EP3561430B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP3561430B1
EP3561430B1 EP19169686.3A EP19169686A EP3561430B1 EP 3561430 B1 EP3561430 B1 EP 3561430B1 EP 19169686 A EP19169686 A EP 19169686A EP 3561430 B1 EP3561430 B1 EP 3561430B1
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EP
European Patent Office
Prior art keywords
flat tubes
heat exchanger
fins
front edge
cutouts
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
EP19169686.3A
Other languages
German (de)
English (en)
Other versions
EP3561430A3 (fr
EP3561430A2 (fr
Inventor
Ryuji KAWABATA
Hiroshi Hasegawa
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.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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Publication of EP3561430A2 publication Critical patent/EP3561430A2/fr
Publication of EP3561430A3 publication Critical patent/EP3561430A3/fr
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Publication of EP3561430B1 publication Critical patent/EP3561430B1/fr
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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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating 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
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • 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
    • F28F2215/08—Fins with openings, e.g. louvers
    • 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 a heat exchanger which includes a plurality of plate-like fins and a plurality of flat tubes having a plurality refrigerant flow paths and which effects heat exchange between air flowing between the plurality of fins and refrigerant flowing through the refrigerant flow paths of the plurality of flat tubes.
  • a heat exchanger including plate-like fins and a plurality of flat tubes having a plurality of refrigerant flow paths and being perpendicularly inserted in tube insertion cutouts provided so as to be parallel to each other on the airflow downstream side of the fins.
  • Fig. 17 is a plan view taken along an x-y plane of the conventional heat exchanger disclosed in Patent Literature 1.
  • the x-direction is the air flow direction
  • the y-direction is the flat tube arrangement direction.
  • a heat exchanger 1 includes plate-like fins 2, and a plurality of flat tubes 5 having a plurality of refrigerant flow paths 4 and being inserted at right angles in tube insertion cutouts 3 provided parallel to each other on the airflow downstream side (in the +x-direction) of the fins, with a flat portion 6 being provided on the airflow upstream side (in the -x-direction) of the tube insertion cutouts 3 of each fin 2.
  • the distance from the flat tubes 5 to the front edge portion of the fin 2 is longer, so that in the case where the heat exchanger is used in an environment where frost formation occurs, there is slowness in the heat conduction from the refrigerant flowing through the refrigerant flow paths 4 of the flat tubes 5 to the airflow upstream side (-x-direction) of the fin 2 where the humidity amount in the air is large and frost formation is likely to occur, making it possible to suppress an air blockade due to the frost.
  • Patent Literature 2 describes a heat exchanger comprising a plurality of flattened heat exchange pipes, which are arranged in parallel, headers which support both ends of the heat exchange pipes and supply a working fluid to the heat exchange pipes, a plurality of radiation members, which are made of a strip sheet and are combined with the heat exchange pipes in such a manner that the radiation members are stacked in layers in the same direction and have their longitudinal direction arranged approximately perpendicular to the longitudinal direction of heat exchanging pipes, and a plurality of needle-like pin fins, which are formed by punching the radiation members.
  • the radiation members are provided with cut-and-bent portions on one surface thereof, which determine the distance between the stacked radiation members, wherein each cut-and-bent portion is formed by cutting and bending a portion of the radiation member at a given angle inclined relative to the longitudinal direction and a lateral direction of the radiation member.
  • Patent Literature 3 describes a heat exchanger, wherein a flat tube is inserted into a tube insertion part of a fin, and joined thereto by brazing, the edges of the tube insertion part are bent so as to slant inward as approaching the tip thereof.
  • the conventional structure In a condition in which frost formation is likely to occur as in a cold region or at midwinter, however, the conventional structure is still insufficient in sufficiently suppressing frost formation, and involves generation of air blockade, an increase in draft resistance, and a reduction in the amount of air passing through the heat exchanger, resulting in deterioration in heat exchange performance.
  • the present invention has been made to solve the above problem in the prior art. It is an object of the present invention to provide a heat exchanger employing a flat tube which can achieve an improvement in terms of heat exchange performance by promoting heat conduction on an airflow upstream side in the flat tube while reducing the fin efficiency on the airflow upstream side and suppressing frost formation on the upstream side in the fin airflow.
  • a heat exchanger in accordance with the present invention includes a plurality of plate-like fins arranged at predetermined intervals, and a plurality of flat tubes having a plurality of refrigerant flow paths, each of the fins including a flat portion, tube insertion cutouts formed to be parallel to each other to allow insertion of the flat tubes on an airflow downstream side, and collar portions with which the respective flat tubes are in contact, wherein the plate-like fins further include front edge cutouts extending from at least part of airflow upstream side surfaces of the flat tubes inserted in the tube insertion cutouts to the flat portion.
  • the heat exchanger of the present invention can suppress the frost formation on the fins on the upstream side in the fin airflow where the humidity amount in the air is large, so that it is possible to suppress a reduction in the amount of air passing through the heat exchanger due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • a heat exchanger including a plurality of plate-like fins arranged at predetermined intervals, and a plurality of flat tubes having a plurality of refrigerant flow paths, each of the fins including a flat portion, tube insertion cutouts formed parallel to each other to allow insertion of the flat tubes on an airflow downstream side, and collar portions with which the respective flat tubes are in contact; and front edge cutouts are provided in the plate-like fins so as to extend from at least part of airflow upstream side surfaces of the flat tubes inserted in the tube insertion cutouts to the flat portion.
  • a flat tube side opening width of the front edge cutouts is h
  • a height of the flat tubes is H
  • the height of the flat tubes is larger than a flat tube side openings of the front edge cutouts, and when the flat tubes are inserted, the flat tubes come into contact with the flat tube side openings of the front edge cutouts and are fixed thereto.
  • drain cutouts including a gravitational direction component at the front edge cutouts.
  • the condensed water quickly flows down without freezing, so that it is possible to prevent the heat exchanger from freezing to stop the heating operation, thus making it possible to achieve an improvement in terms of heating capacity.
  • the fins are cut by the drain cutouts, and the heat conduction from the airflow upstream side surfaces of the flat tubes to the front edge portions of the fins becomes slow, so that even in a condition in which frost formation is more likely to occur, it is possible to suppress frost formation on the fins on the airflow upstream side where the amount of humidity in the air is large, and a reduction in the amount of air passing through the heat exchanger due to an increase in draft resistance is suppressed, making it possible to achieve an improvement in terms of heat exchange performance.
  • Fig. 1 is a perspective view of a heat exchanger according to Embodiment 1 of the present invention.
  • An x-direction is an airflow direction
  • a y-direction is a flat tube arrangement direction
  • a z-direction is a fin arrangement direction.
  • a heat exchanger 10 includes a plurality of plate-like fins 11 arranged at predetermined intervals, and a plurality of flat tubes 12 which are perpendicularly inserted in the plurality of fins 11 and which are arranged parallel to each other. Heat exchange is effected between air flowing between the plurality of fins 11, and refrigerant flowing through a plurality of refrigerant flow paths 13 formed in the plurality of flat tubes 12.
  • refrigerant there is employed, for example, R410A, R32, or mixture refrigerant containing R32.
  • Fig. 2 is a plan view of a fin of the heat exchanger of Embodiment 1 of the present invention taken along an x-y plane
  • Fig. 3 is a side view of the fin, as seen from the x-direction and taken along a z-y plane, of the heat exchanger of Embodiment 1 of the present invention and is a sectional view taken along the line A-A of Fig. 2 .
  • the fin 11 includes a flat portion 14, heat conduction promoting portions 15, tube insertion cutouts 16 which allow insertion of the flat tubes 12 on an airflow downstream side (+x-direction) and which are formed parallel to each other, collar portions 17 with which the respective flat tubes 12 are in contact, and front edge cutouts 18 formed to extend from at least part of an airflow upstream side surfaces (-x-direction) of the flat tubes 12 inserted in the tube insertion cutouts 16 toward the flat portion 14.
  • the heat conduction promoting portions 15 are raised toward an airflow path side (+z-direction) from the flat portion 14 of the fin 11 and are chevron-shaped. They are provided between a plurality of flat tubes 12 adjacent to each other and between the front edge portions of the flat tubes 12 and the rear edge portions of the flat tubes 12.
  • openings of the tube insertion cutouts 16 are larger than a height of the flat tubes 12 (a length in the y-direction).
  • the collar portions 17 are raised substantially perpendicularly from the flat portion 14 of the fin 11 toward the airflow path side (+z-direction), and are held in contact with a surface of the adjacent fin 11, thus maintaining an interval between the fins 11 adjacent to each other. They are soldered to the flat tubes 12 by brazing.
  • cut-and-raised portions such different from the collar portions 17 such as tabs (not shown) may be brought into contact with the surface of the adjacent fine 11, thereby maintaining an interval between the fins 11 adjacent to each other.
  • the air impinges upon the front edge portions of the fins 11, and a boundary layer becomes thinner, so that heat conductivity becomes higher.
  • the air having impinged upon the front edge portions of the fins 11 passes between the plurality of fins 11 adjacent to each other.
  • the air having come into contact with the airflow upstream side (-x-direction) surfaces of the flat tubes 12 performs heat exchange with the refrigerant flowing through the refrigerant flow paths 13 on the airflow upstream side (-x-direction) of the flat tubes 12, and then passes between the plurality of flat tubes 12 adjacent to each other.
  • Fig. 4 is a z-x plan view illustrating an internal structure of an outdoor unit 20 to which the heat exchanger 10 of the present embodiment is applied
  • Fig. 5 is a z-y front view illustrating the internal structure of the outdoor unit 20 to which the heat exchanger 10 of the present embodiment is applied.
  • the outdoor unit 20 includes a compressor 21, a change-over valve 22, an outdoor expansion valve 23, a blower 24, and the heat exchanger 10.
  • the outdoor unit 20 and the indoor unit are connected to each other through a liquid pipe 25 and a gas pipe 26.
  • a plurality of flat tubes 12 are arranged in a horizontal directions (a z-direction and an x-direction) so as to be parallel to each other along an axial direction (a y-direction) of header pipes 27a and 27b, and the refrigerant flow paths 13 in the flat tubes 12 communicate with an interior of the header pipes 27a and 27b.
  • the header pipe 27a is connected to the change-over valve 22 via refrigerant piping 28a, and to the outdoor expansion valve 23 via refrigerant piping 28b.
  • a partition 29 is provided inside the header pipe 27a, and a refrigerant flow path is divided into an axially upper side (+y-direction) and an axially lower side (-y-direction) of the header pipe 27a.
  • the heat exchanger 10 functions as a condenser.
  • Gas refrigerant which is sent from the compressor of the outdoor unit 20 is caused to flow into the header pipe 27a from the refrigerant piping 28a via the change-over valve 22.
  • This gas refrigerant passes through the interior of the header pipe 27a, and flows into a plurality of refrigerant flow paths 13 of the plurality of flat tubes 12 connected to the axially upper side (+y-direction) of the header pipe 27a before flowing in the horizontal direction (+z-direction and +x-direction) to flow out into the header pipe 27b.
  • the refrigerant having flowed into the header pipe 27b flows into the refrigerant flow paths 13 of the plurality of flat tubes 12 connected to the axially lower side (-y-direction) of the header pipe 27b, and flows in the horizontal direction (-x-direction and -z-direction).
  • the refrigerant radiates heat and is condensed through heat exchange with air sent from the blower 24.
  • the condensed refrigerant flows into the header pipe 27a, and passes through the outdoor expansion valve 23 and the liquid pipe 25 from the refrigerant piping 28b before flowing out into the indoor unit.
  • the condensed refrigerant having flowed out into the indoor unit absorbs heat and is evaporated through heat exchange with the air at an indoor heat exchanger (not shown).
  • the evaporated refrigerant passes through the gas pipe 26 and is circulated to the compressor 21 via the change-over valve 22.
  • the heat exchanger 10 functions as an evaporator.
  • the gas refrigerant sent from the compressor 21 of the outdoor unit 20 passes through the gas pipe 26 via the change-over valve 22, and flows out into the indoor unit.
  • the gas refrigerant having flowed out into the indoor unit radiates heat and is condensed through heat exchange with the air at the indoor heat exchanger provided in the indoor unit.
  • the condensed refrigerant passes through the liquid pipe 25 and the outdoor expansion valve 23 to become gas-liquid two-phase refrigerant before flowing into the header pipe 27a from the refrigerant piping 28b.
  • the gas-liquid two-phase refrigerant flows from the header pipe 27a into the refrigerant flow paths 13 of the plurality of flat tubes 12 connected to the axially lower side (-y-direction) of the header pipe 27a, and flows in the horizontal direction (+z-direction and +x-direction) before flowing out into the header pipe 27b.
  • the refrigerant having flowed out into the header pipe 27b flows into the refrigerant flow paths 13 of the plurality of flat tubes 12 connected to the axially upper side (+y-direction) of the header pipe 27b, and flows in the horizontal direction (-x-direction and -z-direction).
  • the refrigerant absorbs heat and is evaporated through heat exchange with the air sent from the blower 24.
  • the evaporated refrigerant flows into the header pipe 27a, passes through the interior, and is circulated to the compressor 21 from the refrigerant piping 28a via the change-over valve 22.
  • the heat exchanger 10 functions as an evaporator
  • low temperature refrigerant flows through the refrigerant flow paths 13 of the flat tubes 12, and heat exchange is effected with the air.
  • the water in the air adheres to surfaces of the fins 11 and the flat tubes 12, and condensed water is generated.
  • the condensed water freezes as frost.
  • At least a part of the collar portions 17 of the fins 11 is cut, and air comes into direct contact with the airflow upstream side (-x-direction) surface of the flat tubes 12, so that it is possible to promote the heat conduction on the airflow upstream side (-x-direction) of the flat tubes 12, making it possible to achieve a further improvement in terms of heat exchange performance.
  • Fig. 6 is a plan view of a fin of a heat exchanger of Embodiment 2 of the present invention taken along the x-y plane
  • Fig. 7 is an enlarged view of a fin of the heat exchanger of Embodiment 2 of the present invention taken along the x-y plane and is an enlarged view of portion B of Fig. 6 .
  • the y-direction height of the flat tubes 12 is larger than openings of the front edge cutouts 18 on the flat tube 12 side.
  • h is at least 0.1 mm or more.
  • h it is preferable for h to be still larger.
  • the collar portions 17 of the fins 11 on the airflow upstream side (-x-direction) of the flat tube 12 are thus greatly cut, and the area thereof coming into direct contact with the airflow upstream side (-x-direction) of the flat tube 12 increases, so that the heat conduction from the airflow upstream side (-x-direction) surfaces of the flat tube 12 to the front edge portions of the fins 11 becomes slower while promoting the heat conduction on the airflow upstream side (-x-direction) of the flat tube 12, and it is possible to further suppress frost formation on the fins 11 on the airflow upstream side (-x-direction) where the humidity amount in the air is large, and it is possible to suppress a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • the point E it is preferable for the point E to be provided at the airflow downstream side (+x-direction) than an intermediate position between the points C and D.
  • the distance from the point E to the point D is at least 0.1 mm or more.
  • Fig. 8 is a plan view of a fin of a heat exchanger according to Modification 1 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 9 is a plan view of a fin of a heat exchanger according to Modification 2 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 10 is a plan view of a fin of a heat exchanger according to Modification 3 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 11 is a plan view of a fin of a heat exchanger according to Modification 4 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 8 is a plan view of a fin of a heat exchanger according to Modification 1 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 9 is a plan view of a fin of a heat exchanger according to Modification 2 of Embodiment
  • Fig. 12 is a plan view of a fin of a heat exchanger according to Modification 5 of Embodiment 2 of the present invention taken along the x-y plane;
  • Fig. 13 is a plan view of a fin of a heat exchanger according to Modification 6 of Embodiment 2 of the present invention taken along the x-y plane.
  • the front edge cutouts 18 provide a similar effect if they are provided at positions shifted in a tube arrangement direction (y-direction), using as a reference the center plane a passing through the central portion in the y-direction height of the flat tubes 12 and parallel to the airflow direction (x-direction).
  • the front edge cutouts 18 may be of a triangular or a rectangular configuration. This helps to enlarge a cut area of the front edge cutouts 18, and the amount of air existing between the airflow upstream side (-x-direction) surfaces of the flat tubes 12 and the fins 11 increases, and the heat conduction from the airflow upstream side (-x-direction) surfaces of the flat tubes 12 to the front edge portions of the fins 11 becomes still slower, so that it is possible to further suppress frost formation on the fins 11 on the airflow upstream side (-x-direction) where the amount of humidity in the air is large, and to suppress a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • the front edge cutouts 18 may be inclined in the gravitational direction (-y-direction) with respect to the airflow direction (+x-direction).
  • the plurality of front edge cutouts 18 may be provided for one flat tube 12.
  • the cut portions of the fins 11 increase, and the heat conduction to the front edge portions of the fins 11 becomes slower, so that it is possible to further suppress frost formation on the fins 11 on the airflow upstream side (-x-direction) where the amount of humidity in the air is large, and a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance is suppressed, making it possible to achieve an improvement in terms of heat exchange performance.
  • Fig. 14 is a plan view of a fin of a heat exchanger of Embodiment 3 of the present invention taken along the x-y plane.
  • drain cutouts 19 including a gravitational direction (-y-direction) component are provided at the front edge cutouts 18.
  • the condensed water generated on the airflow upstream side (-x-direction) of the flat tubes 12 and having flowed into the front edge cutouts 18 flows along the drain cutouts 19, and flows in the gravitational direction (-y-direction) to grow.
  • an amount of water increases, and the gravitational force applied to the dew condensation water increases, whereby the water flows down quickly.
  • the condensed water quickly flows down without freezing, so that it is possible to prevent the heating operation from being stopped due to the freezing of the heat exchanger 10, making it possible to achieve an improvement in terms of heating capacity.
  • the heat conduction to the front edge portions of the fins 11 from the airflow upstream side (-x-direction) surfaces of the flat tubes 12 becomes slower, so that even in a condition in which frost formation is more likely to occur, it is possible to suppress frost formation on the fins 11 on the airflow upstream side (-x-direction) where the humidity amount in the air is large, and to suppress a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • an opening width w of the drain cutouts 19 is at least 0.1 mm or more.
  • the fins 11 there are provided portions where the fins 11 are cut between the front edge portions (point D) of the flat tubes 12 and a position at a minimum distance from the flat tubes 12 (point C), and between the front edge portions (point D) of the flat tubes 12 and a position at a maximum distance from the flat tubes 12 (point F), so that the heat conduction from the flat tubes 12 to the front edge portions of the finis 11 becomes slow, and it is possible to further suppress frost formation over the entire front edge portions of the fins 11 on the airflow upstream side (-x-direction) where the humidity amount in the air is large, and to suppress a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • Fig. 15 is a plan view of a fin of a heat exchanger according to Modification 1 of Embodiment 3 of the present invention taken along the x-y plane.
  • the drain cutouts 19 are formed so as to extend solely in the gravitational direction (-y-direction).
  • the condensed water generated on the airflow upstream side (-x-direction) of the flat tubes 12 and having flowed into the front edge cutouts 18 flows along the drain cutouts 19, and flows more smoothly in the gravitational direction (-y-direction) to grow, with the amount of water increasing and the gravitational force applied to the dew condensation water increasing, with the result that the water flows down quickly.
  • Fig. 16 is a plan view of a fin of a heat exchanger according to Modification 2 of Embodiment 3 of the present invention taken along the x-y plane.
  • the drain cutouts 19 may be formed on the airflow upstream side (-x-direction) of the flat tubes 12.
  • drain cutouts 19 are formed at the lower end in the gravitational direction (-y-direction) of the front edge cutouts 18, so that the portions of the front edge cutouts 18 where the condensed water is maintained are reduced, and the condensed water can be drained more quickly, and it is possible to prevent a reduction in the amount of air passing through the heat exchanger 10 due to the increase in draft resistance, making it possible to achieve an improvement in terms of heat exchange performance.
  • a heat exchanger employing flat tubes, wherein the heat conduction on the airflow upstream side of the flat tubes is promoted while lowering a fin efficiency on the airflow upstream side and suppressing frost formation on the airflow upstream side of the fins, whereby it is possible to achieve an improvement in terms of heat exchange performance.
  • the heat exchanger is applicable to a refrigerator, air conditioner, hot-water-supply/air-conditioning combined apparatus, etc.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (3)

  1. Échangeur de chaleur comprenant une pluralité d'ailettes en forme de plaque (11) agencées à des intervalles prédéterminés et une pluralité de tubes plats (12) présentant une pluralité de trajets d'écoulement de fluide frigorigène (13), chacune des ailettes comprenant une partie plate (14), des découpes d'insertion de tube (16) formées pour être parallèles les unes aux autres pour permettre l'insertion des tubes plats sur un côté en aval de l'écoulement d'air et des parties de collier (17) avec lesquelles les tubes plats respectifs sont en contact, caractérisé en ce que les ailettes en forme de plaque (11) comprennent en outre des découpes de bord avant (18) s'étendant à partir d'au moins une partie des surfaces sur un côté en amont de l'écoulement d'air des tubes plats insérés dans les découpes d'insertion de tube vers la partie plate.
  2. Échangeur de chaleur selon la revendication 1, dans lequel, présumant qu'une largeur d'ouverture de la découpe de bord avant sur un côté de tube plat est h et qu'une hauteur des tubes plats est H, h < H.
  3. Échangeur de chaleur selon la revendication 2, dans lequel les découpes de bord avant sont chacune pourvues d'une découpe de drain (19) comprenant un composant de direction gravitationnelle.
EP19169686.3A 2018-04-25 2019-04-16 Échangeur de chaleur Active EP3561430B1 (fr)

Applications Claiming Priority (1)

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JP2018083667A JP2019190727A (ja) 2018-04-25 2018-04-25 熱交換器

Publications (3)

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EP3561430A2 EP3561430A2 (fr) 2019-10-30
EP3561430A3 EP3561430A3 (fr) 2019-11-06
EP3561430B1 true EP3561430B1 (fr) 2022-10-19

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Publication number Priority date Publication date Assignee Title
KR102222507B1 (ko) * 2019-11-14 2021-03-04 엘지전자 주식회사 열교환기
JP2022148602A (ja) * 2021-03-24 2022-10-06 東芝キヤリア株式会社 熱交換器
WO2024080937A1 (fr) * 2022-10-14 2024-04-18 National University Of Singapore Appareil, système et procédé d'échange de chaleur
CN116399154B (zh) * 2023-06-02 2023-09-29 广东美的暖通设备有限公司 翅片、换热组件、微通道换热器及暖通设备

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09324995A (ja) * 1996-06-05 1997-12-16 Toshiba Corp 熱交換器
JP2004353954A (ja) * 2003-05-29 2004-12-16 Denso Corp 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
JP2012154498A (ja) * 2011-01-21 2012-08-16 Daikin Industries Ltd 熱交換器および空気調和機
WO2012098912A1 (fr) * 2011-01-21 2012-07-26 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
JP5523495B2 (ja) 2011-04-22 2014-06-18 三菱電機株式会社 フィンチューブ型熱交換器及び冷凍サイクル装置
US10082344B2 (en) * 2015-03-02 2018-09-25 Mitsubishi Electric Coporation Fin-and-tube heat exchanger and refrigeration cycle apparatus including the same
WO2016194043A1 (fr) * 2015-05-29 2016-12-08 三菱電機株式会社 Échangeur de chaleur
JP6233540B2 (ja) * 2016-04-20 2017-11-22 ダイキン工業株式会社 熱交換器及び空調機
CN109312991B (zh) * 2016-07-01 2020-11-10 三菱电机株式会社 热交换器及具备该热交换器的制冷循环装置
CN107940818A (zh) * 2017-09-30 2018-04-20 博格思众（常州）热交换器有限公司 一种翅片、冷凝器及翅片的制造方法

Also Published As

Publication number Publication date
EP3561430A3 (fr) 2019-11-06
CN110398163B (zh) 2022-12-06
EP3561430A2 (fr) 2019-10-30
CN110398163A (zh) 2019-11-01
JP2019190727A (ja) 2019-10-31

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