience of description.
  • Second heat exchange portion 31 b is configured similarly to first heat exchange portion 31 a.
  • each of the plurality of first fins F 1 is a corrugated fin.
  • Each of the plurality of first heat transfer tubes T 1 is a linear flat tube.
  • Each of the plurality of first fins F 1 is arranged between corresponding two of the plurality of first heat transfer tubes T 1 .
  • a header 36 is connected to each of both ends of each of the plurality of first heat transfer tubes T 1 .
  • the heat exchange efficiency of a counter flow, a parallel flow and an orthogonal flow in each of the condenser and the evaporator will be described with reference to FIG. 9 .
  • the counter flow, the parallel flow and the orthogonal flow indicate a relationship of the refrigerant flow with respect to the air flow.
  • the heat exchange efficiency becomes lower in the order of the counter flow, the orthogonal flow and the parallel flow.
  • the refrigerant temperature in each path with respect to the refrigerant flow when heat exchanger HE functions as a condenser or an evaporator in the present embodiment will be described with reference to FIG. 10 .
  • the refrigerant temperature in the condenser becomes lower in both of the first row and the second row, as the refrigerant flow increases.
  • the refrigerant temperature in the first row becomes lower than the refrigerant temperature in the second row.
  • the refrigerant temperature in the first row becomes higher than the refrigerant temperature in the second row.
  • first heat transfer portion HP 1 has the plurality of first heat transfer tubes T 1 arranged to allow the flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 to be orthogonal to the flow of the air flowing across first heat transfer portion HP 1 . Therefore, the flow of the zeotropic refrigerant with respect to the air flow is the orthogonal flow.
  • the heat exchange efficiency can be higher than that of the parallel flow, whether heat exchanger HE functions as a condenser or as an evaporator. Accordingly, it is possible to averagely ensure the heat exchange efficiency in the condenser and the evaporator, while using the zeotropic refrigerant.
  • first capillary tube 34 a by making the flow path resistance of first capillary tube 34 a smaller than the flow path resistance of second capillary tube 34 b , a large amount of the refrigerant can flow through first heat transfer tubes T 1 in the first row having a high heat load. Therefore, a difference in outlet temperature of the refrigerant between first heat transfer tubes T 1 in the first row and second heat transfer tubes T 2 in the second row decreases, and thus, the heat exchange efficiency can be increased.
  • Refrigeration cycle apparatus 100 includes above-described heat exchanger HE. Therefore, there can be provided refrigeration cycle apparatus 100 including heat exchanger HE that makes it possible to averagely ensure the heat exchange efficiency in the condenser and the evaporator, while using the zeotropic refrigerant.
  • Heat exchanger HE according to a second embodiment has the same configuration, operation, and function and effect as those of heat exchanger HE according to the first embodiment, unless otherwise specified.
  • an inlet and an outlet for the zeotropic refrigerant in first heat transfer portion HP 1 and an inlet and an outlet for the zeotropic refrigerant in second heat transfer portion HP 2 are arranged opposite to each other.
  • first heat transfer portion HP 1 the refrigerant inlet is arranged in the uppermost column, and the refrigerant outlet is arranged in the lowermost column.
  • second heat transfer portion HP 2 the refrigerant inlet is arranged in the lowermost column, and the refrigerant outlet is arranged in the uppermost column. That is, the inlet and the outlet for the zeotropic refrigerant in first heat transfer portion HP 1 and the inlet and the outlet for the zeotropic refrigerant in second heat transfer portion HP 2 are arranged upside down.
  • heat exchange portion 31 includes a third heat exchange portion 31 c .
  • Third heat exchange portion 31 c is arranged on the windward side relative to first heat exchange portion 31 a in air flow direction D 1 .
  • Third heat exchange portion 31 c is arranged in a first row in air flow direction D 1 .
  • Third heat exchange portion 31 c includes a third heat transfer portion HP 3 .
  • third heat exchange portion 31 c includes a plurality of third heat transfer portions HP 3 .
  • Third heat exchange portion 31 c has a plurality of third fins F 3 , a plurality of third heat transfer tubes T 3 , and a plurality of third connection portions C 3 (not shown).
  • the plurality of third fins F 3 , the plurality of third heat transfer tubes T 3 and the plurality of third connection portions C 3 (not shown) are configured similarly to the plurality of first fins F 1 , the plurality of first heat transfer tubes T 1 and the plurality of first connection portions C 1 (not shown).
  • the zeotropic refrigerant flows through the plurality of third heat transfer tubes T 3 of third heat transfer portion HP 3 .
  • the zeotropic refrigerant continuously flows through the plurality of third heat transfer tubes T 3 and the plurality of third connection portions C 3 (not shown).
  • Capillary tube 34 includes a third capillary tube 34 c connected to third heat exchange portion 31 c .
  • An inner diameter of third capillary tube 34 c may be larger than the inner diameter of first capillary tube 34 a .
  • a length of third capillary tube 34 c may be longer than the length of first capillary tube 34 a.
  • heat exchanger HE In heat exchanger HE according to the present embodiment, the inlet and the outlet for the zeotropic refrigerant in first heat transfer portion HP 1 and the inlet and the outlet for the zeotropic refrigerant in second heat transfer portion HP 2 are arranged opposite to each other. Therefore, an air blowout temperature distribution in a height direction of heat exchanger HE can be averaged.
  • heat exchanger HE when heat exchanger HE is applied to outdoor heat exchanger 3 , an amount of frost formation at low outdoor air temperature is made uniform, and thus, the average heating capacity can be enhanced. In addition, when heat exchanger HE is applied to indoor heat exchanger 5 , dew scattering is less likely to occur, and thus, the comfortability and the quality performance can be enhanced.
  • Heat exchanger HE according to a third embodiment has the same configuration, operation, and function and effect as those of heat exchanger HE according to each of the first and second embodiments, unless otherwise specified.
  • first heat transfer portion HP 1 and second heat transfer portion HP 2 have a first path PS 1 and a second path PS 2 .
  • First path PS 1 is arranged to allow a flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 and the plurality of second heat transfer tubes T 2 to be parallel to a flow of the air flowing across first heat transfer portion HP 1 and second heat transfer portion HP 2 .
  • Second path PS 2 is arranged to allow the flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 and the plurality of second heat transfer tubes T 2 to counter the flow of the air flowing across first heat transfer portion HP 1 and second heat transfer portion HP 2 .
  • First path PS 1 and second path PS 2 are combined.
  • an inlet and an outlet for the zeotropic refrigerant in first heat transfer portion HP 1 and an inlet and an outlet for the zeotropic refrigerant in second heat transfer portion HP 2 are arranged opposite to each other.
  • heat exchange portion 31 includes third heat exchange portion 31 c .
  • Third heat exchange portion 31 c is arranged between first heat exchange portion 31 a and second heat exchange portion 31 b in air flow direction D 1 .
  • first path PS 1 is arranged to allow the flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 and the plurality of second heat transfer tubes T 2 to be parallel to the flow of the air flowing across first heat transfer portion HP 1 and second heat transfer portion HP 2 .
  • Second path PS 2 is arranged to allow the flow of the zeotropic refrigerant flowing through the plurality of first heat transfer tubes T 1 and the plurality of second heat transfer tubes T 2 to counter the flow of the air flowing across first heat transfer portion HP 1 and second heat transfer portion HP 2 . Therefore, the air blowout temperature distribution in the height direction of heat exchanger HE can be further averaged. As a result, the heat load of each path can be further made uniform, and thus, the heat exchange efficiency can be increased.
  • heat exchanger HE when heat exchanger HE is applied to outdoor heat exchanger 3 , an amount of frost formation at low outdoor air temperature is made uniform, and thus, the average heating capacity can be enhanced. In addition, when heat exchanger HE is applied to indoor heat exchanger 5 , dew scattering is less likely to occur, and thus, the comfortability and the quality performance can be enhanced.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US18/567,529 2021-07-07 2021-07-07 Heat exchanger and refrigeration cycle apparatus Abandoned US20240288202A1 (en)

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WO2023281656A1 (ja) 2023-01-12
JP7630622B2 (ja) 2025-02-17

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