US20100175864A1 - Fin tube heat exchanger - Google Patents

Fin tube heat exchanger Download PDF

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Publication number
US20100175864A1
US20100175864A1 US11/917,994 US91799406A US2010175864A1 US 20100175864 A1 US20100175864 A1 US 20100175864A1 US 91799406 A US91799406 A US 91799406A US 2010175864 A1 US2010175864 A1 US 2010175864A1
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United States
Prior art keywords
heat transfer
fins
guide fins
air flow
heat exchanger
Prior art date
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Abandoned
Application number
US11/917,994
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English (en)
Inventor
Hirokazu Fujino
Hyunyoung Kim
Toshimitsu Kamada
Kazushige Kasai
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Daikin Industries Ltd
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Daikin Industries Ltd
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
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KASAI, KAZUSHIGE, FUJINO, HIROKAZU, KAMADA, TOSHIMITSU, KIM, HYUNYOUNG
Publication of US20100175864A1 publication Critical patent/US20100175864A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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

Definitions

  • the present invention relates to a fin tube heat exchanger, and in particular to a fin tube heat exchanger having heat transfer fins disposed in an air flow and plural heat transfer tubes that are inserted in the heat transfer fins and disposed in a direction substantially orthogonal to a flow direction of the air flow.
  • fin tube heat exchangers i.e., cross fin and tube heat exchangers
  • heat transfer fins disposed in an air flow
  • plural heat transfer tubes that are inserted in the heat transfer fins and disposed in a direction substantially orthogonal to a flow direction of the air flow
  • a fin tube heat exchanger in which the aforementioned guide fins are employed is used as an evaporator of a heat medium such as refrigerant which uses air as a heat source such as represented by air conditioners and the like, a problem arises in that drain water occurring due to heat exchange between the air and the heat medium accumulates on the guide fins and increases ventilation resistance. Further, when a fin tube heat exchanger in which the aforementioned guide fins are employed is used as an outdoor heat exchanger configuring an outdoor unit of an air conditioner, a problem arises in that, although sometimes frost occurring on the heat transfer fin surfaces is removed by defrosting operation, water drainability is lowered in this case.
  • a fin tube heat exchanger pertaining to a first invention comprises: heat transfer fins disposed in an air flow; and plural heat transfer tubes that are inserted in the heat transfer fins and disposed in a direction substantially orthogonal to a flow direction of the air flow.
  • On the heat transfer fins plural guide fins arranged straightly from upstream to downstream in the flow direction of the air flow are formed, by cutting and raising, on the heat transfer fin surfaces on both sides of the heat transfer tubes.
  • Straight lines that hypothetically interconnect the plural guide fins slant with respect to the flow direction of the air flow so as to guide the air flow in the vicinities of the heat transfer tubes to rear sides of the heat transfer tubes in the flow direction of the air flow.
  • the guide fins are plurally divided from upstream to downstream in the flow direction of the air flow, and the plural guide fins slant with respect to the flow direction of the air flow so as to guide the air flow in the vicinities of the heat transfer tubes to rear sides of the heat transfer tubes in the flow direction of the air flow, so mainly the effect of renewing the boundary layers can be reliably obtained by the guide fins of the plural guide fins that are disposed on the front sides of the heat transfer fins in the flow direction of the air flow and the effect of reducing dead water regions formed of the rear sides of the heat transfer fins in the flow direction of the air flow can be obtained by the guide fins that are disposed on the rear sides of the heat transfer fins in the flow direction of the air flow, and it can be made easier for drain water occurring on the heat transfer fin surfaces to be drained from gaps between the guide fins.
  • a heat transfer promoting effect by the guide fins can be obtained without being affected by drain water occurring on the heat transfer fin surfaces.
  • the guide fins of the plural guide fins that are disposed on the rear sides of the heat transfer fins in the flow direction of the air flow have the same inclination as the guide fins that are disposed on the front sides in the flow direction of the air flow, so not only do they reduce dead water regions formed in portions on the rear sides of the heat transfer tubes in the flow direction of the air flow, but they can prevent new dead water regions from being formed on the backs of the guide fins.
  • the effect of promoting heat transfer by the guide fins can be obtained without being affected by drain water occurring on the heat transfer fin surfaces, and new dead water regions can be prevented from being formed on the backs of the guide fins, so a heat transfer promoting effect and water drainability by the guide fins can be simultaneously achieved.
  • a fin tube heat exchanger pertaining to a second invention is the fin tube heat exchanger pertaining to the first invention, wherein the height of each of the guide fins gradually increases downstream in the flow direction of the air flow.
  • each of the guide fins by giving each of the guide fins a shape whose height gradually increases downstream in the flow direction of the air flow, vertical vortexes can be created on the back of each of the guide fins, so that the heat transfer promoting effect by the guide fins can be further raised.
  • a fin tube heat exchanger pertaining to a third invention is the fin tube heat exchanger pertaining to the first or second invention, wherein a water drainage promoting portion for causing water accumulating between the guide fins that are mutually adjacent on the straight lines to flow downward is formed in the heat transfer fins.
  • the water drainage promoting portion is formed between the guide fins, so the ability of the guide fins to drain water can be further raised.
  • a fin tube heat exchanger pertaining to a fourth invention is the tin tube heat exchanger pertaining to the third invention, wherein the water drainage promoting portion is a slit formed between the guide fins that are mutually adjacent on the straight lines.
  • a fin tube heat exchanger pertaining to a fifth invention is the fin tube heat exchanger pertaining to the third invention, wherein the water drainage promoting portion is a cutout formed in end portions of the guide fins that are mutually adjacent on the straight lines, which end portions are portions that become lower end portions of the guide fins.
  • a fin tube heat exchanger pertaining to a sixth invention is the fin tube heat exchanger pertaining to the third invention, wherein the water drainage promoting portion is a water-conducting rib formed between the guide fins that are mutually adjacent on the straight lines.
  • FIG. 1 is a cross-sectional diagram of a fin tube heat exchanger pertaining to a first embodiment of the present invention.
  • FIG. 2 is a cross-sectional diagram along A-A of FIG. 1 .
  • FIG. 3 is a cross-sectional diagram along B-B of FIG. 1 .
  • FIG. 4 is a diagram showing a fin tube heat exchanger pertaining to a modification of the first embodiment, the diagram showing portion C of FIG. 1 .
  • FIG. 5 is a diagram showing a fin tube heat exchanger pertaining to a modification of the first embodiment, the diagram showing portion C of FIG. 1 .
  • FIG. 6 is a diagram showing a fin tube heat exchanger pertaining to a modification of the first embodiment, the diagram showing portion C of FIG. 1 .
  • FIG. 7 is a cross-sectional diagram of a fin tube heat exchanger pertaining to a second embodiment of the present invention.
  • FIG. 8 is a cross-sectional diagram along A-A of FIG. 7 .
  • FIG. 9 is a cross-sectional diagram along B-B of FIG. 7 .
  • FIG. 10 is a diagram showing a fin tube heat exchanger pertaining to a modification of the second embodiment, the diagram showing portion C of FIG. 7 .
  • FIG. 11 is a diagram showing a fin tube heat exchanger pertaining to a modification of the second embodiment, the diagram showing portion C of FIG. 7 .
  • FIG. 12 is a diagram showing a fin tube heat exchanger pertaining to a modification of the second embodiment, the diagram showing portion C of FIG. 7 .
  • FIG. 1 to FIG. 3 there are shown relevant portions of a fin tube heat exchanger 1 pertaining to a first embodiment of the present invention.
  • FIG. 1 is a cross-sectional diagram of the fin tube heat exchanger 1 .
  • FIG. 2 is a cross-sectional diagram along A-A of FIG. 1 .
  • FIG. 3 is a cross-sectional diagram along B-B of FIG. 1 .
  • the fin tube heat exchanger 1 is a cross fin and tube heat exchanger and is mainly disposed with plural plate-shaped heat transfer fins 2 and plural heat transfer tubes 3 .
  • the heat transfer fins 2 are disposed so as to be arranged in a plate thickness direction in a state where the planar direction thereof is generally along a flow direction of an air flow such as that of air.
  • Plural through holes 2 a are formed in the heat transfer fins 2 at intervals in a direction substantially orthogonal to the flow direction of the air flow. Portions around the through holes 2 a serve as annular collar portions 23 that project towards one side in the plate thickness direction of the heat transfer fins 2 .
  • the collar portions 23 contact surfaces of the heat transfer fins 2 adjacent in the plate thickness direction that are opposite of surfaces where the collar portions 23 are formed, such that a predetermined interval H is ensured between each of the heat transfer fins 2 in the plate thickness direction.
  • the heat transfer tubes 3 are tube members inside of which a heat medium such as refrigerant flows; the heat transfer tubes 3 are inserted in the plural heat transfer fins 2 , which are disposed so as to be arranged in the plate thickness direction, and disposed in a direction substantially orthogonal to the flow direction of the air flow. Specifically, the heat transfer tubes 3 penetrate the through holes 2 a formed in the heat transfer fins 2 and tightly contact the inner surfaces of the collar portions 23 as a result of tube expansion work during assembly of the fin tube heat exchanger 1 .
  • the fin tube heat exchanger 1 of the present embodiment is used in a state where the arranging direction of the plural heat transfer tubes 3 is in a substantially vertical direction. For this reason, the air flow flows so as to cross through the fin tube heat exchanger 1 in a substantially horizontal direction. It will be noted that in the following description, when language such as “upper side” or “upward” and “lower side” or “downward” is used, this will indicate the arranging direction of the heat transfer tubes 3 .
  • plural (in the present embodiment, two) a set of guide fins 21 a and 21 b and a set of guide fins 21 c and 21 d arranged straightly from upstream to downstream in the flow direction of the air flow are formed, by cutting and raising, on the heat transfer fin 2 surfaces on both sides of each of the heat transfer fins 3 (i.e., the lower side and the upper side of each of the heat transfer fins 3 ).
  • attack angles ⁇ 1 and ⁇ 2 that the straight lines L 1 and L 2 form with respect to the flow direction of the air flow are set to be within the range of 10° to 30°.
  • each of the guide fins 21 a to 21 d is formed such that its height gradually increases downstream in the flow direction of the air flow.
  • each of the guide fins 21 a to 21 d is substantially trapezoidal or substantially triangular (see FIG. 3 ; FIG. 3 is a diagram showing the guide fins 21 c and 21 d , but the guide fins 21 a and 21 b also have the same shape) and is formed such that its maximum height h is less than the height H of the collar portions 23 .
  • slit holes 22 a to 22 d that are formed in the heat transfer fins 2 when the guide fins 21 a to 21 d are cut and raised are disposed on the far sides of the heat transfer fins 3 with the guide fins 21 a to 21 d being interposed therebetween.
  • the guide fins formed on both sides of each of the heat transfer tubes 3 are divided into the plural (in the present embodiment, two) the set of the guide fins 21 a and 21 b and the set of the guide fins 21 c and 21 d from upstream to downstream in the flow direction of the air flow, and the set of the guide fins 21 a and 21 b and the set of the guide fins 21 c and 21 d slant with respect to the flow direction of the air flow so as to guide the air flow in the vicinities of the heat transfer tubes 3 to the rear sides of the heat transfer tubes 3 in the flow direction of the air flow, so mainly the effect of renewing the boundary layers can be reliably obtained by the guide fins 21 a and 21 c of the guide fins 21 a to 21 d that are disposed on the front sides of the heat transfer fins 2 in the flow direction of the air flow and the effect of reducing dead water regions formed on portions of the rear sides of the heat transfer fins 3 in the flow
  • the guide fins 21 a and 21 b and the guide fins 21 c and 21 d are straightly arranged on the straight lines L 1 and L 2 from upstream to downstream in the flow direction of the air flow
  • the guide fins 21 b and 21 d of the guide fins 21 a to 21 d that are disposed on the rear sides of the heat transfer fins 2 in the flow direction of the air flow have the same inclination as the guide fins 21 a and 21 c that are disposed on the front sides in the flow direction of the air flow, so not only do they reduce dead water regions formed in portions on the rear sides of the heat transfer tubes 3 in the flow direction of the air flow, but they can prevent new dead water regions from being formed on the backs of the guide fins 21 b and 21 d.
  • a heat transfer promoting effect by the guide fins 21 a to 21 d can be obtained without being affected by drain water occurring on the heat transfer fin 2 surfaces, and new dead water regions can be prevented from being formed on the backs of the guide fins 21 b and 21 d , so a heat transfer promoting effect and water drainability by the guide fins can be simultaneously achieved.
  • each of the guide fins 21 a to 21 d by giving each of the guide fins 21 a to 21 d a shape whose height gradually increases downstream in the flow direction of the air flow, vertical vortexes can be formed on the back of each of the guide fins 21 a to 21 d , so the heat transfer promoting effect by each of the guide fins 21 a to 21 d can be further raised.
  • FIG. 4 to FIG. 6 are diagrams showing portion C of FIG. 1 when each type of water drainage promoting portion is formed in the heat transfer fins 2 .
  • the slits 32 and 35 are formed in the heat transfer fins 2 .
  • the slits 32 and 35 are formed, so as to cross the straight lines L 1 and L 2 in the vertical direction, in gap portions between the guide fins 21 a and 21 b that are mutually adjacent on the straight line L 1 and between the guide fins 21 c and 21 d that are mutually adjacent on the straight line L 2 .
  • the slits 32 and 35 are given a narrow slit width by forming vertical incisions in the heat transfer fins 2 , for example, in order to ensure that the slits 32 and 35 do not, as much as possible, affect heat transfer performance.
  • slits 31 , 33 , 34 and 36 that are the same as the slits 32 and 35 may also be formed in the end portions of the guide fins 21 a to 21 d other than the gap portions between the guide fins 21 a and 21 b and between the guide fins 21 c and 21 d.
  • the cutouts 42 and 43 are formed in the heat transfer fins 2 that are mutually adjacent on the straight lines L 1 and L 2 , which end portions become lower end portions of the guide fins 21 a and 21 b and the guide fins 21 c and 21 d (i.e., portions that become lower portions of the guide fins 21 a and 21 b and the guide fins 21 c and 21 d along the direction of gravitational force).
  • the cutouts 42 and 43 are formed in the lower end portion of the guide fin 21 b and in the lower end portion of the guide fin 21 c .
  • the cutouts 42 and 43 are vertical incisions formed in the lower end portions of the guide fins 21 b and 21 c so as to be communicated with the slits 22 b and 22 c that are formed when forming the guide fins 21 c and 21 c by cutting and raising.
  • cutouts 41 and 44 that are the same as the cutouts 42 and 43 may also be formed in the end portions of the guide fins 21 a and 21 d other than the portions that become the lower end portions of the guide fins 21 b and 21 c.
  • the water-conducting rib 52 is formed, so as to cross the straight lines L 1 and L 2 in the vertical direction, in gap portions between the guide fins 21 a and 21 b that are mutually adjacent on the straight line L 1 and between the guide fins 21 c and 21 d that are mutually adjacent on the straight line L 2 .
  • the water-conducting rib 52 is a long and narrow projection that extends upward and is formed by pressing the heat transfer fin 2 surfaces, and the water-conducting rib 52 is formed so as to continuously interconnect, in the vertical direction (i.e., in the direction of gravitational force), the gap portion between the guide fins 21 a and 21 b and the gap portion between the guide fins 21 c and 21 d .
  • the water-conducting rib 52 cannot be straightly extended in the vertical direction, so by forming just the portion thereof in the vicinity of the collar portion 23 in a circular arc shape, a state where the water-conducting rib 52 is continuously formed in substantially the direction of gravitational force can be maintained.
  • water-conducting ribs 51 and 53 that are the same as the water-conducting rib 52 may also be formed on the portion on the front side of the guide fins 21 a and 21 c in the flow direction of the air flow and the portion on the rear side of the guide fins 21 b and 21 d in the flow direction of the air flow other than the gap portion between the guide fins 21 a and 21 b and the gap portion between the guide fins 21 c and 21 d.
  • the ability of the heat transfer fins 2 to drain water can be further raised because the slits 32 and 35 , the cutouts 42 and 43 , or the water-conducting rib 52 serving as a water drainage promoting portion are formed between the guide fins 21 a and 21 b that are mutually adjacent on the straight line L 1 of the heat transfer fins 2 and between the guide fins 21 c and 21 d that are mutually adjacent on the straight line L 2 .
  • FIG. 7 is a cross-sectional diagram of the fin tube heat exchanger 101 .
  • FIG. 8 is a cross-sectional diagram along A-A of FIG. 7 .
  • FIG. 9 is a cross-sectional diagram along B-B of FIG. 7 .
  • the basic configuration of the fin tube heat exchanger 101 is the same as the configuration of the fin tube heat exchanger 1 of the first embodiment except for guide fins 121 a to 121 f of later-described heat transfer fins 102 . For this reason, description in regard to the basic configuration of the fin tube heat exchanger 101 will be omitted by changing the reference numerals that relate to the heat transfer fins 102 from the 10s to the 100s.
  • plural (in the present embodiment, three) a set of guide fins 121 a , 121 b and 121 c and a set of guide fins 121 d , 121 e and 121 f arranged straightly from upstream to downstream in the flow direction of the air flow are formed, by cutting and raising, on the heat transfer fin 2 surfaces on both sides of each of the heat transfer fins 3 (i.e., the lower side and the upper side of each of the heat transfer fins 3 ).
  • Straight lines L 1 and L 2 that hypothetically interconnect the guide fins 121 a , 121 b and 121 c and the guide fins 121 d , 121 e and 121 f slant with respect to the flow direction of the air flow so as to guide the air flow in the vicinities of the heat transfer tubes 3 to the rear sides of the heat transfer tubes 3 in the flow direction of the air flow.
  • attack angles ⁇ 1 and ⁇ 2 that the straight lines L 1 and L 2 form with respect to the flow direction of the air flow are set to be within the range of 10° to 30°.
  • each of the guide fins 121 a to 121 f is formed such that its height gradually increases downstream in the flow direction of the air flow.
  • each of the guide fins 121 a to 121 f is substantially trapezoidal or substantially triangular (see FIG. 9 ; FIG. 9 is a diagram showing the guide fins 121 d , 121 e and 121 f , but the guide fins 121 a , 121 b and 121 c also have the same shape) and is formed such that its maximum height h is less than the height H of collar portions 123 .
  • slit holes 122 a to 122 f that are formed in the heat transfer fins 102 when the guide fins 121 a to 121 f are cut and raised are disposed on the far sides of the heat transfer fins 3 with the guide fins 121 a to 121 f being interposed therebetween.
  • the guide fins of the fin tube heat exchanger 1 of the first embodiment had a two-division structure comprising the set of the guide fins 21 a and 21 b and the set of the guide fins 21 c and 21 d
  • the guide fins here have a three-division structure comprising the set of the guide fins 121 a , 121 b and 121 c and the set of the guide fins 121 d , 121 e and 121 f , so the number of gaps between the guide fins for draining drain water occurring on the heat transfer fin 102 surfaces increases. For this reason, the ability to drain water can be raised in comparison to the fin tube heat exchanger 1 of the first embodiment.
  • fin tube heat exchanger 101 also, similar to the fin tube heat exchanger 1 of the first embodiment, slits 132 , 133 , 136 and 137 (see FIG. 10 ), cutouts 142 , 143 , 144 and 145 (see FIG. 11 ), or water-conducting ribs 152 and 153 (see FIG.
  • FIG. 10 to FIG. 12 are diagrams showing portion C of FIG. 7 when each type of water drainage promoting portion is formed in the heat transfer fins 102 .
  • slits 131 , 134 , 135 and 138 , cutouts 141 and 146 , or water-conducting ribs 151 and 154 may also be formed in portions other than between the guide fins 121 a and 121 b , between the guide fins 121 b and 121 c , between the guide fins 121 d and 121 e , and between the guide fins 121 e and 121 f.
  • a heat transfer promoting effect and water drainability by guide tins can be simultaneously achieved in a fin tube heat exchanger.

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  • 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)
  • Details Of Fluid Heaters (AREA)
US11/917,994 2005-07-01 2006-06-26 Fin tube heat exchanger Abandoned US20100175864A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2005-194254 2005-07-01
JP2005194254A JP2007010279A (ja) 2005-07-01 2005-07-01 フィンチューブ型熱交換器
PCT/JP2006/312716 WO2007004457A1 (ja) 2005-07-01 2006-06-26 フィンチューブ型熱交換器

Publications (1)

Publication Number Publication Date
US20100175864A1 true US20100175864A1 (en) 2010-07-15

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US11/917,994 Abandoned US20100175864A1 (en) 2005-07-01 2006-06-26 Fin tube heat exchanger

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US (1) US20100175864A1 (ja)
EP (1) EP1906129B1 (ja)
JP (1) JP2007010279A (ja)
KR (1) KR100973225B1 (ja)
CN (1) CN100554855C (ja)
AU (1) AU2006266965B2 (ja)
ES (1) ES2370795T3 (ja)
WO (1) WO2007004457A1 (ja)

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US10005413B2 (en) 2016-10-05 2018-06-26 Toyota Motor Engineering & Manufacturing North America, Inc. Vehicles including front grille assemblies with air flow director fins
US11236951B2 (en) * 2018-12-06 2022-02-01 Johnson Controls Technology Company Heat exchanger fin surface enhancement
US20220065556A1 (en) * 2020-08-31 2022-03-03 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner using the heat exchanger

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JP5162929B2 (ja) * 2007-03-14 2013-03-13 ダイキン工業株式会社 フィンチューブ型熱交換器
JP2008232448A (ja) * 2007-03-16 2008-10-02 Daikin Ind Ltd フィンチューブ型熱交換器および空気調和装置
JP4293252B2 (ja) * 2007-03-19 2009-07-08 ダイキン工業株式会社 熱交換器用フィン、並びにガイド及びその使用方法
JP2008249298A (ja) * 2007-03-30 2008-10-16 Daikin Ind Ltd フィンチューブ型熱交換器
JP5304025B2 (ja) * 2008-05-27 2013-10-02 ダイキン工業株式会社 フィンチューブ型熱交換器
JP5304024B2 (ja) * 2008-05-27 2013-10-02 ダイキン工業株式会社 フィンチューブ型熱交換器
CN102374816A (zh) * 2011-11-09 2012-03-14 海信（山东）空调有限公司 环翼桥式换热器翅片、换热器及空调
US20170074564A1 (en) * 2014-05-15 2017-03-16 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus including the heat exchanger
CN105758246B (zh) * 2014-12-15 2019-06-11 浙江盾安人工环境股份有限公司 换热器翅片和换热器
JP6680225B2 (ja) * 2017-01-19 2020-04-15 株式会社デンソー 熱交換器及び熱交換器の製造方法
CN112964112A (zh) * 2021-03-25 2021-06-15 山东西努克机械科技有限公司 一种高效散热翅片

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EP1906129A1 (en) 2008-04-02
CN100554855C (zh) 2009-10-28
WO2007004457A1 (ja) 2007-01-11
ES2370795T3 (es) 2011-12-22
EP1906129A4 (en) 2010-08-11
EP1906129B1 (en) 2011-09-07
KR100973225B1 (ko) 2010-07-30
AU2006266965B2 (en) 2009-08-13
WO2007004457A8 (ja) 2008-01-31
JP2007010279A (ja) 2007-01-18
AU2006266965A1 (en) 2007-01-11
KR20080011445A (ko) 2008-02-04
CN101208575A (zh) 2008-06-25

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