US20130299152A1 - Heat exchanger and air conditioner - Google Patents

Heat exchanger and air conditioner Download PDF

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Publication number
US20130299152A1
US20130299152A1 US13/980,584 US201213980584A US2013299152A1 US 20130299152 A1 US20130299152 A1 US 20130299152A1 US 201213980584 A US201213980584 A US 201213980584A US 2013299152 A1 US2013299152 A1 US 2013299152A1
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US
United States
Prior art keywords
upwind
heat exchanger
heat
air
plates
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/980,584
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English (en)
Inventor
Yasutaka Ohtani
Yoshio Oritani
Takuya Kazusa
Masanori Jindou
Junichi Hamadate
Shun Yoshioka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
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Daikin Industries Ltd
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Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YOSHIOKA, SHUN, HAMADATE, Junichi, KAZUSA, Takuya, ORITANI, YOSHIO, JINDOU, MASANORI, OHTANI, Yasutaka
Publication of US20130299152A1 publication Critical patent/US20130299152A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/04—Preventing the formation of frost or condensate
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to heat exchangers having a flat tube and a fin and configured to exchange heat between a fluid flowing in the flat tube and air, and air conditioners having the heat exchangers.
  • Patent Document 1 and Patent Document 2 show heat exchangers of this type.
  • a plurality of flat tubes each extending in a horizontal direction, are arranged one above another with a predetermined space between the flat tubes, and plate-like fins are arranged in a direction along which the flat tubes extend, with a predetermined space between the fins.
  • FIG. 2 of Patent Document 2 elongated cutouts are formed in the fins, and the flat tube is inserted in each of the cutouts.
  • air flowing in an air passage between adjacent flat tubes is heat exchanged with a fluid flowing in the flat tube.
  • the present invention is thus intended to prevent frost, in a heat exchanger having a plurality of flat tubes and a plurality of fins, from adhering to a surface of each fin in an air passage.
  • the first aspect of the present invention is directed to a heat exchanger, including: a plurality of flat tubes ( 33 ) arranged one above another such that flat surfaces thereof face each other; and a plurality of vertically extending, plate-like fins ( 36 ) arranged in an extension direction of the flat tubes ( 33 ), wherein each of the fins ( 36 ) includes a plurality of intermediate plates ( 70 ) arranged one above another and dividing a space between adjacent ones of the flat tubes ( 33 ) into air passages ( 40 ), a plurality of tube insertion portions ( 46 ) each provided between vertically adjacent ones of the intermediate plates ( 70 ), with an upwind side thereof being open such that a corresponding one of the flat tubes ( 33 ) is inserted therein, a vertically extending downwind plate ( 75 ) that is continuous with downwind ends of the plurality of intermediate plates ( 70 ) arranged one above another, and a plurality of upwind plates ( 77 ) extending further toward an upwind side than the flat tubes ( 33 )
  • a plurality of upwind plates ( 77 ) project from the upwind ends of the plurality of intermediate plates ( 70 ) to the upwind side.
  • the air passes through the heat exchanger serving as an evaporator, the air is cooled first by the upwind plates ( 77 ).
  • the air is cooled by the upwind plates ( 77 ) to a temperature equal to or lower than a dew point, moisture in the air is condensed.
  • the temperature of the air flowing on the lateral sides of the upwind plates ( 77 ) is equal to or lower than 0° C., moisture in the air turns into frost on the surface of the upwind plates ( 77 ).
  • the air is dehumidified.
  • the air dehumidified in this manner flows in the air passages ( 40 ) along the intermediate plates ( 70 ).
  • the intermediate plates ( 70 ) are located relatively close to the flat tubes ( 33 ), and thus, the air flowing in the air passages ( 40 ) is cooled rapidly.
  • this air has been dehumidified by the upwind plates ( 77 ), and therefore, the accumulation of frost on the surfaces of the intermediate plate ( 70 ) is reduced.
  • each of the upwind plates ( 77 ) is provided with an upwind side heat-transfer portion ( 81 , 91 , 92 , 95 ), and therefore, heat transfer between the air and the upwind plates ( 77 ) is promoted.
  • the air flowing on the lateral sides of the upwind plates ( 77 ) can be easily cooled, and the effect of dehumidifying the air is improved.
  • the accumulation of frost on the surfaces of the intermediate plates ( 70 ) can be further advantageously reduced.
  • the second aspect of the present invention is that in the first aspect of the present invention, the upwind side heat-transfer portion includes a rib ( 91 , 92 ) which extends in a protruding direction of the upwind plates ( 77 ).
  • the upwind plate ( 77 ) is provided with the rib ( 91 , 92 ).
  • the rib ( 91 , 92 ) comprises an upwind side heat-transfer portion.
  • the upwind plate ( 77 ) projects from the intermediate plate ( 70 ). This may lead to easy bending of the upwind plate ( 77 ) in a horizontal direction with respect to the intermediate plate ( 70 ).
  • the rib ( 91 , 92 ) of the upwind plate ( 77 ) is provided so as to extend in the projecting direction of the upwind plate ( 77 ) to increase the bending strength of the upwind plate ( 77 ) in the horizontal direction.
  • the upwind side heat-transfer portion includes an intermediate heat-transfer portion ( 81 , 95 ) provided at a middle portion, in a vertical direction, of each of the upwind plates ( 77 ), and the rib ( 91 , 92 ) provided on at least one of an upper side or a low side of the intermediate heat-transfer portion ( 81 , 95 ).
  • the upwind plate ( 77 ) is provided with the intermediate heat-transfer portion ( 81 , 95 ).
  • the intermediate heat-transfer portion ( 81 , 95 ) comprises an upwind side heat-transfer portion. Since the intermediate heat-transfer portion ( 81 , 95 ) is provided at a middle portion, in the vertical direction, of the upwind plate ( 77 ), heat transfer between the air and the intermediate heat-transfer portion ( 81 , 95 ) is promoted, and the effect of cooling the air is improved.
  • the intermediate heat-transfer portion ( 81 , 95 ) provided on the upwind plate ( 77 ) may easily lead the air to the upper side or the lower side of the intermediate heat-transfer portion ( 81 , 95 ).
  • the rib ( 91 , 92 ) is provided on the upper side or the lower side of the intermediate heat-transfer portion ( 81 , 95 ), and therefore, heat transfer between the air and the rib ( 91 , 92 ) is promoted as well. As a result, the effect of cooling the air flowing on the lateral sides of the upwind plates ( 77 ) is further improved.
  • the upwind side heat-transfer portion includes a protrusion ( 81 ) which extends in a direction orthogonal to an air passage direction.
  • the upwind plate ( 77 ) is provided with the protrusion ( 81 ).
  • the protrusion ( 81 ) comprises an upwind side heat-transfer portion. Since the protrusion ( 81 ) extends in a direction which intersects with the air passage direction, heat transfer between the air and the protrusion ( 81 ) is promoted, and the effect of cooling the air is improved.
  • the fifth aspect of the present invention is that in any one of the first to fourth aspects of the present invention, the upwind side heat-transfer portion includes a raised portion ( 95 ) formed by cutting and bending part of the fin ( 36 ).
  • the upwind plate ( 77 ) is provided with the raised portion ( 95 ) as an upwind side heat-transfer portion. As a result, heat transfer between the air and the raised portion ( 95 ) is promoted, and the effect of cooling the air is improved.
  • the sixth aspect of the present invention is directed to an air conditioner, and having a refrigerant circuit ( 20 ) including the heat exchanger ( 30 ) of any one of the first to fifth aspects of the present invention, wherein the refrigerant circuit ( 20 ) performs a refrigeration cycle by circulating a refrigerant.
  • the heat exchanger ( 30 ) of the first to fifth aspects of the present invention is applied to the air conditioner.
  • the heat exchanger ( 30 ) serving as an evaporator the accumulation of frost on the surfaces of the intermediate plates ( 70 ) which partition the air passages ( 40 ) is reduced.
  • the upwind plates ( 77 ) are provided so as to extend from the intermediate plates ( 70 ) of the fin ( 36 ) to the upwind side, and each of the upwind plates ( 77 ) is provided with the upwind side heat-transfer portion ( 81 , 91 , 92 , 95 ).
  • the air before flowing into the air passages ( 40 ) can be dehumidified by the upwind plates ( 77 ). This can reduce the accumulation of frost on the surfaces of the intermediate plates ( 70 ), and thus, it is possible to prevent a reduction in heat-transfer rate of the fin ( 36 ), and an increase in flow pass resistance of the air passages ( 40 ).
  • the rib ( 91 , 92 ) can improve the effect of cooling the air, and prevent bending of the upwind plates ( 77 ). Since leaning of the upwind plates ( 77 ) is prevented as mentioned, the air can flow evenly into the air passages ( 40 ). As a result, reliability of the heat exchanger can be ensured.
  • heat transfer between the air and the upwind plates ( 77 ) can be promoted, and the effect of cooling the air by the upwind plates ( 77 ) can be further improved.
  • the tip of the raised portion ( 95 ) is in contact with the adjacent upwind plate ( 77 ), thereby preventing the upwind plate ( 77 ) from leaning horizontally.
  • the amount of frost adhering to the intermediate plates ( 70 ) facing the air passages ( 40 ) can be reduced.
  • FIG. 1 is a refrigerant circuit diagram showing a schematic configuration of an air conditioner having a heat exchanger of an embodiment.
  • FIG. 2 is an oblique view schematically showing the heat exchanger of the embodiment.
  • FIG. 3 is a partial cross-sectional view of the front side of the heat exchanger of the embodiment.
  • FIG. 4 is a cross-sectional view of part of the heat exchanger taken along the line A-A of FIG. 3 .
  • FIG. 5 shows a main part of a fin of the heat exchanger of the embodiment.
  • FIG. 5(A) is a front side of the fin.
  • FIG. 5(B) is a cross-sectional view taken along the line B-B of FIG. 5(A) .
  • FIG. 6 shows cross-sectional views of the fins of the heat exchanger of the embodiment.
  • FIG. 6(A) is a cross-section taken along the line C-C of FIG. 5 .
  • FIG. 6(B) is a cross-section taken along the line D-D of FIG. 5 .
  • a heat exchanger ( 30 ) of the embodiment comprises an outdoor heat exchanger ( 23 ) of an air conditioner ( 10 ) described later.
  • the air conditioner ( 10 ) having the heat exchanger ( 30 ) of the present embodiment will be described with reference to FIG. 1 .
  • the air conditioner ( 10 ) has an outdoor unit ( 11 ) and an indoor unit ( 12 ).
  • the outdoor unit ( 11 ) and the indoor unit ( 12 ) are connected to each other via a liquid communication pipe ( 13 ) and a gas communication pipe ( 14 ).
  • a refrigerant circuit ( 20 ) is formed by the outdoor unit ( 11 ), the indoor unit ( 12 ), the liquid communication pipe ( 13 ), and the gas communication pipe ( 14 ).
  • the refrigerant circuit ( 20 ) includes a compressor ( 21 ), a four-way valve ( 22 ), an outdoor heat exchanger ( 23 ), an expansion valve ( 24 ), and an indoor heat exchanger ( 25 ).
  • the compressor ( 21 ), the four-way valve ( 22 ), the outdoor heat exchanger ( 23 ), and the expansion valve ( 24 ) are accommodated in the outdoor unit ( 11 ).
  • the outdoor unit ( 11 ) is provided with an outdoor fan ( 15 ) configured to supply outdoor air to the outdoor heat exchanger ( 23 ).
  • the indoor heat exchanger ( 25 ) is accommodated in the indoor unit ( 12 ).
  • the indoor unit ( 12 ) is provided with an indoor fan ( 16 ) configured to supply indoor air to the indoor heat exchanger ( 25 ).
  • the refrigerant circuit ( 20 ) is a closed circuit filled with a refrigerant.
  • a discharge side of the compressor ( 21 ) is connected to a first port of the four-way valve ( 22 ), and a suction side of the compressor ( 21 ) is connected to a second port of the four-way valve ( 22 ).
  • the outdoor heat exchanger ( 23 ), the expansion valve ( 24 ), and the indoor heat exchanger ( 25 ) are provided sequentially from a third port to a fourth port of the four-way valve ( 22 ).
  • the compressor ( 21 ) is a scroll type or rotary type hermetic compressor.
  • the four-way valve ( 22 ) switches between a first state (the state shown in broken line in FIG. 1 ) in which the first port communicates with the third port, and the second port communicates with the fourth port, and a second state (the state shown in solid line in FIG. 1 ) in which the first port communicates with the fourth port, and the second port communicates with the third port.
  • the expansion valve ( 24 ) is a so-called electronic expansion valve ( 24 ).
  • the outdoor heat exchanger ( 23 ) the outdoor air is heat exchanged with the refrigerant.
  • the outdoor heat exchanger ( 23 ) is comprised of the heat exchanger ( 30 ) of the present embodiment.
  • the indoor heat exchanger ( 25 ) the indoor air is heat exchanged with the refrigerant.
  • the indoor heat exchanger ( 25 ) is comprised of a so-called cross-fin type fin-and-tube heat exchanger having a circular heat-transfer tube.
  • the air conditioner ( 10 ) performs a cooling operation.
  • the four-way valve ( 22 ) is set to the first state during the cooling operation.
  • the outdoor fan ( 15 ) and the indoor fan ( 16 ) are driven during the cooling operation.
  • the refrigerant circuit ( 20 ) performs a refrigeration cycle. Specifically, the refrigerant discharged from the compressor ( 21 ) passes through the four-way valve ( 22 ), flows into the outdoor heat exchanger ( 23 ), and dissipates heat to the outdoor air and condenses. The refrigerant flowing out of the outdoor heat exchanger ( 23 ) expands when it passes through the expansion valve ( 24 ), flows into the indoor heat exchanger ( 25 ), and takes heat from the indoor air and evaporates. The refrigerant flowing out of the indoor heat exchanger ( 25 ) passes through the four-way valve ( 22 ) and is then sucked into the compressor ( 21 ) and compressed. The indoor unit ( 12 ) supplies air which has been cooled in the indoor heat exchanger ( 25 ) to an indoor space.
  • the air conditioner ( 10 ) performs a heating operation.
  • the four-way valve ( 22 ) is set to the second state during the heating operation.
  • the outdoor fan ( 15 ) and the indoor fan ( 16 ) are driven during the heating operation.
  • the refrigerant circuit ( 20 ) performs a refrigeration cycle. Specifically, the refrigerant discharged from the compressor ( 21 ) passes the four-way valve ( 22 ), flows into the indoor heat exchanger ( 25 ), and dissipates heat to the indoor air and condenses. The refrigerant flowing out of the indoor heat exchanger ( 25 ) expands when it passes through the expansion valve ( 24 ), flows into the outdoor heat exchanger ( 23 ), and takes heat from the outdoor air and evaporates. The refrigerant flowing out of the outdoor heat exchanger ( 23 ) passes through the four-way valve ( 22 ) and is then sucked into the compressor ( 21 ) and compressed. The indoor unit ( 12 ) supplies air which has been heated in the indoor heat exchanger ( 25 ) to an indoor space.
  • the outdoor heat exchanger ( 23 ) functions as an evaporator in the heating operation.
  • the evaporation temperature of the refrigerant in the outdoor heat exchanger ( 23 ) may sometimes be below 0° C.
  • the moisture in the outdoor air turns into frost and adheres to the outdoor heat exchanger ( 23 ).
  • the air conditioner ( 10 ) performs a defrosting operation every time a duration of the heating operation reaches a predetermined value (e.g., several tens of minutes), for example.
  • the four-way valve ( 22 ) is switched from the second state to the first state, and the outdoor fan ( 15 ) and the indoor fan ( 16 ) are stopped.
  • a high temperature refrigerant discharged from the compressor ( 21 ) is supplied to the outdoor heat exchanger ( 23 ).
  • the frost adhering to the surface of the outdoor heat exchanger ( 23 ) is heated and melted by the refrigerant.
  • the refrigerant which dissipates heat in the outdoor heat exchanger ( 23 ) sequentially passes through the expansion valve ( 24 ) and the indoor heat exchanger ( 25 ), and is then sucked into the compressor ( 21 ) and compressed.
  • the heating operation starts again. That is, the four-way valve ( 22 ) is switched from the first state to the second state, and the outdoor fan ( 15 ) and the indoor fan ( 16 ) are driven again.
  • the heat exchanger ( 30 ) of the present embodiment which comprises the outdoor heat exchanger ( 23 ) of the air conditioner ( 10 ) will be described with reference to FIGS. 2 to 6 .
  • the heat exchanger ( 30 ) of the present embodiment includes one first header collecting pipe ( 31 ), one second header collecting pipe ( 32 ), a plurality of flat tubes ( 33 ), and a plurality of fins ( 35 ).
  • the first header collecting pipe ( 31 ), the second header collecting pipe ( 32 ), the flat tubes ( 33 ), and the fins ( 35 ) are all aluminum alloy members, and are attached to one another with solder.
  • Both of the first header collecting pipe ( 31 ) and the second header collecting pipe ( 32 ) are in an elongated hollow cylindrical shape, with both ends closed.
  • the first header collecting pipe ( 31 ) is provided upright at the left end of the heat exchanger ( 30 )
  • the second header collecting pipe ( 32 ) is provided upright at the right end of the heat exchanger ( 30 ).
  • the first header collecting pipe ( 31 ) and the second header collecting pipe ( 32 ) are provided such that their axial directions are vertical.
  • the flat tube ( 33 ) is a heat-transfer tube having a flat oblong cross section or a rectangular cross section with rounded corners.
  • the plurality of flat tubes ( 33 ) extend in a horizontal direction, and are arranged such that the flat surfaces thereof face each other. Further, the plurality of flat tubes ( 33 ) are arranged one above another with a predetermined space between the flat tubes ( 33 ).
  • One end of each of the flat tubes ( 33 ) is inserted in the first header collecting pipe ( 31 ), and the other end of the flat tube ( 33 ) is inserted in the second header collecting pipe ( 32 ).
  • Each fin ( 36 ) is in a plate-like shape, and the fins ( 36 ) are arranged in an extension direction of the flat tube ( 33 ) with a predetermined space between the fins ( 36 ). In other words, the fins ( 36 ) are arranged to be substantially orthogonal to the extension direction of the flat tube ( 33 ). As will be described in detail later, an area of each fin ( 36 ) which is located between vertically adjacent flat tubes ( 33 ) comprises an intermediate plate ( 70 ).
  • a space between vertically adjacent flat tubes ( 33 ) is divided into a plurality of air passages ( 40 ) by the intermediate plates ( 70 ) of the fins ( 36 ).
  • the refrigerant flowing in the fluid passages ( 34 ) of the flat tube ( 33 ) exchanges heat with the air flowing in the air passages ( 40 ).
  • each of the fins ( 36 ) is a vertically elongate plate-like fin formed by pressing a metal plate.
  • the thickness of each fin ( 36 ) is approximately 0.1 mm.
  • the fin ( 36 ) is provided with a plurality of elongate cutouts ( 45 ) each extending in a width direction (i.e., in an air passage direction) of the fin ( 36 ) from a leading edge ( 38 ) of the fin ( 36 ).
  • the plurality of cutouts ( 45 ) are formed in the fin ( 36 ) at predetermined intervals in a longitudinal direction (i.e., a vertical direction) of the fin ( 36 ).
  • a portion between the intermediate plates ( 70 ) of the fins ( 36 ) comprises a tube insertion portion ( 46 ).
  • the flat tube ( 33 ) is inserted in the tube insertion portion ( 46 ) from the open upwind side, and is held.
  • the width of the tube insertion portion ( 46 ) in the vertical direction is substantially equal to the width of the thickness of the flat tube ( 33 ), and the length of the tube insertion portion ( 46 ) is substantially equal to the width of the flat tube ( 33 ).
  • the flat tube ( 33 ) is inserted in the tube insertion portion ( 46 ) of the fin ( 36 ) from the leading edge ( 38 ) of the fin ( 36 ).
  • the flat tube ( 33 ) is attached to the periphery of the tube insertion portion ( 46 ) with solder. That is, the flat tube ( 33 ) is fitted to the periphery of the tube insertion portion ( 46 ) which is part of the cutout ( 45 ).
  • the fin ( 36 ) includes a plurality of intermediate plates ( 70 ) in areas between vertically adjacent flat tubes ( 33 ), a downwind plate ( 75 ) provided on the downwind side of the intermediate plates ( 70 ), and an upwind plate ( 77 ) provided on the upwind side of each of the plurality of intermediate plates ( 70 ).
  • the intermediate plates ( 70 ) divide the space between vertically adjacent flat tubes ( 33 ) into the air passages ( 40 ). That is, the intermediate plates ( 70 ) face the air passages ( 40 ).
  • the downwind plate ( 75 ) is continuous with the downwind ends of all the intermediate plates ( 70 ) arranged one above another.
  • Each of the upwind plate ( 77 ) projects from a middle portion in the vertical direction of the upwind end of each intermediate plate ( 70 ) toward the upwind side.
  • the height of each upwind plate ( 77 ) is smaller than the height of each intermediate plate ( 70 ), and the width of the upwind plate ( 77 ) is narrower than the width of the intermediate plate ( 70 ).
  • the fin ( 36 ) is provided with louvers ( 50 a , 50 b ) and protrusions ( 81 - 83 ).
  • the protrusions ( 81 - 83 ) are located upwind of the louvers ( 50 a , 50 b ).
  • the numbers of the protrusions ( 81 - 83 ) and the louvers ( 50 a , 50 b ) described below are merely examples.
  • the fin ( 36 ) is provided with three protrusions ( 81 - 83 ) in an upwind side area.
  • the three protrusions ( 81 - 83 ) are arranged side by side in the air passage direction (i.e., the direction from the leading edge ( 38 ) to the trailing edge ( 39 ) of the fin ( 36 )). That is, the fin ( 36 ) is provided with a first protrusion ( 81 ), a second protrusion ( 82 ), and a third protrusion ( 83 ) sequentially from the upwind side to the downwind side.
  • the first protrusion ( 81 ) lies across the upwind plate ( 77 ) and the intermediate plate ( 70 ), and the second protrusion ( 82 ) and the third protrusion ( 83 ) are provided on the intermediate plate ( 70 ).
  • Each of the protrusions ( 81 - 83 ) has an inverted V shape formed by making the fin ( 36 ) protrude toward the air passage ( 40 ).
  • the three protrusions ( 81 - 83 ) protrude to the same direction.
  • the protrusions ( 81 - 83 ) protrude to the right when viewed from the leading edge ( 38 ) of the fin ( 36 ).
  • Ridges ( 81 a , 82 a , 83 a ) of the protrusions ( 81 - 83 ) are substantially in parallel with the leading edge ( 38 ) of the fin ( 36 ). That is, the ridges ( 81 a , 82 a , 83 a ) of the protrusions ( 81 - 83 ) intersect with the airflow direction in the air passage ( 40 ).
  • the width W 1 of the first protrusion ( 81 ) in the air passage direction is smaller than the width W 2 of the second protrusion ( 82 ) in the air passage direction
  • the width W 3 of the third protrusion ( 83 ) is smaller than the width W 1 of the first protrusion ( 81 ) in the air passage direction (W 1 ⁇ W 2 ⁇ W 3 ).
  • the intermediate plate ( 70 ) of the fin ( 36 ) is provided with a group of louvers ( 50 a , 50 b ) at the downwind side of the protrusions ( 81 - 83 ).
  • the louvers ( 50 a , 50 b ) are obtained by giving a plurality of slit-like cuts in the intermediate plate ( 70 ) and plastically deforming a portion between adjacent cuts as if twisting the portion.
  • the longitudinal direction of each louver ( 50 a , 50 b ) is substantially parallel to the leading edge ( 38 ) of the fin ( 36 ) (i.e., the vertical direction). That is, the longitudinal direction of each louver ( 50 a , 50 b ) intersects with the air passage direction.
  • the lengths of the louvers ( 50 a , 50 b ) are equal to each other.
  • the louvers ( 50 a , 50 b ) are tilted with respect to their peripheral flat portions. Specifically, bent-out ends ( 53 a , 53 b ) on the upwind side of the louvers ( 50 a , 50 b ) protrude to the left when viewed from the leading edge ( 38 ) of the fin ( 36 ). On the other hand, bent-out ends ( 53 a , 53 b ) of the louvers ( 50 a , 50 b ) on the downwind side protrude to the right when viewed from the leading edge ( 38 ) of the fin ( 36 ).
  • each of the bent-out ends ( 53 a , 53 b ) of the louvers ( 50 a , 50 b ) includes a main edge ( 54 a , 54 b ), an upper edge ( 55 a , 55 b ), a lower edge ( 56 a , 56 b ).
  • the main edge ( 54 a , 54 b ) extends substantially in parallel with the leading edge ( 38 ) of the fin ( 36 ).
  • the upper edge ( 55 a , 55 b ) extends from the upper end of the main edge ( 54 a , 54 b ) to the upper end of the louver ( 50 a , 50 b ), and is tilted with respect to the main edge ( 54 a , 54 b ).
  • the lower edge ( 56 a , 56 b ) extends from the lower end of the main edge ( 54 a , 54 b ) to the lower end of the louver ( 50 a , 50 b ), and is tilted relative to the main edge ( 54 a , 54 b ).
  • a tilt angle ⁇ 2 of the lower edge ( 56 a ) with respect to the main edge ( 54 a ) is smaller than a tilt angle ⁇ 1 of the upper edge ( 55 a ) with respect to the main edge ( 54 a ) (i.e., ⁇ 2 ⁇ 1 ).
  • the lower edge ( 56 a ) is longer than the upper edge ( 55 a ).
  • the upwind side louver ( 50 a ) is an asymmetric louver in which the shape of the bent-out end ( 53 a ) is asymmetric in the vertical direction.
  • the louver ( 50 b ) is a symmetric louver in which the shape of the bent-out end ( 53 b ) is symmetric in the vertical direction.
  • one auxiliary protrusion ( 85 ) lies across the intermediate plate ( 70 ) and the downwind plate ( 75 ).
  • the auxiliary protrusion ( 85 ) has an inverted V shape formed by making the fin ( 36 ) protrude.
  • each auxiliary protrusion ( 85 ) protrudes to the right when viewed from the leading edge ( 38 ) of the fin ( 36 ).
  • the ridge ( 85 a ) of the auxiliary protrusion ( 85 ) is substantially in parallel with the leading edge ( 38 ) of the fin ( 36 ). That is, the ridge ( 85 a ) of the auxiliary protrusion ( 85 ) intersects with the airflow direction in the air passage ( 40 ).
  • the lower end of the auxiliary protrusion ( 85 ) is tilted downward toward the downwind side.
  • the width W 5 of the auxiliary protrusion ( 85 ) in the air passage direction is smaller than the width W 3 of the third protrusion ( 83 ) in the air passage direction (W 5 ⁇ W 3 ).
  • the downwind plate ( 75 ) of the fin ( 36 ) is provided with a vertically extending water-conducting rib ( 49 ), a plurality of downwind tabs ( 48 ) arranged in the vertical direction, and a plurality of downwind protrusions ( 84 ) each provided between vertically adjacent downwind tabs ( 48 ).
  • the water-conducting rib ( 49 ) is an elongated recessed groove extending vertically along the trailing edge ( 39 ) of the fin ( 36 ).
  • the water-conducting rib ( 49 ) extends from the upper end to the lower end of the downwind plate ( 75 ) of the fin ( 36 ).
  • Each of the downwind tabs ( 48 ) is a small rectangular piece formed by cutting and bending the fin ( 36 ).
  • the downwind tabs ( 48 ) keep a space between the fins ( 36 ), with the tips thereof being in contact with their adjacent fin ( 36 ).
  • Each downwind protrusion ( 84 ) has an inverted V shape formed by making the downwind plate ( 75 ) protrude.
  • each downwind protrusion ( 84 ) protrudes to the right when viewed from the leading edge ( 38 ) of the fin ( 36 ).
  • Ridges ( 84 a ) of the downwind protrusions ( 84 ) are substantially in parallel with the leading edge ( 38 ) of the fin ( 36 ). That is, the ridges ( 84 a ) of the downwind protrusions ( 84 ) intersect with the airflow direction in the air passage ( 40 ).
  • the fin ( 36 ) is provided with two horizontal ribs ( 91 , 92 ), and the above-described first protrusion ( 81 ) which lie across the upwind plate ( 77 ) and the intermediate plate ( 70 ).
  • the first protrusion ( 81 ) comprises an intermediate heat-transfer portion provided at a middle portion, in the vertical direction, of the upwind plate ( 77 ).
  • the first protrusion ( 81 ) comprises an upwind side heat-transfer portion which promotes heat transfer between the fin ( 36 ) and air on the upwind side of the intermediate plate ( 70 ).
  • the upper horizontal rib ( 91 ) is provided at an area on the upper side of the first protrusion ( 81 ) and the upwind tab ( 95 ), and the lower horizontal rib ( 92 ) is provided at an area on the lower side of the first protrusion ( 81 ) and the upwind tab ( 95 ).
  • the horizontal ribs ( 91 , 92 ) are comprised of raised lines which protrude toward the air passage ( 40 ). The direction to which the horizontal ribs ( 91 , 92 ) protrude is the same as the protrusion direction of the protrusions ( 81 , 82 , 83 , 84 ).
  • the upper horizontal rib ( 91 ) extends horizontally from the leading edge ( 38 ) of the fin ( 36 ) to an upper portion of the second protrusion ( 82 ).
  • the lower horizontal rib ( 92 ) extends horizontally from the leading edge ( 38 ) of the fin ( 36 ) to a lower portion of the second protrusion ( 82 ). That is, in the fin ( 36 ), the two horizontal ribs ( 91 , 92 ) extend linearly in the protruding direction of the upwind plates ( 77 ) (i.e., in the air passage direction).
  • the horizontal ribs ( 91 , 92 ) comprise reinforcing ribs which prevent the upwind plate ( 77 ) from being bent toward the air passage ( 40 ) with respect to the intermediate plate ( 70 ) of the fin ( 36 ).
  • the horizontal ribs ( 91 , 92 ) also comprise upwind side heat-transfer portions which promote heat transfer between the fin ( 36 ) and air on the upwind side of the intermediate plate ( 70 ).
  • the upwind tab ( 95 ) as a raised portion is provided on the front side of each of the upwind plates ( 77 ).
  • the upwind tab ( 95 ) comprises an intermediate heat-transfer portion provided at a middle portion, in the vertical direction, of the upwind plate ( 77 ).
  • the upwind tab ( 95 ) is a small rectangular piece formed by cutting and bending the fin ( 36 ) so as to protrude in a thickness direction of the fin ( 36 ).
  • the front surface of the upwind tab ( 95 ) is tilted obliquely downward with respect to the air passage direction (i.e., the horizontal direction).
  • an airflow resistance of the heat exchanger ( 30 ) can be reduced, compared to the case in which the front surface of the upwind tab ( 95 ) is vertical.
  • the upwind tab ( 95 ) keeps a space between the fins ( 36 ), with the tips thereof being in contact with the adjacent fin ( 36 ).
  • the upwind tab ( 95 ) also comprises an upwind side heat-transfer portion which promotes heat transfer between the fin ( 36 ) and air on the upwind side of the intermediate plate ( 70 ).
  • the outdoor heat exchanger ( 23 ) of the present embodiment functions as an evaporator in the heating operation.
  • the evaporation temperature of the refrigerant may sometimes be below 0° C., and frost may adhere to the surface of the fin ( 36 ).
  • the air before flowing into the air passage ( 40 ) is cooled/dehumidified by the upwind plates ( 77 ), thereby reducing the accumulation of frost on the inner side of the air passage ( 40 ).
  • the upwind tab ( 95 ), the first protrusion ( 81 ), and the horizontal ribs ( 91 , 92 ) comprise heat-transfer promotion portions which promote heat transfer between air and the upwind plates ( 77 ).
  • the intermediate plates ( 70 ) are relatively close to the flat tubes ( 33 ), and thus, the air flowing in the air passages ( 40 ) is cooled rapidly. However, this air has been dehumidified before flowing into the air passages ( 40 ), and therefore, the accumulation of frost on the surfaces of the intermediate plates ( 70 ) is reduced.
  • the upwind plates ( 77 ) extend from the intermediate plates ( 70 ) of the fin ( 36 ) toward the upwind side.
  • the air before flowing into the air passages ( 40 ) can be cooled and dehumidified.
  • each of the upwind plates ( 77 ) is provided with the upwind tab ( 95 ), the first protrusion ( 81 ), and the horizontal ribs ( 91 , 92 ), it is possible to promote heat transfer between the air and the upwind plates ( 77 ), and improve the effect of dehumidifying the air.
  • the accumulation of frost on the surfaces of the intermediate plates ( 70 ) is reduced.
  • the two horizontal ribs ( 91 , 92 ) provided on each of the upwind plates ( 77 ) prevent the upwind plates ( 77 ) from being bent in the horizontal direction with respect to the intermediate plate ( 70 ). Such bending of the upwind plates ( 77 ) can be further prevented by the upwind tab ( 95 ) whose tip is brought into contact with the adjacent fin ( 36 ).
  • any of the upwind tab ( 95 ), the first protrusion ( 81 ), and the two horizontal ribs ( 91 , 92 ) may be omitted.
  • each of the upwind plates ( 77 ) may be provided with the louvers ( 50 a , 50 b ) of the above embodiment, and the louvers ( 50 a , 50 b ) may be used as upwind side heat-transfer portions (raised portions).
  • the present invention is useful for a heat exchanger having a flat tube and a fin, and configured to exchange heat between a fluid flowing in the flat tube and air.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US13/980,584 2011-01-21 2012-01-23 Heat exchanger and air conditioner Abandoned US20130299152A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2011-011269 2011-01-21
JP2011011269 2011-01-21
PCT/JP2012/000392 WO2012098918A1 (ja) 2011-01-21 2012-01-23 熱交換器および空気調和機

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US13/980,655 Expired - Fee Related US9328973B2 (en) 2011-01-21 2012-01-23 Heat exchanger and air conditioner
US13/980,584 Abandoned US20130299152A1 (en) 2011-01-21 2012-01-23 Heat exchanger and air conditioner

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US (2) US9328973B2 (de)
EP (2) EP2653820A4 (de)
JP (2) JP5397489B2 (de)
KR (2) KR101451054B1 (de)
CN (2) CN103348211B (de)
AU (2) AU2012208124B2 (de)
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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US20180010857A1 (en) * 2015-03-31 2018-01-11 Gd Midea Heating & Ventilating Equipment Co., Ltd. Heat exchanger and multi-split system having same
US20180224210A1 (en) * 2017-02-03 2018-08-09 Samsung Electronics Co., Ltd. Heat exchanger and method of manufacturing the same
US20190120557A1 (en) * 2016-04-13 2019-04-25 Daikin Industries, Ltd. Heat exchanger
US10578375B2 (en) * 2015-09-21 2020-03-03 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Fin and heat exchanger having same

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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JP7457587B2 (ja) 2020-06-18 2024-03-28 三菱重工サーマルシステムズ株式会社 熱交換器、熱交換器ユニット、及び冷凍サイクル装置

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2428145A (en) * 1944-09-11 1947-09-30 Pacific Metals Company Ltd Heat transfer fin
US3309763A (en) * 1962-12-20 1967-03-21 Borg Warner Method for making a heat exchanger
US5207270A (en) * 1990-10-22 1993-05-04 Matsushita Electric Industrial Co., Ltd. Fin-tube heat exchanger
EP0769669A1 (de) * 1995-10-17 1997-04-23 Norsk Hydro Technology B.V. Wärmetauscher
US5642777A (en) * 1995-01-23 1997-07-01 Lg Electronics Inc. Fin tube heat exchanger
JP2000234883A (ja) * 1999-02-17 2000-08-29 Showa Alum Corp 熱交換器
US20020134537A1 (en) * 2001-02-07 2002-09-26 Stephen Memory Heat exchanger
WO2003046458A1 (fr) * 2001-11-27 2003-06-05 Valeo Thermique Moteur Ailette de module d'echange de chaleur
FR2872891A1 (fr) * 2004-07-12 2006-01-13 Valeo Thermique Moteur Sas Ailette de dispositif d'echange de chaleur a persiennes et lanieres
US7111670B2 (en) * 2002-12-25 2006-09-26 T. Rad Co., Ltd. Plate fin for heat exchanger and heat exchanger core
US7578339B2 (en) * 2003-05-23 2009-08-25 Mitsubishi Denki Kabushiki Kaisha Heat exchanger of plate fin and tube type
GB2466687A (en) * 2009-01-05 2010-07-07 Mitsubishi Electric Corp Heat exchanger and method of manufacturing a heat exchanger

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3167046A (en) * 1956-01-24 1965-01-26 Modine Mfg Co Method of forming a sheet metal fin strip element for heat exchange structures
FR1480185A (fr) * 1966-03-09 1967-05-12 Chausson Usines Sa Radiateur de chauffage pour véhicule
JPS4884947A (de) * 1972-02-16 1973-11-10
JPS60174495A (ja) * 1984-10-03 1985-09-07 Hitachi Ltd 空気調和機用熱交換器
JPH0271096A (ja) * 1988-09-05 1990-03-09 Matsushita Refrig Co Ltd フィン付熱交換器
JP2624336B2 (ja) * 1989-06-28 1997-06-25 松下冷機株式会社 フィン付熱交換器
JPH0363499A (ja) 1989-07-31 1991-03-19 Matsushita Refrig Co Ltd フィン付熱交換器
JP2735310B2 (ja) * 1989-09-08 1998-04-02 株式会社東芝 熱交換器
JPH0590173U (ja) * 1992-04-20 1993-12-07 住友軽金属工業株式会社 フィン・チューブ式熱交換器
JP3264525B2 (ja) * 1992-10-12 2002-03-11 東芝キヤリア株式会社 熱交換器
JPH06221787A (ja) * 1993-01-29 1994-08-12 Nippondenso Co Ltd 熱交換器
JPH06300474A (ja) 1993-04-12 1994-10-28 Daikin Ind Ltd フィン付熱交換器
JP3061537B2 (ja) * 1994-09-16 2000-07-10 アネスト岩田株式会社 湿式塗装室用塗料スラッジ捕集システム
JP3942210B2 (ja) 1996-04-16 2007-07-11 昭和電工株式会社 熱交換器、及びこの熱交換器を用いたルームエアコン並びにカーエアコン
US5752567A (en) * 1996-12-04 1998-05-19 York International Corporation Heat exchanger fin structure
JPH10339594A (ja) * 1997-06-09 1998-12-22 Toshiba Corp 熱交換器
JP2002031434A (ja) * 2000-07-19 2002-01-31 Fujitsu General Ltd 空気調和機の熱交換器
JP4096226B2 (ja) 2002-03-07 2008-06-04 三菱電機株式会社 フィンチューブ型熱交換器、その製造方法及び冷凍空調装置
JP2004251554A (ja) * 2003-02-20 2004-09-09 Matsushita Electric Ind Co Ltd ヒートポンプ用室外熱交換器
WO2005010442A1 (ja) * 2003-07-28 2005-02-03 Matsushita Electric Industrial Co., Ltd. 空気調和機
WO2006004137A1 (en) 2004-07-05 2006-01-12 Showa Denko K.K. Evaporator
JP2006170601A (ja) * 2004-07-05 2006-06-29 Showa Denko Kk エバポレータ
JP2006153327A (ja) * 2004-11-26 2006-06-15 Daikin Ind Ltd 熱交換器
JP2007232246A (ja) * 2006-02-28 2007-09-13 Denso Corp 熱交換器
JP5084304B2 (ja) * 2007-03-06 2012-11-28 三菱電機株式会社 フィンチューブ型熱交換器及び冷凍サイクル
JP4679542B2 (ja) * 2007-03-26 2011-04-27 三菱電機株式会社 フィンチューブ熱交換器、およびそれを用いた熱交換器ユニット並びに空気調和機
CN201141739Y (zh) * 2007-11-23 2008-10-29 北京龙源冷却技术有限公司 单排翅片管散热器
JP2009281693A (ja) * 2008-05-26 2009-12-03 Mitsubishi Electric Corp 熱交換器、その製造方法及びこの熱交換器を用いた空調冷凍装置
JP4845943B2 (ja) * 2008-08-26 2011-12-28 三菱電機株式会社 フィンチューブ型熱交換器および冷凍サイクル空調装置
CN201311227Y (zh) * 2008-11-14 2009-09-16 上虞市春晖风冷设备有限公司 一种冷风机散热翅片

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2428145A (en) * 1944-09-11 1947-09-30 Pacific Metals Company Ltd Heat transfer fin
US3309763A (en) * 1962-12-20 1967-03-21 Borg Warner Method for making a heat exchanger
US5207270A (en) * 1990-10-22 1993-05-04 Matsushita Electric Industrial Co., Ltd. Fin-tube heat exchanger
US5642777A (en) * 1995-01-23 1997-07-01 Lg Electronics Inc. Fin tube heat exchanger
EP0769669A1 (de) * 1995-10-17 1997-04-23 Norsk Hydro Technology B.V. Wärmetauscher
JP2000234883A (ja) * 1999-02-17 2000-08-29 Showa Alum Corp 熱交換器
US20020134537A1 (en) * 2001-02-07 2002-09-26 Stephen Memory Heat exchanger
US7032313B2 (en) * 2001-02-07 2006-04-25 Modine Manufacturing Company Method of fabricating a heat exchanger
WO2003046458A1 (fr) * 2001-11-27 2003-06-05 Valeo Thermique Moteur Ailette de module d'echange de chaleur
US7111670B2 (en) * 2002-12-25 2006-09-26 T. Rad Co., Ltd. Plate fin for heat exchanger and heat exchanger core
US7578339B2 (en) * 2003-05-23 2009-08-25 Mitsubishi Denki Kabushiki Kaisha Heat exchanger of plate fin and tube type
FR2872891A1 (fr) * 2004-07-12 2006-01-13 Valeo Thermique Moteur Sas Ailette de dispositif d'echange de chaleur a persiennes et lanieres
GB2466687A (en) * 2009-01-05 2010-07-07 Mitsubishi Electric Corp Heat exchanger and method of manufacturing a heat exchanger

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016010389A1 (ko) * 2014-07-17 2016-01-21 엘지전자 열교환기 및 그를 갖는 히트펌프
KR20160009974A (ko) * 2014-07-17 2016-01-27 엘지전자 주식회사 열교환기 및 그를 갖는 히트펌프
US20170198954A1 (en) * 2014-07-17 2017-07-13 Lg Electronics Inc. HEAT EXCHANGER AND HEAT PUMP HAVING THE SAME (As Amended)
US10126030B2 (en) * 2014-07-17 2018-11-13 Lg Electronics Inc. Heat exchanger and heat pump having the same
KR102203435B1 (ko) * 2014-07-17 2021-01-14 엘지전자 주식회사 열교환기 및 그를 갖는 히트펌프
US20180010857A1 (en) * 2015-03-31 2018-01-11 Gd Midea Heating & Ventilating Equipment Co., Ltd. Heat exchanger and multi-split system having same
US10578375B2 (en) * 2015-09-21 2020-03-03 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Fin and heat exchanger having same
US20190120557A1 (en) * 2016-04-13 2019-04-25 Daikin Industries, Ltd. Heat exchanger
US10801784B2 (en) * 2016-04-13 2020-10-13 Daikin Industries, Ltd. Heat exchanger with air flow passage for exchanging heat
US20180224210A1 (en) * 2017-02-03 2018-08-09 Samsung Electronics Co., Ltd. Heat exchanger and method of manufacturing the same
US11079180B2 (en) * 2017-02-03 2021-08-03 Samsung Electronics Co., Ltd. Heat exchanger and method of manufacturing the same

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JP2012163322A (ja) 2012-08-30
WO2012098920A1 (ja) 2012-07-26
AU2012208124A1 (en) 2013-08-01
AU2012208124B2 (en) 2015-05-14
KR101521371B1 (ko) 2015-05-19
JP5397489B2 (ja) 2014-01-22
CN103314267B (zh) 2015-09-30
WO2012098918A1 (ja) 2012-07-26
US20130306286A1 (en) 2013-11-21
JP2012163323A (ja) 2012-08-30
JP5196043B2 (ja) 2013-05-15
CN103314267A (zh) 2013-09-18
EP2653820A4 (de) 2015-03-11
AU2012208126A1 (en) 2013-08-01
CN103348211A (zh) 2013-10-09
EP2653820A1 (de) 2013-10-23
EP2667125A1 (de) 2013-11-27
KR101451054B1 (ko) 2014-10-15
KR20130124548A (ko) 2013-11-14
CN103348211B (zh) 2016-01-13
EP2667125A4 (de) 2015-03-04
EP2667125B1 (de) 2016-04-20
US9328973B2 (en) 2016-05-03
KR20130110221A (ko) 2013-10-08
AU2012208126B2 (en) 2015-07-02

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