EP1574801A2 - Echangeur de chaleur et ailette ondulée - Google Patents

Echangeur de chaleur et ailette ondulée Download PDF

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Publication number
EP1574801A2
EP1574801A2 EP05003995A EP05003995A EP1574801A2 EP 1574801 A2 EP1574801 A2 EP 1574801A2 EP 05003995 A EP05003995 A EP 05003995A EP 05003995 A EP05003995 A EP 05003995A EP 1574801 A2 EP1574801 A2 EP 1574801A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cuts
wave
flanks
exchanger network
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Withdrawn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
EP05003995A
Other languages
German (de)
English (en)
Other versions
EP1574801A3 (fr
Inventor
Bernhard Dipl.-Ing. Lamich
Anton Zielbauer
Viktor Dipl.-Ing. Brost
Jens Dipl.-Ing. Nies
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.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
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 Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP1574801A2 publication Critical patent/EP1574801A2/fr
Publication of EP1574801A3 publication Critical patent/EP1574801A3/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—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 obliquely

Definitions

  • the invention relates to a heat exchanger network with at least one row Flat tubes, through which a liquid or a gas flows, with in between arranged corrugated fins, whose flanks channels with an air inlet and form an air outlet, flows through the cooling air, wherein the Heat exchanger network is arranged perpendicular to the cooling air flow direction.
  • the invention relates to corrugated fins that form part of a Heat exchanger network are.
  • the object of the invention is a heat exchanger network and a to propose suitable corrugated rib, which for the vertical arrangement of the Heat exchanger network promises improved efficiency of the heat exchange.
  • the claim 11 describes the second solution according to the invention, in the is provided that the respective air inlet of the channels without offset to the respective air outlet of the channels is arranged, wherein the wave flanks a Contour that consists of a single sheet.
  • those formed by the wave flanks Channels of the corrugated fins are formed so that the respective air inlet into each of the Channels offset from the respective air outlet from each of the channels is arranged each air particle forced to an intense contact with the wave flanks.
  • the air no longer, as in the prior art, horizontally through the channels flow through, because it is deflected by the offset in the vertical.
  • the horizontally flowing cooling air is changed according to the offset in the horizontal deflected.
  • the size of the offset is determined by the size of the angle between the Wave direction and the vertical influences. Of course, by the Depth of the heat exchanger network. At a deeper heat exchanger network is at same amount of offset amount greater than a flatter Heat exchanger network. The cooling air follows the wave flanks and becomes characterized diverted.
  • Wave flank cuts are present that are out of the plane of each Flank protruding.
  • Such preferably gill-like cuts are not Basically new, however, she has to the knowledge of the applicant so far no one with an inclination angle and / or with a contour extending corrugations of the Well rib provided.
  • the cuts may be different be configured and bring about special advantages.
  • the surfaces of the wave flanks can be flat or have a contour.
  • the cuts mean that the mentioned channels and the Heilein - and the air outlets not to be understood are that the same air particles passing through an entrance into the respective channel Enter also emerge through the associated outlet again. Rather, it is intends not to form the channels discreetly, so that at least a part the cooling air can distribute on adjacent channels, before they at the outlets the Heat exchanger network leaves again.
  • the corrugated fin according to the invention is characterized in that in the with a Tilt angle extending wave flanks cuts arranged out of the plane the wave flank are exposed.
  • Such a corrugated fin according to the invention can of course also in one with a tendency to the cooling air flow direction arranged heat exchanger network can be provided.
  • Fig. 1 shows a part of a heat exchanger network according to the invention trained heat exchanger.
  • Fig. 2 shows a heat exchanger from the State of the art.
  • FIGS. 3 to 23 show different embodiments of Corrugated ribs and their production.
  • the heat exchanger is placed perpendicular to the flow direction of the cooling air (arrow) according to Figure 1, as it is provided in most applications in automotive or elsewhere. He owns a collecting box 25 with an inlet or outlet nozzle 27 through the liquid or hot charge air flows to flow over the arranged in a row flat tubes 1 to the not shown, lying at the opposite end of the flat tubes 1 , other collection box. In this case, the gas flowing in the flat tubes 1 or the liquid is cooled by means of the cooling air flowing through the corrugated fins 2 .
  • the flat tubes 1 and the corrugated fins 2 form the heat exchanger network, which is preferably firmly connected by means of soldering.
  • the channels 4 formed by the wave flanks 3 of the corrugated fins 2 are formed so that the respective air inlet 5 is arranged in each of the channels 4 offset from the respective air outlet 6 from each of the channels 4 .
  • the level of the air inlets 5 is higher than the level of the air outlets. 6
  • the flat tubes 1 and the corrugated fins 2 are horizontal. As a result, the air outlet 6 is located on the right or left in the horizontal - the offset 40 offset from the air inlet. 5
  • the efficiency of the heat exchange is particularly promoted because the turbulence of the air is further improved without overly adversely increasing the pressure loss of the cooling air flow.
  • the heat exchange rate between the liquid flowing in the flat tubes 1 or, for example, the strongly heated charge air with the cooling air has been significantly increased.
  • the heat exchanger shown can be designed with or without tubesheets. Since in the illustrated embodiment, the corrugated fins 2 represent in plan view as a parallelogram, results between the perpendicular to the vertical 50 extending ends of the flat tubes 1 and between the plane perpendicular to the vertical 50 extending plane of the indicated tube bottom 26 and the corrugated fin 2 an angle ⁇ . Should this angle ⁇ be perceived as disadvantageous, it can be avoided by appropriate selection of the position and contour of the separating cut in the production of the corrugated fins 2 taking place from the metal strip.
  • FIG. 3 shows a perspective view of a corrugated fin 2, in the wave flanks 3 over a substantial portion 10 of the shaft sections 7 flanks 3 introduced.
  • 4 and 5 show views of a flat tube 1 over the broad side of a corrugated fin 2 are arranged with obliquely extending wave flanks 3 .
  • the offset 40 between air inlets 5 and 6 air outlets identified.
  • the angle ⁇ between the shaft running direction 30 and the vertical 50 has been drawn, the vertical 50 coinciding with the course of the edges of the flat tubes 1 .
  • the shaft running direction 30 is always the direction perpendicular to the wave flanks 3 direction.
  • FIGS. 6 and 7 differ from FIGS. 4 and 5 in that the wave flanks 3 have been provided with a rounding or with a contour 35 .
  • FIGS. 9-13 show, according to the section AA, different embodiments of sections 7 in the corrugation flanks 3 .
  • a web 20 is present, wherein the edges of the web 20 are bent.
  • the angle of the turn corresponds to the angle of attack 12 of the individual cuts 7 .
  • the cuts 7 may either all be unidirectional (FIGS. 11, 13) or intersections in the opposite direction of the exhibition (FIGS. 9, 10) may be provided.
  • FIG. 13 shows an embodiment with a contour 35 in the wave flanks 3 , which are likewise provided with cuts 7 .
  • an offset 40 occurs between the air inlet 5 and the air outlet 6 .
  • FIG. 12 shows sections 7 , which have been exposed alternately from the plane 31 of the wave flanks 3 .
  • the deployment angle 12 can also change along the contour 35 , it can be larger or smaller.
  • Figs. 14, 15 and 16 show cross-sectional profiles of the corrugated fins 2 produced by rolling. A feature worth mentioning is shown in FIG. 16. One of the edges 23 is provided with a larger bending radius 22 than the other bending edge, so that the production by means of rollers is simplified. The release of the corrugated fin 2 from the roll tool has been facilitated.
  • FIGS. 17 and 18 show the production of corrugated fins 2 with planar corrugation flanks 3 , which have an inclination to the edges.
  • the rollers 100, 101 are formed with a corresponding helical toothing 103 .
  • the roll bodies 100, 101 consist of a corresponding multiplicity of disk-shaped parts 104 , which are assembled to form the roll body.
  • Each disc-shaped part 104 on the upper roller 100 cooperates knife-like with a corresponding part 104 on the lower roller 101 to produce the cuts 7 and their exposure from the plane 31 of the wave flanks 3 .
  • FIGS. 20 and 21 show corrugated fins 2 with a contour of the wave flanks 3 .
  • the contour of the helical gearing 103 must, of course, correspond to the contour on the wave flanks 3 .
  • the outlet of the finished corrugated fins 2 from the pair of rollers must be provided with an angle ⁇ corresponding to the angle of inclination.
  • FIG. 23 shows a plan view of a corrugated fin 2 with an arcuate contour 35 of the corrugation flanks 3 , as proposed in an independent alternative solution.
  • this variant of the corrugated fin 2 offers the advantages of the invention, so that the heat exchange between the media is increased by an extended path for the cooling air.
  • cuts 7 are provided, which are not shown. Which shape the contour 35 has depends on the technical possibilities.
  • the corrugated fins 2 according to the invention are produced inexpensively on a rolling machine with a relatively high feed rate.
  • Such rolling machines consist of the pair of rollers in a so-called roller mill and have a suitable drive unit. They are used for mass production and represent a considerable investment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP05003995A 2004-03-13 2005-02-24 Echangeur de chaleur et ailette ondulée Withdrawn EP1574801A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004012427A DE102004012427A1 (de) 2004-03-13 2004-03-13 Wärmetauschernetz und Wellrippe
DE102004012427 2004-03-13

Publications (2)

Publication Number Publication Date
EP1574801A2 true EP1574801A2 (fr) 2005-09-14
EP1574801A3 EP1574801A3 (fr) 2006-05-17

Family

ID=34813695

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05003995A Withdrawn EP1574801A3 (fr) 2004-03-13 2005-02-24 Echangeur de chaleur et ailette ondulée

Country Status (3)

Country Link
US (1) US20050199378A1 (fr)
EP (1) EP1574801A3 (fr)
DE (1) DE102004012427A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1793190A1 (fr) * 2005-12-03 2007-06-06 Modine Manufacturing Company Ailette pour échangeur de chaleur, procédé de fabrication et échangeur de chaleur
WO2012152265A1 (fr) * 2011-05-11 2012-11-15 Gea Energietechnik Gmbh Refroidisseur sec soumis à l'effet de l'air
EP2612100A2 (fr) * 2010-09-02 2013-07-10 EDC Automotive, LLC Échangeur de chaleur compact

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7267162B2 (en) * 2005-06-10 2007-09-11 Delphi Technologies, Inc. Laminated evaporator with optimally configured plates to align incident flow
US7540320B1 (en) * 2006-02-10 2009-06-02 Thomas Middleton Semmes High efficiency conditioning air apparatus
US20070240865A1 (en) 2006-04-13 2007-10-18 Zhang Chao A High performance louvered fin for heat exchanger
US20070246202A1 (en) * 2006-04-25 2007-10-25 Yu Wen F Louvered fin for heat exchanger
DE102007031675A1 (de) * 2007-07-06 2009-01-08 Behr Gmbh & Co. Kg Wärmeübertrager und Verfahren zur Herstellung einer Wellrippe
DE102009021177A1 (de) 2009-05-13 2010-11-18 Behr Gmbh & Co. Kg Rippe für einen Wärmetauscher
CN101975492A (zh) * 2010-10-19 2011-02-16 广东美的制冷设备有限公司 一种新型换热装置
DE102011004306A1 (de) * 2011-02-17 2012-08-23 Behr Gmbh & Co. Kg Rippe für einen Wärmeübertrager
EP3148828A1 (fr) * 2014-05-28 2017-04-05 RBC Green Energy II, LLC Système d'échange de chaleur refroidi par air
EP3575728B1 (fr) 2018-05-30 2020-12-16 Valeo Autosystemy SP. Z.O.O. Noyau d'un échangeur de chaleur comprenant des ailettes ondulées

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Publication number Priority date Publication date Assignee Title
US1454107A (en) * 1923-05-08 Mqoid-cooling radiator
US1458128A (en) * 1919-10-13 1923-06-12 Edward T Curran Radiator
FR565207A (fr) * 1923-04-18 1924-01-22 Radiateur pour moteurs à combustion interne d'automobiles
GB2027533B (en) * 1978-05-31 1982-12-22 Covrad Ltd Heat exchangers
JPS58178192A (ja) * 1982-04-14 1983-10-19 Nippon Radiator Co Ltd コルゲ−トフイン
US4657070A (en) * 1984-02-15 1987-04-14 Hudson Products Corporation Air-cooled vapor condensers
DE4142019A1 (de) * 1991-12-19 1993-06-24 Behr Gmbh & Co Wellrippe fuer flachrohrwaermetauscher
US5505257A (en) * 1993-06-18 1996-04-09 Goetz, Jr.; Edward E. Fin strip and heat exchanger construction
US5669438A (en) * 1996-08-30 1997-09-23 General Motors Corporation Corrugated cooling fin with louvers
US5765630A (en) * 1996-09-19 1998-06-16 Siemens Electric Limited Radiator with air flow directing fins
FR2757259B1 (fr) * 1996-12-18 1999-03-05 Valeo Thermique Moteur Sa Ailette metallique perfectionnee pour echangeur de chaleur, notamment pour vehicule automobile
JP4158225B2 (ja) * 1997-07-25 2008-10-01 株式会社デンソー 熱交換器および筐体冷却装置
AU4359000A (en) * 1999-04-19 2000-11-02 Peerless Of America, Inc. An improved fin array for heat transfer assemblies and method of making same
JP4041654B2 (ja) * 2001-01-31 2008-01-30 カルソニックカンセイ株式会社 熱交換器のルーバーフィンおよびその熱交換器並びにそのルーバーフィンの組付け方法
DE10249451A1 (de) * 2002-03-09 2003-09-18 Behr Gmbh & Co Wärmetauscher
JP2004177082A (ja) * 2002-11-29 2004-06-24 Matsushita Electric Ind Co Ltd 熱交換器

Non-Patent Citations (1)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1793190A1 (fr) * 2005-12-03 2007-06-06 Modine Manufacturing Company Ailette pour échangeur de chaleur, procédé de fabrication et échangeur de chaleur
EP2612100A2 (fr) * 2010-09-02 2013-07-10 EDC Automotive, LLC Échangeur de chaleur compact
EP2612100A4 (fr) * 2010-09-02 2014-10-29 Edc Automotive Llc Échangeur de chaleur compact
WO2012152265A1 (fr) * 2011-05-11 2012-11-15 Gea Energietechnik Gmbh Refroidisseur sec soumis à l'effet de l'air

Also Published As

Publication number Publication date
EP1574801A3 (fr) 2006-05-17
DE102004012427A1 (de) 2005-09-29
US20050199378A1 (en) 2005-09-15

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