EP2447659A2 - Wärmetauscher und Lamelle dafür - Google Patents

Wärmetauscher und Lamelle dafür Download PDF

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Publication number
EP2447659A2
EP2447659A2 EP20110187109 EP11187109A EP2447659A2 EP 2447659 A2 EP2447659 A2 EP 2447659A2 EP 20110187109 EP20110187109 EP 20110187109 EP 11187109 A EP11187109 A EP 11187109A EP 2447659 A2 EP2447659 A2 EP 2447659A2
Authority
EP
European Patent Office
Prior art keywords
micro
heat exchanger
header
slots
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.)
Withdrawn
Application number
EP20110187109
Other languages
English (en)
French (fr)
Other versions
EP2447659A3 (de
Inventor
Young Min Kim
Hayase Gaku
Kang Tae Seo
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.)
Samsung Electronics Co Ltd
Original Assignee
Samsung Electronics Co 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
Application filed by Samsung Electronics Co Ltd filed Critical Samsung Electronics Co Ltd
Publication of EP2447659A2 publication Critical patent/EP2447659A2/de
Publication of EP2447659A3 publication Critical patent/EP2447659A3/de
Withdrawn legal-status Critical Current

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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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • Embodiments of the present disclosure relate to a heat exchanger of an air conditioner having a structure capable of achieving enhancements in drainage and heat transfer performance.
  • Heat exchangers which implement one part of the refrigeration cycle, are used in equipment such as air conditioners and refrigerators.
  • Heat exchangers include a plurality of fins for heat exchange arranged to be spaced apart from one another, and a plurality of refrigerant tubes, which is installed to come into contact with the plural fins for heat exchange, to guide refrigerant.
  • air flowing into the heat exchanger from the outside undergoes heat exchange while passing through the fins for heat exchange, so that cooling operation or heating operation is achieved.
  • Heat exchangers are classified into fin & tube type and parallel flow type heat exchangers in accordance with shapes of the fin and tube and coupling relations therebetween.
  • the fin & tube type heat exchanger has a structure in which press-worked fins are layered, and a plurality of circular tubes is then fitted between adjacent ones of the layered fins through a press-fit process.
  • the parallel flow type heat exchanger has a structure in which a fin having a corrugated shape is joined between flat elliptical tubes through a brazing process.
  • the parallel flow type heat exchanger is superior in terms of heat exchange efficiency, as compared to the fin & tube type heat exchanger.
  • drainage of condensed water from the parallel flow type heat exchanger may be troublesome.
  • FMC fin micro-channel heat exchanger
  • a heat exchanger includes a first header connected with an inflow tube and an outflow tube, a second header spaced apart from the first header by a desired distance and arranged parallel to the first header, a plurality of flat micro-channel tubes arranged in a front row and a rear row between the first header and the second header, and a plurality of plate type fins, each of the micro-channel tubes includes micro-channels, and each of the fins includes slots arranged in a front row and a rear row to respectively fit the front row and rear row micro-channel tubes into the slots.
  • Louvers or slits may be formed between vertically adjacent ones of the slots in each of the fins.
  • the louvers may have a pitch LP satisfying a range of about 0.8mm ⁇ Lip ⁇ 1.2mm.
  • a clearance D1 between each slot and each louver or slit adjacent to each other may satisfy a range of about 0mm ⁇ D1 ⁇ 1 mm.
  • a clearance D2 between the front row and rear row slots may satisfy a range of about D2 ⁇ 2mm.
  • a ratio R between an air-side heat transfer area A and a refrigerant-side heat transfer area C defined by equations below may satisfy a range of about 2.5mm ⁇ R ⁇ 3.5mm:
  • A Lf x Wf - sum of slot areas per fin x 2 x total number of fins
  • C Wc + Hc x 2 x Lt x total number of micro - channels per micro - channel tube x total number of micro - channel tubes
  • R A / C , where "Lf” represents an overall height of each fin, "Wf” represents a width of each fin, “Wc” represents a width of each micro-channel, “Hc” represents a height of each micro-channel, and "Lt” represents a length of each micro-channel tube.
  • Openings arranged in the form of a lattice between vertically adjacent ones of the slots may be formed at each of the fins.
  • Each of the openings may have a square shape.
  • the first and second headers may extend vertically.
  • a fin assembly for a heat exchanger including a plurality of plate type fins into which flat micro-channel tubes are fitted, wherein each of the fins may include slots arranged in a front row and a rear row to receive the micro-channel tubes, respectively, and louvers or slits formed between vertically adjacent ones of the slots.
  • the louvers may have a pitch LP satisfying a range of about 0.8mm ⁇ Lip ⁇ 1.2mm.
  • a clearance D1 between each slot and each louver or slit adjacent to each other may satisfy a range of about 0mm ⁇ D1 ⁇ 1 mm.
  • a clearance D2 between the front row and rear row slots may satisfy a range of about D2 ⁇ 2mm.
  • a fin assembly for a heat exchanger including a plurality of plate type fins into which flat micro-channel tubes are fitted, wherein each of the fins may include slots arranged in a front row and a rear row to receive the micro-channel tubes, respectively, and openings arranged in a lattice form between the vertically adjacent ones of the slots.
  • Each of the openings may have a square shape.
  • FIG. 1 is a perspective view illustrating an external appearance of a heat exchanger according to an exemplary embodiment of the present disclosure.
  • the heat exchanger 1 includes a first header 10, a second header 20, micro-channel tubes 30, and fins 40.
  • the first header 10 and the second header 20 extend vertically while being spaced apart from each other by a desired distance.
  • Tube coupling portions (not shown) are formed at facing walls of the first and second headers 10 and 20. Each tube coupling portion is formed by cutting the corresponding header wall to a size in accordance with a cross section of the corresponding micro-channel tube 30 to couple the micro-channel tube 30 to the tube coupling portion.
  • the first header 10 and the second header 20 include respective front tanks 11 and 21 and respective rear tanks 12 and 22.
  • the front tanks 11 and 21 and the rear tanks 12 and 22 are partitioned by partition walls, respectively.
  • Each of the front tanks 11 and 21 and the rear tanks 12 and 22 may be further vertically partitioned by baffles 13.
  • the micro-channel tubes 30 are installed between the first and second headers 10 and 20, to guide refrigerant by communicating the first header 10 with the second header 20.
  • Each of the micro-channel tubes 30 is a path through which refrigerant passes. Refrigerant is compressed or expanded while circulating in an air conditioner (not shown), so that cooling and heating may be achieved.
  • the micro-channel tubes 30, which are vertically spaced apart from one another by a desired clearance, are arranged in two rows, namely, a front row and a rear row. That is, the micro-channel tubes 30 include front row micro-channel tubes 31 and rear row micro-channel tubes 32.
  • the front row and rear row micro-channel tubes 31 and 32 are alternately arranged in a zigzag formation.
  • the front row and rear row micro-channel tubes 31 and 32 may be arranged to be horizontally aligned with each other, as shown in FIG. 4 .
  • an inflow tube 14 into which refrigerant flows and an outflow tube 15 from which heat-exchanged refrigerant while passing through the micro-channel tubes 30 is discharged are connected to the first header 10.
  • the inflow and outflow tubes 14 and 15 may be respectively connected to lower and upper sides of the first header 10, in order to prevent accumulation of refrigerant droplets caused by gravity, even if refrigerant flowing into the first header 10 has both a gas phase and a liquid phase.
  • FIG. 2 is a top view schematically illustrating a fin structure of the heat exchanger according to an exemplary embodiment of the present disclosure.
  • FIG. 3 is a sectional view taken along line I - I of FIG. 2 .
  • FIGS. 2 and 3 A structure of fins and tubes for the heat exchanger according to the exemplary embodiments of the present disclosure will be described with reference to FIGS. 2 and 3 .
  • a fin body 43 in each fin 40 is formed to have a plate shape with a certain width Wf and height Hf.
  • the fin body 43 may be a rectangular thin plate.
  • Each fin 40 is installed to come into contact with the corresponding micro-channel tubes 30, and may be formed as widely as possible so that the section thereof to radiate or absorb heat becomes wider.
  • Heat of refrigerant flowing inside the micro-channel tubes 30 is transferred to air flowing around the fins 40 via the micro-channel tubes 30 and fins 40, thereby easily radiating heat to the outside.
  • front row slots 44 and rear row slots 45 are formed at each of the fins 40 so that the front row and rear row micro-channel tubes 31 and 32 are fitted into the front row slots 44 and the rear row slots 45, respectively.
  • collars 47 perpendicular to the fin body 43 are formed respectively at peripheral areas of the front row and rear row slots 44 and 45 to easily fit the front row and rear row micro-channel tubes 31 and 32 into the corresponding front row and rear row slots 44 and 45 respectively, thereby securing a desired joining force.
  • the fins 40 are arranged to be evenly spaced in parallel with a flow direction of air. Thus, air may execute heat exchange while naturally flowing along surfaces of the fins 40 without greatly undergoing resistance caused by the fins 40.
  • the front row and rear row slots 44 and 45 of each fin 40 are also arranged in a zigzag formation.
  • the front row and rear row slots 44 and 45 of each fin 40 are also arranged to be horizontally aligned with each other, of course.
  • front row and rear row louvers 41 and 42 are formed between the vertically adjacent slots 44 and between the vertically adjacent slots 45 respectively, to enhance heat transfer efficiency by increasing a contact area with air.
  • the louvers 41 are formed between the vertically adjacent front row slots 44, and the louvers 42 are formed between the vertically adjacent rear row slots 45.
  • each fin 40 the front row louvers 41 and the rear row louvers 42 are symmetrically arranged in a width direction of the fin 40, and each of the front row louvers 41 and the rear row louvers 42 is formed so that a portion of the fin body 43 is slightly bent from a plane of the fin 40 in an upward or downward direction to be inclined at a desired angle. Accordingly, air flowing along the fins 40 is dispersed by the louvers 41 and 42, and growth of a boundary layer is restrained, so that heat exchange efficiency may be enhanced.
  • the clearance D1 between each slot 44 or 45 and each louver 41 or 42 may be 1 mm or less, in order to prevent an increase in air-side pressure loss and a deterioration in heat transfer performance due to formation of water droplets at lower ends of the micro-channel tubes 30.
  • condensed water may be smoothly drained to lower ends of the fins 40 by capillary action.
  • drainage performance may be enhanced when the clearance D2 between the front row slots 44 into which the front row micro-channel tubes 31 are respectively fitted and the rear row slots 45 into which the rear row micro-channel tubes 32 are respectively fitted may be 2mm or more.
  • Drainage performance may be enhanced when the pitch LP of the louvers 41 and 42 satisfies a range of 0.8mm ⁇ Lip ⁇ 1.2mm.
  • FIG. 5 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • FIG. 6 is a sectional view taken along line II - II of FIG. 5 .
  • FIG. 7 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • slits 46a and 46b may be formed between vertically adjacent slots 44 and between vertically adjacent slots 45, respectively.
  • the slits 46a are formed between the vertically adjacent front row slots 44, and the slits 46b are formed between the vertically adjacent rear row slots 45. Air is changed into turbulent air while flowing into openings of the slits 46a and 46b, and the turbulent air circulates around the micro-channel tubes 30, and thus heat exchange efficiency may be improved.
  • front row slots 44 and rear row slots 45 of each fin 40 may be arranged in a zigzag formation or to be horizontally aligned with each other.
  • FIG. 8 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • FIG. 9 is a sectional view taken along line III - III of FIG. 8 .
  • FIG. 10 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • louvers 41 and 42 and slits 46a and 46b in each fin 40 may also be formed together, and front row slots 44 and rear row slots 45 in each fin 40 may be arranged in a zigzag formation or to be horizontally aligned with each other. Since the remaining components are the same as those according to another exemplary embodiment of the present disclosure, no description will be given.
  • each of the micro-channel tubes 30 has a flat shape, and a plurality of micro-channels 33 is formed in the micro-channel tube 30 to guide refrigerant in the micro-channel tube 30.
  • each of the micro-channel tubes 30 may have a circular shape in a cross section, the micro-channel tube 30 may have a flat shape to expand a heat transfer area.
  • FIG. 12 is a graph illustrating variation in heat exchange performance according to a ratio between an air-side heat transfer area and a refrigerant-side heat transfer area.
  • the x-axis refers to the ratio R between the air-side heat transfer area A and the refrigerant-side heat transfer area C
  • the y-axis refers to the quantity of heat per frontal area Q/FA, heat transfer capacity per frontal area HA/FA, and pressure loss per unit length dP/L (however, numerical values of the y-axis are relative values).
  • performance characteristics according to the ratio R between the air-side heat transfer area A and the refrigerant-side heat transfer area C may be varied.
  • pressure loss increases as the ratio R between the air-side heat transfer area A and the refrigerant-side heat transfer area C increases. Therefore, when the ratio R satisfies a range of about 2.5 ⁇ R ⁇ 3.5, overall performance characteristics may be optimized.
  • the ratio R between the air-side heat transfer area A and the refrigerant-side heat transfer area C is 10 ⁇ R ⁇ 20 in the case of the fin & tube type heat exchanger, whereas the ratio R is 3 ⁇ R ⁇ 4 in the case of the parallel flow type heat exchanger.
  • the refrigerant-side heat transfer area C may be increased, in order to obtain an optimal performance characteristic.
  • FIGS. 13 and 14 are views explaining a method of joining the tubes and fins for the heat exchanger according to an exemplary embodiment of the present disclosure, respectively.
  • the joining of the micro-channel tubes 30 and fins 40 as described above may be achieved by welding wires 50, in addition to a brazing process conventionally used to join aluminum clad fins and tubes.
  • the fin 40 and the front row and rear row micro-channel tubes 31 and 32 may be welded and joined together while the melted welding wires flow into the gaps between the micro-channel tubes and the corresponding slots, as shown in FIG. 14 .
  • joining defects may be greatly resolved in addition to easy welding.
  • FIG. 15 is a perspective view illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • the fin 140 may include a fin body 143, slots 145 alternatively arranged in a zigzag formation to respectively fit the micro-channel tubes, and a plurality of openings 148 arranged in a lattice form between the vertically adjacent slots 145. Collars 147 may be formed respectively around the slots 145 so as to easily attach the micro-channel tubes to the slots 145 by fitting the micro-channel tubes into the slots 145.
  • air F flowing in a thickness direction of the fins 140 may pass between a front surface and a rear surface of each fin 140 through the openings 148 while flowing between the fins 140. Further, since a plurality of fins 140 is layered, the openings 148 arranged at corresponding positions between the layered fins 140 may form a channel. Thus, a reduction in air-side pressure loss and an enhancement in heat transfer performance may be achieved.
  • a fin micro-channel heat exchanger having a structure capable of achieving enhancements in drainage and heat transfer performance.

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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)
EP20110187109 2010-10-28 2011-10-28 Wärmetauscher und Lamelle dafür Withdrawn EP2447659A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020100106368A KR20120044847A (ko) 2010-10-28 2010-10-28 열교환기 및 그 핀

Publications (2)

Publication Number Publication Date
EP2447659A2 true EP2447659A2 (de) 2012-05-02
EP2447659A3 EP2447659A3 (de) 2015-04-08

Family

ID=45001646

Family Applications (1)

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EP20110187109 Withdrawn EP2447659A3 (de) 2010-10-28 2011-10-28 Wärmetauscher und Lamelle dafür

Country Status (4)

Country Link
US (1) US20120103583A1 (de)
EP (1) EP2447659A3 (de)
KR (1) KR20120044847A (de)
CN (1) CN102706040A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3038977A1 (fr) * 2015-07-17 2017-01-20 Valeo Systemes Thermiques Echangeur de chaleur a ailettes comprenant des persiennes ameliorees
CN109000488A (zh) * 2017-09-14 2018-12-14 华北电力大学 一种点阵式换热器

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD775315S1 (en) * 2012-08-02 2016-12-27 Mitsubishi Electric Corporation Fin-plate for heat exchanger
USD749201S1 (en) * 2012-08-02 2016-02-09 Mitsubishi Electric Corporation Fin-plate for heat exchanger
KR101421953B1 (ko) * 2012-12-27 2014-07-22 현대자동차주식회사 자동차용 적층형 열전발전장치
US10006662B2 (en) * 2013-01-21 2018-06-26 Carrier Corporation Condensing heat exchanger fins with enhanced airflow
WO2014209345A1 (en) * 2013-06-28 2014-12-31 Schneider Electric It Corporation Indirect evaporator cooler heat exchanger manufacturing method
WO2015040746A1 (ja) * 2013-09-20 2015-03-26 三菱電機株式会社 熱交換器、その熱交換器を用いた空気調和装置、及びその熱交換器の製造方法
DE102014202788A1 (de) * 2013-12-19 2015-06-25 Robert Bosch Gmbh Wärmetauscher
CN103888054A (zh) * 2014-03-04 2014-06-25 苏州边枫电子科技有限公司 带散热结构的太阳能接线盒
WO2016139730A1 (ja) * 2015-03-02 2016-09-09 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
CN106802029B (zh) * 2015-11-25 2020-04-07 杭州三花微通道换热器有限公司 换热器芯体和具有它的换热器
US10378835B2 (en) * 2016-03-25 2019-08-13 Unison Industries, Llc Heat exchanger with non-orthogonal perforations
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
JP2018071860A (ja) * 2016-10-27 2018-05-10 株式会社富士通ゼネラル 熱交換器
CN109237984A (zh) * 2017-07-10 2019-01-18 美的集团股份有限公司 换热器及家用电器
CN109900136B (zh) * 2017-12-07 2021-12-07 浙江盾安机械有限公司 一种翅片及换热器
CN110345780A (zh) * 2018-04-03 2019-10-18 丹佛斯微通道换热器（嘉兴）有限公司 换热器
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger
US11047631B2 (en) * 2019-02-20 2021-06-29 Caterpillar Inc. Bumper clip for tube type heat exchangers
CN112344763B (zh) * 2019-08-07 2022-04-01 丹佛斯有限公司 制造换热器的方法
AU2020329293B2 (en) * 2019-08-14 2023-06-08 Shell Internationale Research Maatschappij B.V. Heat exchanger system and method

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3897821A (en) * 1973-08-03 1975-08-05 Barry Wehmiller Co Heat transfer coil
US4360141A (en) * 1980-09-02 1982-11-23 Kensrue Milo M Holder for welding seam back-up tape
JPH1089870A (ja) * 1996-09-18 1998-04-10 Nippon Light Metal Co Ltd 熱交換器の製造方法及び熱交換器
KR100220724B1 (ko) * 1996-12-30 1999-09-15 윤종용 공기조화기의 열교환기
JP2001194084A (ja) * 1999-12-15 2001-07-17 Lg Electronics Inc フィン・チューブ型の熱交換器
FR2804501B1 (fr) * 2000-01-28 2002-04-12 Valeo Thermique Moteur Sa Module d'echange de chaleur, en particulier pour vehicule automobile
US6964296B2 (en) * 2001-02-07 2005-11-15 Modine Manufacturing Company Heat exchanger
US6745827B2 (en) * 2001-09-29 2004-06-08 Halla Climate Control Corporation Heat exchanger
JP4300508B2 (ja) * 2002-12-25 2009-07-22 株式会社ティラド 熱交換器用プレートフィンおよび熱交換器コア
US7028766B2 (en) * 2003-11-25 2006-04-18 Alcoa Inc. Heat exchanger tubing with connecting member and fins and methods of heat exchange
DE112005001009T5 (de) * 2004-05-11 2007-03-08 Showa Denko Kk Wärmetauscher
US7721794B2 (en) * 2007-02-09 2010-05-25 Lennox Industries Inc. Fin structure for heat exchanger
EP2313728A1 (de) * 2008-06-13 2011-04-27 Goodman Global, Inc. Verfahren zur herstellung eines rohr- und rippenwärmetauschers mit reduziertem rohrdurchmesser und dadurch hergestellte optimierte rippe
CN201476625U (zh) * 2009-06-15 2010-05-19 浙江康盛股份有限公司 微通道冷凝器
CN101619950B (zh) * 2009-08-13 2011-05-04 三花丹佛斯（杭州）微通道换热器有限公司 翅片和具有该翅片的换热器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3038977A1 (fr) * 2015-07-17 2017-01-20 Valeo Systemes Thermiques Echangeur de chaleur a ailettes comprenant des persiennes ameliorees
WO2017012867A1 (fr) * 2015-07-17 2017-01-26 Valeo Systemes Thermiques Échangeur de chaleur a ailettes comprenant des persiennes améliorées
CN108369076A (zh) * 2015-07-17 2018-08-03 法雷奥热***公司 包括改进的百叶片的翅片热交换器
US10914530B2 (en) 2015-07-17 2021-02-09 Valeo Systemes Thermiques Fin heat exchanger comprising improved louvres
CN109000488A (zh) * 2017-09-14 2018-12-14 华北电力大学 一种点阵式换热器
CN109000488B (zh) * 2017-09-14 2024-05-28 华北电力大学 一种点阵式换热器

Also Published As

Publication number Publication date
EP2447659A3 (de) 2015-04-08
CN102706040A (zh) 2012-10-03
KR20120044847A (ko) 2012-05-08
US20120103583A1 (en) 2012-05-03

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