WO2018100738A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

Info

Publication number
WO2018100738A1
WO2018100738A1 PCT/JP2016/085941 JP2016085941W WO2018100738A1 WO 2018100738 A1 WO2018100738 A1 WO 2018100738A1 JP 2016085941 W JP2016085941 W JP 2016085941W WO 2018100738 A1 WO2018100738 A1 WO 2018100738A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
plate
fin
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.)
Ceased
Application number
PCT/JP2016/085941
Other languages
English (en)
Japanese (ja)
Inventor
英明 前山
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2018553624A priority Critical patent/JP6997722B2/ja
Priority to EP16922957.2A priority patent/EP3550247B1/fr
Priority to PCT/JP2016/085941 priority patent/WO2018100738A1/fr
Publication of WO2018100738A1 publication Critical patent/WO2018100738A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • 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 a heat exchanger and an air conditioner, and more particularly to a heat exchanger and an air conditioner including corrugated fins.
  • a heat exchanger that includes a heat transfer tube through which a refrigerant flows and a corrugated fin connected to the heat transfer tube (see, for example, Japanese Patent Application Laid-Open No. 9-280754).
  • An object of the present invention is to provide a heat exchanger with improved drainage in a corrugated fin.
  • the 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 the air flow direction, and the refrigerant flows therein.
  • the first plate fin extends in the first direction.
  • the first plate fin is arranged at a first interval from 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 disposed at a second interval 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 by a plurality of first connection portions arranged at a third interval in the first direction.
  • the first plate fin and the second corrugated fin are connected by a plurality of second connection portions arranged at a fourth interval in the first direction.
  • the third interval and the fourth interval are larger than the first interval and the second interval.
  • the air conditioner according to the present disclosure includes a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, and includes a refrigerant circuit in which the refrigerant circulates. At least one of the first heat exchanger and the second heat exchanger is the heat exchanger.
  • FIG. 1 It is a schematic diagram of the heat exchanger which concerns on Embodiment 1 of this invention. It is a partial expansion perspective schematic diagram in the area
  • FIG. 1 is a schematic diagram of a heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 2 is a partially enlarged perspective schematic view of region II in FIG.
  • FIG. 3 is a schematic front view of a portion of the heat exchanger shown in FIG.
  • the heat exchanger 1 shown in FIGS. 1 to 3 includes a plurality of heat transfer tubes 11 that are flat tubes, a plurality of plate fins 12 disposed between the heat transfer tubes 11, and the heat transfer tubes 11 and the plate fins 12.
  • a corrugated fin 13 disposed between or between adjacent plate fins 12, and an upper header 2 and a lower header 3 respectively connected to an upper end and a lower end of a heat transfer tube 11 disposed along the direction of gravity.
  • the main body 10 is constituted by the heat transfer tube 11, the plate fin 12 and the corrugated fin 13.
  • the heat transfer tube 11 is provided so as to extend along a first direction that is a direction along the direction of gravity.
  • a refrigerant circulates inside the heat transfer tube 11. Inside the heat transfer tube 11 having a flat tubular shape, a number of refrigerant flow paths may be formed along the extending direction (first direction).
  • the plurality of heat transfer tubes 11 are arranged at intervals in a second direction indicated by an arrow 16 which is a direction intersecting the first direction so as to have a predetermined pitch P1 as shown in FIG.
  • first to third plate fins 12 a to 12 c are arranged between adjacent heat transfer tubes 11.
  • first to fourth corrugated fins 13a to 13d are arranged.
  • the configuration between adjacent heat transfer tubes 11 is basically the same.
  • the heat exchanger 1 includes at least one heat transfer tube 11, a first plate fin 12a, a second plate fin 12b, and a third plate fin 12c.
  • At least one heat transfer tube 11 extends in a first direction indicated by an arrow 15 that intersects the air flow direction.
  • a refrigerant circulates inside the heat transfer tube 11.
  • the first plate fin 12 a extends in the first direction indicated by the arrow 15.
  • the first plate fins 12a are arranged with at least one heat transfer tube 11 and a first interval P21 in a second direction indicated by an arrow 16 perpendicular to the first direction.
  • the second plate fin 12b extends in the first direction.
  • the second plate fins 12b are arranged at a second interval P22 from the first plate fins 12a in the second direction indicated by the arrow 16.
  • interval between the 2nd plate fin 12b and the 3rd plate fin 12c in a 2nd direction may be the same as the said 2nd space
  • the interval between the heat transfer tube 11 adjacent to the third plate fin 12c and the third plate fin 12c may be the same as or different from the first interval P21.
  • the first interval P21 and the second interval P22 may be the same or different.
  • the first corrugated fin 13a is disposed between at least one heat transfer tube 11 and the first plate fin 12a.
  • the second corrugated fin 13b is disposed between the first plate fin 12a and the second plate fin 12b.
  • the third corrugated fin 13c is disposed between the second plate fin 12b and the third plate fin 12c.
  • the fourth corrugated fin 13 d is disposed between the third plate fin 12 c and the other heat transfer tube 11.
  • the first plate fins 12a and the first corrugated fins 13a are connected by a plurality of first connecting portions 24 arranged at a third interval P3 in the first direction indicated by the arrow 15.
  • the first plate fins 12a and the second corrugated fins 13b are connected by a plurality of second connection portions 25 arranged with a fourth interval P4 in the first direction indicated by the arrow 15.
  • the 1st corrugated fin 13a and the heat exchanger tube 11 are connected by the some connection part arrange
  • the interval between the connection portions may be the same as the third interval P3.
  • the second corrugated fin 13b and the second plate fin 12b are connected by a plurality of connecting portions arranged at intervals along the first direction.
  • the interval between the connection portions may be the same as the fourth interval P4.
  • the third interval P3 and the fourth interval P4 may be the same or different.
  • the configuration of the connecting portion between the third and fourth corrugated fins 13c, 13d, the second and third plate fins 12b, 12c and the other heat transfer tubes 11 is basically the same as the first corrugated fin 13a.
  • the third interval P3 and the fourth interval P4 are larger than the first interval P21 and the second interval P22. If it says from a different viewpoint, the 1st direction between the some connection part to which the corrugated fin 13 is connected with the plate fin 12 from the width
  • the hydrophilicity of at least part of the surfaces of the first plate fins 12a, the second plate fins 12b, the third plate fins 12c, and the at least one heat transfer tube 11 is the first corrugate. It may be higher than the hydrophilicity of the surface of the fin 13a, the second corrugated fin 13b, the third and fourth corrugated fins 13c, 13d.
  • the hydrophilicity of the surfaces of the plate fins 12, the corrugated fins 13, and the heat transfer tubes 11, for example changes the material of these members or forms a surface treatment layer having different hydrophilicity on the surface. It can be adjusted by an arbitrary method such as changing the surface roughness.
  • the surface roughness of the plate fins 12 and the heat transfer tubes 11 may be larger than the surface roughness of the corrugated fins 13.
  • a hydrophilic or hydrophobic surface treatment layer may be formed on any of the plate fins 12 and the heat transfer tubes 11 and the corrugated fins 13.
  • the thickness W of at least one heat transfer tube 11 in the second direction indicated by the arrow 16 in FIG. 3 may be greater than the thickness of the first to third plate fins 12a to 12c. Good.
  • the thickness of the first to third plate fins 12a to 12c may be larger than the thickness of the first to fourth corrugated fins 13a to 13d.
  • the positions of the plurality of first connection portions 24 overlap the positions of the plurality of second connection portions 25 in the first direction indicated by the arrow 15.
  • the position of the plurality of first connection parts 24 overlaps with the position of the plurality of second connection parts 25 when at least the first connection part 24 is viewed from the second direction. It means that a part overlaps the second connection part 25.
  • the first and second corrugated fins are based on the first and second intervals P21 and P22 which are the widths of the regions where the first and second corrugated fins 13a and 13b are disposed.
  • the third interval P3 and the fourth interval P4, which are the pitches of the plurality of connecting portions 24 and 25 connected to the first plate fin 12a, are increased by 13a and 13b.
  • the third and fourth corrugated fins also have a pitch of the plurality of connecting portions with the plate fin 12 larger than the first and second intervals P21 and P22.
  • the inclined portions 33 and 34 of the first and second corrugated fins 13a and 13b located between the connecting portions 24 and 25, and the inclined portions of the third and fourth corrugated fins 13c and 13d are the first. It can be tilted sufficiently with respect to the direction.
  • the inclination angle of the inclined portions 33 and 34 with respect to the first direction may be 70 ° or less (in other words, the inclination angle of the inclined portions 33 and 34 with respect to the second direction is 20 ° or more).
  • the inclination angle of the inclined portions 33 and 34 with respect to the first direction may be 60 ° or less, may be 50 ° or less, and may be 45 ° or less.
  • the inclination angle of the inclined parts 33 and 34 with respect to the second direction may be 30 ° or more, 40 ° or more, or 45 ° or more.
  • the heat exchanger 1 is arranged so that the first direction is the vertical direction, dew condensation water is generated in the inclined portions 33 and 34 inclined with respect to the first direction in the first and second corrugated fins 13a and 13b. It can easily flow downward. Similarly, the dew condensation water can easily flow downward in the inclined portions of the third and fourth corrugated fins 13c and 13d. Therefore, the drainage at the corrugated fins 13 in the heat exchanger 1 can be enhanced.
  • the hydrophilicity of at least part of the surfaces of the first plate fins 12a, the second plate fins 12b, and the at least one heat transfer tube 11 is such that the first corrugated fins 13a and the second It is higher than the hydrophilicity of the surface of the corrugated fin 13b.
  • dew condensation water can be easily moved from the surface of the 1st and 2nd corrugated fin 13a, 13b to the 1st and 2nd plate fin 12a, 12b or the surface of the heat exchanger tube 11.
  • the dew condensation water which moved to the 1st and 2nd plate fins 12a and 12b or the heat exchanger tube 11 can move to the perpendicular downward direction easily, for example. For this reason, the drainage property in a heat exchanger can be improved.
  • the thickness W of the at least one heat transfer tube 11 in the second direction indicated by the arrow 16 in FIG. 3 is thicker than the thickness of the first and second plate fins 12a and 12b.
  • the thicknesses of the first and second plate fins 12a and 12b are thicker than the thicknesses of the first and second corrugated fins 13a and 13b.
  • the first to third plate fins 12a to 12c are thicker than the first to fourth corrugated fins 13a to 13d, which are all the corrugated fins 13.
  • the thickness of the plate fin 12 is thicker than the thickness of the corrugated fin 13, the strength of the plate fin 12 can be increased and the shape of the heat exchanger can be stabilized.
  • the positions of the plurality of first connection parts 24 overlap the positions of the plurality of second connection parts 25 in the first direction.
  • the second and third plate fins 13b and 13c the second corrugated fin 13b and the third corrugated fin 13c, or the third corrugated fin 13c and the fourth corrugated so as to sandwich each of them.
  • the position of the connection portion between the fin 13d and the plate fin overlaps in the first direction. If it does in this way, the position of the connection part in the front and back in the plate fin 12 will overlap, and the shape of the plate fin 12 can be stabilized compared with the case where the position of the said connection part differs in the front and back.
  • FIG. 4 is a partial cross-sectional schematic diagram of a heat exchanger according to Embodiment 2 of the present invention.
  • FIG. 4 corresponds to a partial schematic cross-sectional view of the heat exchanger in a plane perpendicular to the first direction shown in FIG.
  • the heat exchanger shown in FIG. 4 has basically the same configuration as the heat exchanger shown in FIGS. 1 to 3, but the first to third plate fins 12a to 12c and the first to fourth The shape of the corrugated fins 13a to 13d is different from that of the heat exchanger shown in FIGS. Specifically, the width L2 of the first to fourth corrugated fins 13a to 13d is larger than the width L1 of the heat transfer tube 11 in the air flow direction indicated by the arrow 22.
  • the first to fourth corrugated fins 13a to 13d include a portion 27 that protrudes from the heat transfer tube 11 toward the upstream side in the air flow direction.
  • the width L3 of the first to third plate fins 12a to 12c is larger than the width L2 of the first to fourth corrugated fins 13a to 13d.
  • the first to third plate fins 12a to 12c include a portion 26 protruding from the first to fourth corrugated fins 13a to 13d toward the upstream side in the air flow direction.
  • the air flow direction is a direction perpendicular to the first direction and the second direction, and is indicated by an arrow 22 in FIG. Direction.
  • the width L3 of the first and second plate fins 12a, 12b is larger than the width L2 of the first and second corrugated fins 13a, 13b.
  • the width L3 of the first to third plate fins 12a to 12c which are a plurality of plate fins disposed between the two heat transfer tubes 11, is disposed adjacent to the plurality of plate fins. It is larger than the width L2 of the first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins.
  • the portions 26 of the first and second plate fins 12a and 12b protrude more upstream in the air flow direction than the first and second corrugated fins 13a and 13b.
  • the third plate fin 12c includes a portion 26. That is, a portion 26 of the first to third plate fins 12a to 12c, which are a plurality of plate fins, is upstream of the first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins, in the air flow direction. Protruding.
  • the first and second corrugated fins 13 a, 13 b have a portion 27 that protrudes upstream from the at least one heat transfer tube 11 in the air flow direction. That is, a portion 27 of the first to fourth corrugated fins 13a to 13d, which is a plurality of corrugated fins, protrudes upstream from at least one heat transfer tube 11.
  • a louver 23 is formed on the first to fourth corrugated fins 13a to 13d.
  • the louver 23 is formed in inclined portions 33 and 34 (see FIG. 3) in the first to fourth corrugated fins 13a to 13d.
  • the louver 23 is formed to extend linearly in a direction intersecting with the air flow direction, specifically, in a direction perpendicular to the air flow direction.
  • the planar shape of the louver 23 is linear, but may be curved.
  • the louver 23 cuts the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d, and inclines part of the inclined portions 33 and 34 adjacent to the cut with respect to other portions. It may be formed by causing to. Further, a slit as a simple opening may be formed in place of the louver 23.
  • most of the condensed water is attached to the corrugated fins, whereas in the heat exchanger according to the present embodiment, most of the condensed water is the first to third plate fins 12a to 12a. 12c can be attached.
  • the first to third plate fins 12a to 12c have a portion 26 that protrudes further to the windward side than the first to fourth corrugated fins 13a to 13d. Since there is no obstacle below the portion 26, the condensed water flows on the surface of the portion 26 of the first to third plate fins 12a to 12c and falls downward in a short time.
  • the condensed water (moisture) condensed on the first to fourth corrugated fins 13a to 13d is guided downward by the louver 23 formed on the first to fourth corrugated fins 13a to 13d.
  • the dew condensation water may not move sufficiently along the corrugated fin.
  • the inclination of the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d with respect to the second direction is ensured, for example, by 20 ° or more. For this reason, dew condensation water can be easily moved downward along the inclined portions 33 and 34.
  • the heat exchanger 1 can obtain the same effects as the heat exchanger in the first embodiment. Furthermore, in the heat exchanger 1, the width L3 of the first to third plate fins 12a to 12c, which are a plurality of plate fins arranged between the two heat transfer tubes 11, is adjacent to the plurality of plate fins. It is larger than the width L2 of the first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins arranged in this manner.
  • the first to third plate fins 12a to 12c include a portion 26 protruding from the first to fourth corrugated fins 13a to 13d in the air flow direction indicated by the arrow 22.
  • the protruding portion 26 extends along the first direction, and can function as a drainage path for condensed water from the first to fourth corrugated fins 13a to 13d.
  • the dew condensation water adheres at an early stage in the portions 26 of the first to third plate fins 12a to 12c protruding upstream in the air flow direction. Thereafter, the condensed water can be quickly moved below the first and second plate fins 12a and 12b via the portion 26 of the first and second plate fins 12a and 12b.
  • FIG. 5 is a partial cross-sectional schematic diagram of a heat exchanger according to Embodiment 3 of the present invention.
  • 6 is a partial perspective schematic view of the heat exchanger shown in FIG.
  • FIG. 7 is a partial top schematic view of the heat exchanger shown in FIG.
  • the heat exchanger shown in FIGS. 5 to 7 basically has the same configuration as that of the heat exchanger shown in FIG. 4, but the plate member 14 is disposed upstream of the heat transfer tube 11 in the air flow direction.
  • the connection point and the arrangement of the louvers 23 are different from the heat exchanger shown in FIG.
  • the plate member 14 is disposed so as to be connected to the windward end portion 28 that is the upstream side in the air flow direction in the heat transfer tube 11. ing.
  • the plate member 14 may be a hollow member, for example, but may be a solid member.
  • the width of the plate member 14 in the second direction (the direction indicated by the arrow 16 in FIG.
  • the width of the first to fourth corrugated fins 13a to 13d may be the same as L2.
  • the first to fourth corrugated fins 13a to 13d include inclined portions 33 and 34.
  • a plurality of louvers 23 are formed in the inclined portions 33 and 34.
  • the inclined portions 33 and 34 are inclined with respect to the first direction which is the vertical direction.
  • a plurality of louvers 23 extending linearly are formed on the inclined portions 33 and 34.
  • the plurality of louvers 23 are formed to extend downward in the vertical direction toward the upstream side in the air flow direction indicated by the arrow 22. That is, as shown in FIG. 6, the louver 23 in the inclined portion 33 is formed so as to approach the protruding portion apex 36 from the connecting portion 25 as it goes upstream in the air flow direction.
  • the louver in the inclination part 34 is formed so that it may approach the connection part 25 from the protrusion part vertex 36 as it goes to the upstream of the distribution direction of air.
  • the first direction is a direction along the direction of gravity.
  • the 1st corrugated fin 13a is located between the some 1st connection parts 24 (refer FIG. 3), and contains the 1st inclination parts 33 and 34 inclined with respect to the perpendicular direction.
  • the 2nd corrugated fin 13b is located between the some 2nd connection parts 25, and contains the 2nd inclination parts 33 and 34 inclined with respect to the perpendicular direction.
  • At least one louver 23 extending linearly is formed on at least one of the first inclined portion and the second inclined portions 33 and 34. At least one louver 23 is formed to extend downward in the vertical direction as it goes upstream in the air flow direction indicated by arrow 22.
  • the louver 23 is formed on all the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d, but may be formed only on some inclined portions 33 and 34. Further, it may be formed on a part of the first to fourth corrugated fins 13a to 13d.
  • the heat exchanger 1 further includes a plate member 14 connected to a portion of the at least one heat transfer tube 11 located on the upstream side in the air flow direction.
  • frost that has been attached to the heat transfer tube 11 in the past can be dispersed and attached to the plate member 14. For this reason, the amount of frost formation in the heat exchanger tube 11 can be reduced, and the drainage of the heat exchanger tube 11 can be improved as a result.
  • louver 23 in the heat exchanger shown in FIGS. 5 to 7 is formed so as to extend downward in the vertical direction toward the upstream side in the air flow direction. Condensed water adhering to the surface can be guided upstream in the air flow direction. Since the portion 26 of the first to third plate fins 12a to 12c is arranged on the upstream side, the drainage of the heat exchanger can be improved by using the portion 26 as a drainage path.
  • FIG. 8 is a schematic diagram showing a refrigerant circuit of an air-conditioning apparatus according to Embodiment 4 of the present invention.
  • the refrigerant circuit shown in FIG. 8 includes a compressor 41, a first heat exchanger 42 that acts as a condenser, a throttle device 43 that acts as an expansion valve, a second heat exchanger 44 that acts as an evaporator, and two blowers 45.
  • the two blowers 45 are each driven by a blower motor 46.
  • the two blowers 45 blow gas (for example, air) to either the first heat exchanger 42 or the second heat exchanger 44, respectively.
  • the refrigerant circulates in the order of the compressor 41, the first heat exchanger 42, the expansion device 43, and the second heat exchanger 44.
  • the air-conditioning apparatus shown in FIG. 8 includes a compressor 41, a first heat exchanger 42, a throttle device 43 as an expansion valve, and a second heat exchanger 44, and the refrigerant in which the refrigerant circulates. Provide a circuit.
  • At least one of the first heat exchanger 42 and the second heat exchanger 44 shown in FIG. 8 is the heat exchanger described in any one of the first to third embodiments.
  • the blower 45 blows gas to each heat exchanger along the third direction (the direction indicated by the arrow 22 in FIG. 4).
  • the refrigerant flow direction in the first heat exchanger 42 and the second heat exchanger 44 in the refrigerant circuit is reversed from the direction shown in FIG.
  • the exchanger may act as an evaporator and the second heat exchanger may act as a condenser.
  • the air conditioner according to the present disclosure is a heat exchanger according to any of Embodiments 1 to 3 described above as a heat exchanger, it has sufficient drainage. Therefore, in the first and second heat exchangers 42 and 44, it is possible to suppress a decrease in efficiency and occurrence of problems due to insufficient discharge of condensed water.
  • the present invention can be applied to an air conditioner, a refrigeration cycle apparatus, a heat pump apparatus, and the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un échangeur de chaleur à propriété de drainage améliorée. Des premières ailettes de plaque (12a) du présent échangeur de chaleur sont disposées à des premiers intervalles par rapport à au moins un tube de transfert de chaleur (11) dans une seconde direction perpendiculaire à une première direction. Des secondes ailettes de plaque (12b) sont disposées à des deuxièmes intervalles des premières ailettes de plaque (12a) dans la seconde direction. Les premières ailettes de plaque (12a) et des premières ailettes ondulées (13a) sont reliées par une pluralité de premières parties de liaison (24) disposées à des troisièmes intervalles dans la première direction. Les premières ailettes de plaque (12a) et des secondes ailettes ondulées (13b) sont reliées par une pluralité de secondes parties de liaison (25) disposées à des quatrièmes intervalles dans la première direction. Les troisièmes et quatrièmes intervalles sont plus grands que les premiers et deuxièmes intervalles.
PCT/JP2016/085941 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur Ceased WO2018100738A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2018553624A JP6997722B2 (ja) 2016-12-02 2016-12-02 熱交換器および空気調和装置
EP16922957.2A EP3550247B1 (fr) 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur
PCT/JP2016/085941 WO2018100738A1 (fr) 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/085941 WO2018100738A1 (fr) 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur

Publications (1)

Publication Number Publication Date
WO2018100738A1 true WO2018100738A1 (fr) 2018-06-07

Family

ID=62242355

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/085941 Ceased WO2018100738A1 (fr) 2016-12-02 2016-12-02 Échangeur de chaleur et climatiseur

Country Status (3)

Country Link
EP (1) EP3550247B1 (fr)
JP (1) JP6997722B2 (fr)
WO (1) WO2018100738A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021234964A1 (fr) * 2020-05-22 2021-11-25 三菱電機株式会社 Échangeur de chaleur et conditionneur d'air
EP3904808A4 (fr) * 2018-12-28 2022-09-21 Danfoss A/S Échangeur de chaleur
EP3853478B1 (fr) * 2019-01-31 2024-11-27 Hydac Cooling GmbH Dispositif de refroidissement

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5512375A (en) * 1978-07-14 1980-01-28 Nihon Radiator Co Airrcooling evaporator
JPS6344076U (fr) * 1986-09-03 1988-03-24
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
JP2005037002A (ja) * 2003-07-16 2005-02-10 Matsushita Electric Ind Co Ltd 熱交換器
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

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPH11108576A (ja) * 1997-10-02 1999-04-23 Nippon Light Metal Co Ltd 熱交換器
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
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
FR2991034B1 (fr) * 2012-05-25 2014-06-06 Valeo Systemes Thermiques Intercalaire pour echangeur thermique et echangeur thermique associe
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
JP6165360B2 (ja) * 2015-03-30 2017-07-19 三菱電機株式会社 熱交換器および空気調和機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5512375A (en) * 1978-07-14 1980-01-28 Nihon Radiator Co Airrcooling evaporator
JPS6344076U (fr) * 1986-09-03 1988-03-24
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
JP2005037002A (ja) * 2003-07-16 2005-02-10 Matsushita Electric Ind Co Ltd 熱交換器
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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3904808A4 (fr) * 2018-12-28 2022-09-21 Danfoss A/S Échangeur de chaleur
EP3853478B1 (fr) * 2019-01-31 2024-11-27 Hydac Cooling GmbH Dispositif de refroidissement
WO2021234964A1 (fr) * 2020-05-22 2021-11-25 三菱電機株式会社 Échangeur de chaleur et conditionneur d'air
JPWO2021234964A1 (fr) * 2020-05-22 2021-11-25
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

Also Published As

Publication number Publication date
JP6997722B2 (ja) 2022-01-18
EP3550247B1 (fr) 2020-11-25
EP3550247A1 (fr) 2019-10-09
EP3550247A4 (fr) 2019-12-18
JPWO2018100738A1 (ja) 2019-10-17

Similar Documents

Publication Publication Date Title
US9441890B2 (en) Heat exchanger fin with corrugated portion and louvers
EP2857785B1 (fr) Echangeur de chaleur et climatiseur
JP6165360B2 (ja) 熱交換器および空気調和機
KR101451056B1 (ko) 열교환기 및 공기 조화기
KR101451054B1 (ko) 열교환기 및 공기 조화기
JP5934933B2 (ja) 室外熱交換器
US8267160B2 (en) Louvered plate fin
JP6897372B2 (ja) 熱交換器
WO2016194088A1 (fr) Échangeur de chaleur et appareil à cycle de réfrigération
US11175053B2 (en) Heat exchanger, refrigeration cycle device, and air-conditioning apparatus
JP5084707B2 (ja) 空気調和機
JP7660665B2 (ja) 熱交換器および冷凍サイクル装置
JP2019190727A (ja) 熱交換器
CN110462326B (zh) 热交换器及制冷循环装置
WO2018100738A1 (fr) Échangeur de chaleur et climatiseur
JP6980117B2 (ja) 熱交換器、熱交換器ユニット、及び冷凍サイクル装置
JP7006376B2 (ja) 熱交換器
JP2010139115A (ja) 熱交換器及び熱交換器ユニット
WO2021130910A1 (fr) Unité d'échange de chaleur et dispositif à cycle frigorifique
JPH10281674A (ja) 室外機用クロスフィン熱交換器
JP2008025855A (ja) 熱交換器、空気調和装置および熱交換器の製造方法
WO2025079135A1 (fr) Échangeur de chaleur, dispositif à cycle de réfrigération et système à cycle de réfrigération
JP6182429B2 (ja) エバポレータ
JPH11218368A (ja) 冷媒蒸発器
WO2022054406A1 (fr) Échangeur de chaleur et appareil de climatisation

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16922957

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2018553624

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2016922957

Country of ref document: EP

Effective date: 20190702