US20130299152A1 - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
- 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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- Prior art keywords
- upwind
- heat exchanger
- heat
- air
- plates
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- 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.)
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Classifications
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- 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
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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
- 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
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- 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)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011011269 | 2011-01-21 | ||
JP2011-011269 | 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 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130299152A1 true US20130299152A1 (en) | 2013-11-14 |
Family
ID=46515551
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/980,584 Abandoned US20130299152A1 (en) | 2011-01-21 | 2012-01-23 | Heat exchanger and air conditioner |
US13/980,655 Expired - Fee Related US9328973B2 (en) | 2011-01-21 | 2012-01-23 | Heat exchanger and air conditioner |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/980,655 Expired - Fee Related US9328973B2 (en) | 2011-01-21 | 2012-01-23 | Heat exchanger and air conditioner |
Country Status (7)
Country | Link |
---|---|
US (2) | US20130299152A1 (de) |
EP (2) | EP2653820A4 (de) |
JP (2) | JP5196043B2 (de) |
KR (2) | KR101521371B1 (de) |
CN (2) | CN103314267B (de) |
AU (2) | AU2012208126B2 (de) |
WO (2) | WO2012098920A1 (de) |
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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 |
Also Published As
Publication number | Publication date |
---|---|
KR20130110221A (ko) | 2013-10-08 |
US9328973B2 (en) | 2016-05-03 |
CN103314267A (zh) | 2013-09-18 |
EP2667125A4 (de) | 2015-03-04 |
JP2012163323A (ja) | 2012-08-30 |
AU2012208126A1 (en) | 2013-08-01 |
EP2653820A4 (de) | 2015-03-11 |
JP2012163322A (ja) | 2012-08-30 |
JP5397489B2 (ja) | 2014-01-22 |
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AU2012208124A1 (en) | 2013-08-01 |
EP2667125B1 (de) | 2016-04-20 |
KR101451054B1 (ko) | 2014-10-15 |
WO2012098920A1 (ja) | 2012-07-26 |
JP5196043B2 (ja) | 2013-05-15 |
KR101521371B1 (ko) | 2015-05-19 |
CN103348211B (zh) | 2016-01-13 |
CN103348211A (zh) | 2013-10-09 |
US20130306286A1 (en) | 2013-11-21 |
AU2012208124B2 (en) | 2015-05-14 |
CN103314267B (zh) | 2015-09-30 |
WO2012098918A1 (ja) | 2012-07-26 |
EP2667125A1 (de) | 2013-11-27 |
KR20130124548A (ko) | 2013-11-14 |
AU2012208126B2 (en) | 2015-07-02 |
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