EP3550247B1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
EP3550247B1
EP3550247B1 EP16922957.2A EP16922957A EP3550247B1 EP 3550247 B1 EP3550247 B1 EP 3550247B1 EP 16922957 A EP16922957 A EP 16922957A EP 3550247 B1 EP3550247 B1 EP 3550247B1
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EP
European Patent Office
Prior art keywords
heat exchanger
fin
plate
corrugated
fins
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.)
Active
Application number
EP16922957.2A
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German (de)
English (en)
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EP3550247A4 (fr
EP3550247A1 (fr
Inventor
Hideaki Maeyama
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3550247A1 publication Critical patent/EP3550247A1/fr
Publication of EP3550247A4 publication Critical patent/EP3550247A4/fr
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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—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 being attachable to the 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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • 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
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present invention relates to heat exchangers and air conditioning apparatuses, and more particularly to a heat exchanger and an air conditioning apparatus including a corrugated fin.
  • a heat exchanger including a heat transfer tube having refrigerant flowing therethrough, and a corrugated fin connected to the heat transfer tube is conventionally known (see Japanese Patent Laying-Open No. 9-280754 , for example).
  • Document JP 2010 025462 A suggests improving the heat exchanging performance of a heat exchanger by providing a vertical draining guide plate in contact with corrugated fins for guiding condensed water to a drain pan disposed at a lower part of the heat exchanger.
  • the draining guide plate does at least not protrude more upstream in a direction of air flow than the corrugated fins for providing a drainage path without obstacles in a vertical direction.
  • measures are taken such as forming louvers in the corrugated fin or forming grooves in a surface of the heat transfer tube, in order to ensure drainage of condensation water formed on a surface of the corrugated fin.
  • measures it has been difficult to ensure sufficient drainage performance at the corrugated fin only by taking such measures.
  • An object of the present invention is to provide a heat exchanger with improved drainage performance at a corrugated fin.
  • a heat exchanger includes at least one heat transfer tube, a first plate fin, a second plate fin, a first corrugated fin, and a second corrugated fin.
  • the at least one heat transfer tube extends in a first direction intersecting a direction of air flow, and has refrigerant flowing therethrough.
  • the first plate fin extends in the first direction.
  • the first plate fin is spaced a first distance from the at least one heat transfer tube in a second direction perpendicular to the first direction.
  • the second plate fin extends in the first direction.
  • the second plate fin is spaced a second distance from the first plate fin in the second direction.
  • the first corrugated fin is disposed between the at least one heat transfer tube and the first plate fin.
  • the second corrugated fin is disposed between the first plate fin and the second plate fin.
  • the first plate fin and the first corrugated fin are connected to each other by a plurality of first connections spaced a third distance from one another in the first direction.
  • the first plate fin and the second corrugated fin are connected to each other by a plurality of second connections spaced a fourth distance from one another in the first direction.
  • the third distance and the fourth distance are greater than the first distance and the second distance.
  • the direction of air flow is a direction perpendicular to the first direction and the second direction and a width of each of the first and second plate fins is greater than a width of each of the first and second corrugated fins in the direction of air flow.
  • a portion of each of the first and second plate fins protrudes more upstream in the direction of air flow than the first and second corrugated fins.
  • An air conditioning apparatus includes a refrigerant circuit, the refrigerant circuit including a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, and having refrigerant circulating therethrough. At least one of the first heat exchanger and the second heat exchanger is the heat exchanger described above.
  • the angle of inclination of an inclined portion located between the first or second connections in the first and second corrugated fins can be increased, so that the drainage of condensation water through this inclined portion can be improved.
  • Fig. 1 is a schematic diagram of a heat exchanger according to a first embodiment of the present invention.
  • Fig. 2 is a schematic partial enlarged perspective view of a region II in Fig. 1 .
  • Fig. 3 is a schematic front view of the portion of the heat exchanger shown in Fig. 2 .
  • a heat exchanger 1 shown in Figs. 1 to 3 includes a plurality of heat transfer tubes 11 which are flat tubes, a plurality of plate fins 12 disposed between these heat transfer tubes 11, corrugated fins 13 disposed between heat transfer tubes 11 and plate fins 12 or between adjacent plate fins 12, and an upper header 2 and a lower header 3 connected respectively to the upper ends and the lower ends of heat transfer tubes 11 disposed along the direction of gravity.
  • Heat transfer tubes 11, plate fins 12 and corrugated fins 13 form a main body portion 10.
  • Heat transfer tube 11 is provided to extend along a first direction, which is a direction along the direction of gravity. Refrigerant flows through heat transfer tube 11.
  • a plurality of refrigerant flow paths may be formed along a direction in which heat transfer tube 11 extends (first direction).
  • the plurality of heat transfer tubes 11 are spaced from one another in a second direction indicated by an arrow 16 and intersecting the first direction, so as to have a prescribed pitch P1 as shown in Fig. 3 .
  • first to third plate fins 12a to 12c are disposed between adjacent heat transfer tubes 11.
  • First to fourth corrugated fins 13a to 13d are disposed between heat transfer tubes 11 and first to third plate fins 12a to 12c.
  • the configurations between adjacent heat transfer tubes 11 are basically identical.
  • heat exchanger 1 includes at least one heat transfer tube 11, first plate fin 12a, second plate fin 12b, third plate fin 12c, first corrugated fin 13a, second corrugated fin 13b, and third and fourth corrugated fins 13c, 13d.
  • At least one heat transfer tube 11 extends in the first direction indicated by an arrow 15 and intersecting a direction of air flow. Refrigerant flows through heat transfer tube 11.
  • First plate fin 12a extends in the first direction indicated by arrow 15.
  • First plate fin 12a is spaced a first distance P21 from at least one heat transfer tube 11 in the second direction indicated by arrow 16 and perpendicular to the first direction.
  • Second plate fin 12b extends in the first direction.
  • Second plate fin 12b is spaced a second distance P22 from first plate fin 12a in the second direction indicated by arrow 16.
  • a distance between second plate fin 12b and third plate fin 12c in the second direction may be equal to or different from aforementioned second distance P22.
  • a distance between heat transfer tube 11 adjacent to third plate fin 12c and this third plate fin 12c may be equal to or different from aforementioned first distance P21.
  • Aforementioned first distance P21 and second distance P22 may be equal to or different from each other.
  • First corrugated fin 13a is disposed between at least one heat transfer tube 11 and first plate fin 12a.
  • Second corrugated fin 13b is disposed between first plate fin 12a and second plate fin 12b.
  • Third corrugated fin 13c is disposed between second plate fin 12b and third plate fin 12c.
  • Fourth corrugated fin 13d is disposed between third plate fin 12c and another heat transfer tube 11.
  • First plate fin 12a and first corrugated fin 13a are connected to each other by a plurality of first connections 24 spaced a third distance P3 from one another in the first direction indicated by arrow 15.
  • First plate fin 12a and second corrugated fin 13b are connected to each other by a plurality of second connections 25 spaced a fourth distance P4 from one another in the first direction indicated by arrow 15.
  • First corrugated fin 13a and heat transfer tube 11 are connected to each other by a plurality of connections spaced from one another along the first direction. The distance between these connections may be equal to aforementioned third distance P3.
  • Second corrugated fin 13b and second plate fin 12b are connected to each other by a plurality of connections spaced from one another along the first direction. The distance between these connections may be equal to aforementioned fourth distance P4.
  • Aforementioned third distance P3 and fourth distance P4 may be equal to or different from each other.
  • Connections between third and fourth corrugated fins 13c, 13d, and second and third plate fins 12b, 12c and another heat transfer tube 11 are basically similar in configuration to the connections between first corrugated fin 13a, and heat transfer tube 11 and first plate fin 12a described above.
  • Aforementioned third distance P3 and fourth distance P4 are greater than first distance P21 and second distance P22.
  • the distance in the first direction between the plurality of connections where corrugated fin 13 is connected to plate fin 12 is greater than the width of space between heat transfer tube 11 and the plurality of plate fins 12 in the second direction. Louvers may be formed in inclined portions 33, 34 of first to fourth corrugated fins 13a to 13d.
  • the hydrophilicity of at least a portion of the surfaces of first plate fin 12a, second plate fin 12b, third plate fin 12c, and at least one heat transfer tube 11 may be higher than the hydrophilicity of the surfaces of first corrugated fin 13a, second corrugated fin 13b, and third and fourth corrugated fins 13c, 13d.
  • the hydrophilicities of the surfaces of plate fin 12, corrugated fin 13, and heat transfer tube 11 can be adjusted by any method, such as changing the materials for these members, forming surface treatment layers having different hydrophilicities on these surfaces, or changing the surface roughnesses of these surfaces.
  • the surface roughness of plate fin 12 and heat transfer tube 11 may be greater than the surface roughness of corrugated fin 13.
  • a hydrophilic or hydrophobic surface treatment layer may be formed either on plate fin 12 and heat transfer tube 11, or on corrugated fin 13.
  • a thickness W of at least one heat transfer tube 11 may be greater than the thickness of each of first to third plate fins 12a to 12c in the second direction indicated by arrow 16 in Fig. 3 .
  • the thickness of each of first to third plate fins 12a to 12c may be greater than the thickness of each of first to fourth corrugated fins 13a to 13d.
  • the plurality of first connections 24 coincide in position with the plurality of second connections 25 in the first direction indicated by arrow 15.
  • the plurality of first connections 24 coinciding in position with the plurality of second connections 25 means that each of first connections 24 at least partially overlaps with each of second connections 25 when viewed from the second direction.
  • third distance P3 and fourth distance P4 which are the pitches of the plurality of connections 24, 25 where first and second corrugated fins 13a, 13b are connected to first plate fin 12a, respectively, are greater than first and second distances P21, P22, which are the widths of regions where first and second corrugated fins 13a, 13b are disposed, respectively.
  • the pitches of the plurality of connections where the third and fourth corrugated fins are connected to plate fin 12, respectively are greater than aforementioned first and second distances P21, P22. Accordingly, inclined portions 33, 34 of first and second corrugated fins 13a, 13b located between these connections 24 and 25, and also the inclined portions of third and fourth corrugated fins 13c, 13d can be sufficiently inclined relative to the first direction.
  • the angle of inclination of these inclined portions 33, 34 relative to the first direction may be 70° or less (stated from a different perspective, the angle of inclination of inclined portions 33, 34 relative to the second direction may be 20° or more).
  • the angle of inclination of these inclined portions 33, 34 relative to the first direction may be 60° or less, 50° or less, or 45° or less.
  • the angle of inclination of inclined portions 33, 34 relative to the second direction may be 30° or more, 40° or more, or 45° or more.
  • the hydrophilicity of at least a portion of the surfaces of first plate fin 12a, second plate fin 12b, and at least one heat transfer tube 11 is higher than the hydrophilicity of the surfaces of first corrugated fin 13a and second corrugated fin 13b. Accordingly, condensation water can be readily moved from the surfaces of first and second corrugated fins 13a, 13b to the surfaces of first and second plate fins 12a, 12b or the surface of heat transfer tube 11. Then, the condensation water that has moved to first and second plate fins 12a, 12b or heat transfer tube 11 can be readily moved in a vertically downward direction, for example. Accordingly, the drainage performance at the heat exchanger can be improved.
  • thickness W of at least one heat transfer tube 11 is greater than the thickness of each of first and second plate fins 12a, 12b in the second direction indicated by arrow 16 in Fig. 3 .
  • the thickness of each of first and second plate fins 12a, 12b is greater than the thickness of each of first and second corrugated fins 13a, 13b.
  • the thickness of each of first to third plate fins 12a to 12c is greater than the thickness of each of first to fourth corrugated fins 13a to 13d together forming corrugated fin 13. Since the thickness of plate fin 12 is greater than the thickness of corrugated fin 13 in this manner, the strength of plate fin 12 can be increased to stabilize the shape of the heat exchanger.
  • the plurality of first connections 24 coincide in position with the plurality of second connections 25 in the first direction.
  • the connections between second corrugated fin 13b and second plate fin 12b also coincide in position with the connections between third corrugated fin 13c and second plate fin 12b in the first direction, second corrugated fin 13b and third corrugated fin 13c being disposed to sandwich the plate fin therebetween.
  • the connections between third corrugated fin 13c and third plate fin 12c also coincide in position with the connections between fourth corrugated fin 13d and third plate fin 12c in the first direction, third corrugated fin 13c and fourth corrugated fin 13d being disposed to sandwich the plate fin therebetween.
  • the connections coincide in position at the front and rear surfaces of plate fin 12, so that the shape of plate fin 12 can be stabilized as compared to an example where these connections differ in position between the front and rear surfaces.
  • Fig. 4 is a schematic partial sectional view of a heat exchanger according to a second embodiment of the present invention.
  • Fig. 4 corresponds to a schematic partial sectional view of the heat exchanger taken along a plane perpendicular to the first direction shown in Fig. 3 .
  • the heat exchanger shown in Fig. 4 basically has a similar configuration to the heat exchanger shown in Figs. 1 to 3 , but is different from the heat exchanger shown in Figs. 1 to 3 in the shapes of first to third plate fins 12a to 12c and first to fourth corrugated fins 13a to 13d. Specifically, in the direction of air flow indicated by an arrow 22, a width L2 of each of first to fourth corrugated fins 13a to 13d is greater than a width L1 of heat transfer tube 11. In addition, first to fourth corrugated fins 13a to 13d each include a portion 27 protruding more upstream in the direction of air flow than heat transfer tube 11.
  • a width L3 of each of first to third plate fins 12a to 12c is greater than width L2 of each of first to fourth corrugated fins 13a to 13d.
  • First to third plate fins 12a to 12c include portions 26 protruding more upstream in the direction of air flow than first to fourth corrugated fins 13a to 13d.
  • the configuration of the heat exchanger described above is such that, in heat exchanger 1 described above, the direction of air flow is a direction perpendicular to the first direction and the second direction, and is a direction indicated by arrow 22 in Fig. 4 .
  • width L3 of each of first and second plate fins 12a, 12b is greater than width L2 of each of first and second corrugated fins 13a, 13b.
  • width L3 of each of first to third plate fins 12a to 12c, which are a plurality of plate fins disposed between two heat transfer tubes 11, is greater than width L2 of each of first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins disposed adjacent to these plurality of plate fins.
  • first and second plate fins 12a, 12b protrude more upstream in the direction of air flow than first and second corrugated fins 13a, 13b.
  • Third plate fin 12c similarly includes portion 26. That is, portions 26 of first to third plate fins 12a to 12c, which are a plurality of plate fins, protrude more upstream in the direction of air flow than first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins.
  • portions 27 of first and second corrugated fins 13a, 13b protrude more upstream in the direction of air flow than at least one heat transfer tube 11.
  • portions 27 of first to fourth corrugated fins 13a to 13d which are a plurality of corrugated fins, protrude more upstream than at least one heat transfer tube 11.
  • louvers 23 are formed in first to fourth corrugated fins 13a to 13d. Louvers 23 are formed in inclined portions 33, 34 (see Fig. 3 ) of first to fourth corrugated fins 13a to 13d. Louvers 23 are formed to extend linearly in a direction intersecting the direction of air flow, specifically a direction perpendicular to the direction of air flow. Louvers 23 are linear, but may be curved, in plan view. Louvers 23 may be formed by, for example, cutting into inclined portions 33, 34 of first to fourth corrugated fins 13a to 13d, and causing portions of inclined portions 33, 34 that are adjacent to these cuts to be inclined relative to the other portions. Alternatively, slits as simple openings may be formed instead of louvers 23.
  • heat exchanger 1 serves as an evaporator.
  • low-temperature refrigerant flows through the refrigerant flow paths formed within heat transfer tube 11.
  • heat is transferred successively through heat transfer tube 11, first corrugated fin 13a joined to heat transfer tube 11, plate fin 12a joined to first corrugated fin 13a, second corrugated fin 13b joined to plate fin 12a, and second plate fin 12b joined to second corrugated fin 13b. Since the low-temperature refrigerant is flowing through heat transfer tube 11 as described above, the surface temperature of the heat exchanger increases as the distance from heat transfer tube 11 increases.
  • Condensation water mostly adheres to a corrugated fin in a conventional heat exchanger, whereas the heat exchanger according to the present embodiment can allow most of the condensation water to adhere to first to third plate fins 12a to 12c.
  • First to third plate fins 12a to 12c each have portion 26 protruding more windward than first to fourth corrugated fins 13a to 13d. Since there are no obstacles below these portions 26, the condensed moisture flows over the surfaces of portions 26 of first to third plate fins 12a to 12c and drops downward in a short time.
  • the condensation water (moisture) formed on first to fourth corrugated fins 13a to 13d is directed downward by louvers 23 formed in first to fourth corrugated fins 13a to 13d, and drops downward along the shape of the corrugated fins.
  • louvers 23 formed in first to fourth corrugated fins 13a to 13d
  • the inclination of a surface portion of the corrugated fin where a louver is formed relative to the first direction is relatively small, which sometimes hinders the condensation water from moving sufficiently along the corrugated fin.
  • it is ensured that inclined portions 33, 34 of first to fourth corrugated fins 13a to 13d are inclined 20° or more, for example, relative to the second direction. Accordingly, the condensation water can be readily moved downward along these inclined portions 33, 34.
  • Heat exchanger 1 described above can produce similar effects to the heat exchanger in the first embodiment. Moreover, in heat exchanger 1 described above, width L3 of each of first to third plate fins 12a to 12c, which are a plurality of plate fins disposed between two heat transfer tubes 11, is greater than width L2 of each of first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins disposed adjacent to these plurality of plate fins.
  • first to third plate fins 12a to 12c include portions 26 protruding from first to fourth corrugated fins 13a to 13d in the direction of air flow indicated by arrow 22. These protruding portions 26 extend along the first direction, and can function as a drainage path for the condensation water from first to fourth corrugated fins 13a to 13d.
  • the condensation water adheres early to portions 26 of first to third plate fins 12a to 12c protruding upstream in the direction of air flow. Subsequently, the condensation water can be quickly moved to the space below first and second plate fins 12a, 12b through aforementioned portions 26 of first and second plate fins 12a, 12b.
  • Fig. 5 is a schematic partial sectional view of a heat exchanger according to a third embodiment of the present invention.
  • Fig. 6 is a schematic partial perspective view of the heat exchanger shown in Fig. 5 .
  • Fig. 7 is a schematic partial top view of the heat exchanger shown in Fig. 6 .
  • the heat exchanger shown in Figs. 5 to 7 basically has a similar configuration to the heat exchanger shown in Fig. 4 , but is different from the heat exchanger shown in Fig. 4 in that a plate member 14 is connected to heat transfer tube 11 on the upstream side in the direction of air flow, as well as in the disposition of louvers 23.
  • plate member 14 is disposed to be connected to an end 28 of heat transfer tube 11 on the windward side, which is the upstream side in the direction of air flow.
  • Plate member 14 may be a hollow member or a solid member.
  • the width of plate member 14 in the second direction (the direction indicated by arrow 16 in Fig.
  • a combined width of heat transfer tube 11 and plate member 14 in the direction of air flow is equal to width L3 of each of first to third plate fins 12a to 12c.
  • the combined width of heat transfer tube 11 and plate member 14 may be different from width L3 of each of first to third plate fins 12a to 12c, and may be equal to width L2 of each of first to fourth corrugated fins 13a to 13d, for example.
  • First to fourth corrugated fins 13a to 13d include inclined portions 33, 34.
  • the plurality of louvers 23 are formed in these inclined portions 33, 34.
  • Inclined portions 33, 34 are inclined relative to the first direction corresponding to the vertical direction.
  • the plurality of linearly extending louvers 23 are formed in inclined portions 33, 34.
  • the plurality of louvers 23 are formed to extend vertically downward toward the upstream side in the direction of air flow indicated by arrow 22.
  • louvers 23 in inclined portions 33 are each formed to approach a protrusion vertex 36 from connection 25 toward the upstream side in the direction of air flow.
  • the louvers in inclined portions 34 are each formed to approach connection 25 from protrusion vertex 36 toward the upstream side in the direction of air flow.
  • First corrugated fin 13a includes first inclined portions 33, 34 located between the plurality of first connections 24 (see Fig. 3 ) and inclined relative to the vertical direction.
  • Second corrugated fin 13b includes second inclined portions 33, 34 located between the plurality of second connections 25 and inclined relative to the vertical direction.
  • At least one linearly extending louver 23 is formed in at least one of first inclined portions and second inclined portions 33, 34. At least one louver 23 is formed to extend vertically downward toward the upstream side in the direction of air flow indicated by arrow 22.
  • louvers 23 are formed in all of inclined portions 33, 34 of first to fourth corrugated fins 13a to 13d, they may be formed only in some of inclined portions 33, 34. Alternatively, they may be formed in some of first to fourth corrugated fins 13a to 13d.
  • Heat exchanger 1 described above can produce similar effects to the heat exchanger in the second embodiment.
  • heat exchanger 1 described above further includes plate member 14 connected to a portion of at least one heat transfer tube 11 that is located upstream in the direction of air flow.
  • the connection of such plate member 14 to heat transfer tube 11 can cause frost, which conventionally adheres to heat transfer tube 11, to adhere to plate member 14 in a distributed manner. Accordingly, the amount of frost formed at heat transfer tube 11 can be reduced, so that the drainage performance of heat transfer tube 11 can be improved.
  • louvers 23 in the heat exchanger shown in Figs. 5 to 7 are formed to extend vertically downward toward the upstream side in the direction of air flow, the condensation water that has adhered to the surfaces of the corrugated fins can be directed through these louvers 23 to the upstream side in the direction of air flow. Since portions 26 of first to third plate fins 12a to 12c are disposed on this upstream side, these portions 26 can be utilized as drainage paths to improve the drainage performance of the heat exchanger.
  • Fig. 8 is a schematic diagram showing a refrigerant circuit of an air conditioning apparatus according to a fourth embodiment of the present invention.
  • the refrigerant circuit shown in Fig. 8 includes a compressor 41, a first heat exchanger 42 serving as a condenser, a throttle device 43 serving as an expansion valve, a second heat exchanger 44 serving as an evaporator, and two blowers 45.
  • Two blowers 45 are driven by blower motors 46, respectively.
  • Two blowers 45 blow gas (for example, air) at first heat exchanger 42 and second heat exchanger 44, respectively.
  • refrigerant circulates successively through compressor 41, first heat exchanger 42, throttle device 43, and second heat exchanger 44.
  • the air conditioning apparatus shown in Fig. 8 includes a refrigerant circuit, the refrigerant circuit including compressor 41, first heat exchanger 42, throttle device 43 as an expansion valve, and second heat exchanger 44, and having refrigerant circulating therethrough.
  • At least one of first heat exchanger 42 and second heat exchanger 44 shown in Fig. 8 is the heat exchanger described in any one of the first to third embodiments.
  • Aforementioned blowers 45 each blow the gas at its corresponding heat exchanger along a third direction (the direction indicated by arrow 22 in Fig. 4 ).
  • a four-way valve or the like may be disposed in the refrigerant circuit, to reverse the direction in which the refrigerant flows at first heat exchanger 42 and second heat exchanger 44 in the refrigerant circuit from the direction shown in Fig. 8 , to thereby cause the first heat exchanger to serve as an evaporator and the second heat exchanger to serve as a condenser.
  • the air conditioning apparatus includes the heat exchanger according to any one of the first to third embodiments described above as its heat exchanger, and thus has sufficient drainage performance. Accordingly, lowering of efficiency or the occurrence of a fault caused by insufficient drainage of the condensation water at first and second heat exchangers 42, 44 can be suppressed.
  • the present invention is applicable to an air conditioning apparatus, a refrigeration cycle apparatus, a heat pump apparatus and the like.

Claims (8)

  1. Échangeur thermique (1) comprenant :
    au moins un tube de transfert thermique (11) s'étendant dans une première direction croisant une direction de flux d'air, et comprenant un réfrigérant s'écoulant à travers celui-ci ;
    une première ailette plate (12a) s'étendant dans la première direction et espacée d'une première distance par rapport à l'au moins un tube de transfert thermique (11) dans une deuxième direction perpendiculaire à la première direction ;
    une deuxième ailette plate (12b) s'étendant dans la première direction et espacée d'une deuxième distance par rapport à la première ailette plate (12a) dans la deuxième direction ;
    une première ailette ondulée (13a) disposée entre l'au moins un tube de transfert thermique (11) et la première ailette plate (12a) ; et
    une deuxième ailette ondulée (13b) disposée entre la première ailette plate (12a) et la deuxième ailette plate (12b),
    la première ailette plate (12a) et la première ailette ondulée (13a) étant reliées entre elles par une pluralité de premières connexions (24) espacées d'une troisième distance entre elles dans la première direction,
    la première ailette plate (12a) et la deuxième ailette ondulée (13b) étant reliées entre elles par une pluralité de deuxièmes connexion (25) espacées d'une quatrième distance entre elles dans la première direction,
    la troisième distance et la quatrième distance étant supérieures à la première distance et la deuxième distance,
    la direction du flux d'air est une direction perpendiculaire à la première direction et la deuxième direction et
    une largeur de chacune des première et deuxième ailettes plates (12a, 12b) est supérieure à une largeur de chacune des première et deuxième ailettes ondulées (13a, 13b) dans la direction du flux d'air,
    une portion (26) de chacune des première et deuxième ailettes plates (12a, 12b) dépasse plus en amont dans la direction du flux d'air que les première et deuxième ailettes ondulées (13a, 13b).
  2. Échangeur thermique (1) selon la revendication 1, dans lequel
    une portion (27) de chacune des première et deuxième ailettes ondulées (13a, 13b) dépasse plus en amont dans la direction du flux d'air que l'au moins un tube de transfert thermique (11).
  3. Échangeur thermique (1) selon la revendication 1 ou 2, comprenant en outre un élément de plaque (14) relié à une portion de l'au moins un tube de transfert thermique (11) qui est située en amont dans la direction du flux d'air.
  4. Échangeur thermique (1) selon l'une des revendications 1 à 3, dans lequel la première direction est une direction le long de la direction de la gravité,
    la première ailette ondulée (13a) comprend une première portion inclinée (33, 34) située entre la pluralité de premières connexions (24) et inclinée par rapport à une direction verticale,
    la deuxième ailette ondulée (13b) comprend une deuxième portion inclinée (33, 34) située entre la pluralité de deuxièmes connexions (25) et inclinée par rapport à la direction verticale,
    au moins une lame (23) s'étendant de manière linéaire est formée dans au moins une parmi la première portion inclinée (33, 34) et la deuxième portion inclinée (33, 34) et
    l'au moins une lame (23) est formée de façon à s'étendre vers le bas dans la direction verticale vers le côté amont dans la direction du flux d'air.
  5. Échangeur thermique (1) selon l'une des revendications 1 à 4, dans lequel la propriété hydrophobe d'au moins une portion des surfaces de la première ailette plate (12a), de la
    deuxième ailette plate (12b) et de l'au moins un tube de transfert thermique (11) est supérieure à la propriété hydrophobe des surfaces de la première ailette ondulée (13a) et de la deuxième ailette ondulée (13b).
  6. Échangeur thermique (1) selon l'une des revendications 1 à 5, dans lequel
    une épaisseur de l'au moins un tube de transfert thermique (11) est supérieure à une épaisseur de chacune des première et deuxième ailettes plates (12a, 12b) dans la deuxième direction et
    l'épaisseur de chacune des première et deuxième ailettes plates (12a, 12b) est supérieure à une épaisseur de chacune des première et deuxième ailettes ondulées (13a, 13b).
  7. Échangeur thermique (1) selon l'une des revendications 1 à 6, dans lequel
    la pluralité de premières connexions (24) coïncident, en ce qui concerne la position, avec la pluralité de deuxièmes connexions (25) dans la première direction.
  8. Appareil de climatisation comprenant un circuit réfrigérant,
    le circuit réfrigérant comprenant un compresseur (41), un premier échangeur thermique (42), une soupape d'expansion (43) et un deuxième échangeur thermique (44) et comprenant un réfrigérant circulant à travers celui-ci,
    au moins un parmi le premier échangeur thermique (42) et le deuxième échangeur thermique (44) étant l'échangeur thermique selon l'une des revendications 1 à 7.
EP16922957.2A 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur Active EP3550247B1 (fr)

Applications Claiming Priority (1)

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PCT/JP2016/085941 WO2018100738A1 (fr) 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur

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CN111380395A (zh) * 2018-12-28 2020-07-07 丹佛斯有限公司 换热器
JP7292510B2 (ja) * 2020-05-22 2023-06-16 三菱電機株式会社 熱交換器及び空気調和機

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JPH11108576A (ja) * 1997-10-02 1999-04-23 Nippon Light Metal Co Ltd 熱交換器
JP2000234892A (ja) * 1999-02-12 2000-08-29 Zexel Corp 熱交換器の縮小方法及びこの方法により製造される熱交換器
JP2003336988A (ja) * 2002-05-20 2003-11-28 Japan Climate Systems Corp 熱交換器
JP2004150710A (ja) * 2002-10-30 2004-05-27 Denso Corp 冷媒蒸発器およびその製造方法
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
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JP2010025462A (ja) * 2008-07-22 2010-02-04 Nippon Light Metal Co Ltd 熱交換器
JP2010054115A (ja) * 2008-08-28 2010-03-11 Calsonic Kansei Corp エバポレータ
JP4503682B1 (ja) * 2009-04-22 2010-07-14 シャープ株式会社 熱交換器及びそれを搭載した空気調和機
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JP2013250016A (ja) * 2012-06-01 2013-12-12 Panasonic Corp フィンチューブ熱交換器
JP6289729B2 (ja) * 2015-03-02 2018-03-07 三菱電機株式会社 フィンアンドチューブ型熱交換器及びこれを備えた冷凍サイクル装置
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JPWO2018100738A1 (ja) 2019-10-17
EP3550247A4 (fr) 2019-12-18
EP3550247A1 (fr) 2019-10-09
WO2018100738A1 (fr) 2018-06-07
JP6997722B2 (ja) 2022-01-18

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