EP2047198A1 - Refroidisseur pour liquide de refroidissement - Google Patents

Refroidisseur pour liquide de refroidissement

Info

Publication number
EP2047198A1
EP2047198A1 EP08759324A EP08759324A EP2047198A1 EP 2047198 A1 EP2047198 A1 EP 2047198A1 EP 08759324 A EP08759324 A EP 08759324A EP 08759324 A EP08759324 A EP 08759324A EP 2047198 A1 EP2047198 A1 EP 2047198A1
Authority
EP
European Patent Office
Prior art keywords
sheet metal
cooling
range
flat tube
flat tubes
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.)
Granted
Application number
EP08759324A
Other languages
German (de)
English (en)
Other versions
EP2047198B1 (fr
Inventor
Frank Opferkuch
Jan BÖBEL
Axel Fezer
Klaus Mohrlok
Ulrich SCHÄFFER
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 EP2047198A1 publication Critical patent/EP2047198A1/fr
Application granted granted Critical
Publication of EP2047198B1 publication Critical patent/EP2047198B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • 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
    • 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
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

Definitions

  • the invention relates to a coolant cooler for motor vehicles with a Gelo ⁇ ⁇ ended cooling network of flat tubes and fins made of very thin aluminum ⁇ sheets, and disposed at the ends of the flat tubes collector - or environmental steering boxes for the flowing in the flat tubes cooling liquid is cooled by means of cooling air flowing through the ribs.
  • the cooling liquid cooler described in the introduction represents the standard which has been in force for years in such heat exchangers. With the invention described below, this standard is not fundamentally changed but rather optimized in various respects.
  • Compact heat exchangers made of flat tubes and Venetian blind slats are known from the prior art for cooling the drive train of vehicles with internal combustion engines. These are able to achieve the highest cooling performance in the smallest space. In addition to a high volume-related power density, however, the lowest possible pressure loss on the coolant side and a low weight are the aim of an optimization. At the same time, for reasons of strength, in particular due to thermomechanical loads and due to the loads of the cooling network by pressure from the cooling system of the vehicle, the minimum wall thicknesses, in particular of the flat tubes, must be selected such that the same serve the other targets, such as, for.
  • the flat tubes often have no or only 1 to 2 internal supports.
  • the pipe heights are in the range of 1, 3 mm to 2.0 mm.
  • wall thicknesses greater than 0.20 mm are currently used.
  • the hydraulic diameter (4 x flow area / wetted circumference) is a characteristic variable for the hydraulic behavior.
  • hydraulic diameters of 1, 3 mm to 3.0 mm typically result on the coolant side.
  • a coolant radiator having all but one feature of all other features of the preamble of claim 1 is known from US 4,332,293.
  • the flat tubes are made of brass and the ribs of copper. Thisdeckenkeitkühler is therefore too heavy and too expensive. The same applies to thedefactkeitsküh- ler, which is known from US 5,329,988.
  • Another cooling liquid cooler is known from US 4,693,307. In it, a solution is presented, which limits the cooling air-side pressure loss by special design of the ribs.
  • the design of the flat tubes used was apparently not of particular interest indeckenkeitsksselern, because in the specified sources flat tubes have been shown and described without any peculiarities.
  • the object of the invention is to provide a cost-effectivechen-liquid cooler for motor vehicles whose properties such as in particular high heat transfer performance at comparatively low weight to meet the future demands of users in several respects.
  • the inventive solution of the problem arises in a trained according to the preamble of claim 1deflüsskühler by its design with the characterizing features of the same claim.
  • Each flat tube consists of at least two formed sheet metal strips, wherein at least one of the sheet metal strips forms the wall of the flat tube and another sheet metal strip forms a corrugated, inner channels forming channels therein.
  • the ratio of the constriction factor on the coolant side to the constriction factor on the cooling air side is approximately in the range between 0.20 to 0.44.
  • each flat tube consists of three deformed sheet-metal strips, wherein two sheet-metal strips form the wall of the flat tube and the third sheet-metal strip represents the corrugated, inner channels forming the inner channel.
  • the wall thickness of the flat tube is in the range of 0.10-0.20 mm.
  • the thickness of the inner insert is in the range of 0.03 - 0.10 mm. Because the inner liner can be made from thinner sheet metal, the possibility of weight reduction is extended without neglecting the strength.
  • the constriction factor is in a range between 0.15 and 0.28. On the cooling air side, however, the constriction factor is in a range between 0.63 and 0.76.
  • the constriction factor is calculated as the ratio of the area through which flows through to the entire end face F of the respective media side.
  • A is the area flowed through.
  • U is the wetted circumference of the area through which it flows.
  • FIG. 1 shows a view of a cooling liquid cooler according to the invention.
  • 2 shows a cross section through a flat tube of theharides and others.
  • FIGS. 3 and 4 show sections of the cooling network of the cooling liquid cooler according to the invention.
  • FIGS. 5 to 11 are graphs showing the difference between the flat tubes of the cooling liquid cooler of the present invention and the flat tubes of conventional cooling liquid coolers in several respects.
  • Fig. 12 shows another flat tube of another cooling liquid cooler according to the invention.
  • FIG. 5 illustrates evaluations of extensive FEM examinations carried out by the inventors.
  • FIG. 5 illustrates that the flat tubes 101 of the inventive coolant radiator, because of their inner insert c, the is made of a metal strip which is about 0.03 - 0.10 mm thick is much lighter (ordinate) than conventional flat tubes ordewashkeitkühler. At the same time, they can withstand higher internal pressures (abscissa). With regard to the internal pressure stability, the overlapping of the metal strips a, b, in the narrow sides S of the flat tubes 101 proves to be, which will be discussed in more detail below.
  • FIGS. 6 and 7 represent the evaluation of extensive thermo-hydraulic calculations.
  • FIG. 6 makes it clear that cooling liquid coolers according to the invention with such flat tubes 101, at approximately identical pressure loss, have a significantly higher specific cooling capacity than the prior art.
  • the upper cloud results represents thedeckenkeitkühler invention, including the prior art.
  • FIG. 7 permits an identical statement, wherein, in contrast to FIG. 6 in FIG. 7, the abscissa represents the pressure loss in the cooling air.
  • the cooling capacity is related to the inlet temperature difference ETD and to the mass of the cooling network.
  • the operating point was a coolant flow of 160kg / (m 2 s) and a cooling air flow of 8.0 kg / (m 2 s).
  • the investigated cooling grid dimensions were 600 mm flat tube length, 445 mm net width and 32 mm net depth.
  • the ratio of the two constriction factors on the ordinate with respect to the hydraulic diameters on the coolant side is considered.
  • An optimum in terms of compactness, lightweight construction and performance has been found when the hydraulic diameter is approximately between 0.8 and 1.5 mm and the mentioned ratio is in the range between 0.20 and 0.44.
  • 11 is intended to show that flat tubes 11, whose inner inserts c have a pitch T (FIG. 2) between 1, 2 and 3, 5 mm, with a tube height h in the range between 1, 1 mm and about 2.0 mm have occurred particularly frequently in relation to the advantageous properties described above.
  • Fig. 1 shows a front view of the cooling liquid cooler according to the invention.
  • the surface of the cooling network, which was affected by cooling air, was framed with a dashed line.
  • This area F is the end face which is used to determine the constriction factor on the cooling air side.
  • the counter is then the sum of the areas which are traversed by the cooling air, which are directed to the cooling air surfaces of all ribs 102, in other words, the end face F minus the areas occupied by the narrow sides of all flat tubes 101 of theissernet- zes become.
  • the flat tube of Fig. 2 is made of three endless metal strips.
  • Two wall parts rolled in the manner of a sheet-like edge are identically designed but arranged "reversed", one edge of one part encompassing one edge of the other part and the other edge of one part being encompassed by the other edge of the other part 3 and 4 show a section of the cooling network 1, consisting of flat tubes 101 and ribs 102.
  • the ribs 102 are so-called blind ribs 102 which have cuts in the rib flanks 3 and 4 have been indicated by the numerous parallel lines
  • the rib height H was set between 3 and 8 mm, whereby for inserts in the passenger car range 3 to 5.2 mm are cheaper. For commercial vehicles, for example, rib heights of up to 8 mm can be used.
  • the area F was indicated by a dashed line, which is used to determine the Kühifiüsstechniks remedyen constriction factor. This surface F corresponds approximately to the area which is encompassed by the collecting box 3 on the outside.
  • the sum of the area occupied by the flat tube sections is set in relation to the area F and gives the constriction factor on the cooling liquid side.
  • Their flat, that is, undeformed broadsides B have also proven to be an advantageous embodiment of the flat tubes 101, which with the venetian blind ribs 102 permit perfect solder joints, which noticeably contribute to achieving high heat transfer rates.
  • Narrow side S leads.
  • This metal strip a has a thickness of 0.12 mm.
  • the inner strip c forming sheet metal strip c is about 0.09 mm thick. It is wavy and created with its one longitudinal edge in the aforementioned bend B inside.
  • the flat tube is closed, wherein the second narrow side S is formed by nesting the formed longitudinal edges of a sheet metal strip a. All flat tubes have the advantage that their narrow sides S are very stable despite the small sheet thicknesses, as the two figures 2 and 12 show.

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)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un refroidisseur pour liquide de refroidissement de véhicules automobiles, qui présente un réseau brasé de refroidissement (1) constitué de tubes plats (101) et de nervures (102) en tôle d'aluminium très mince (a, b, c) et de caissons de collecte et de renvoi (3) pour le liquide de refroidissement qui s'écoule dans les tubes plats (101) disposés aux extrémités des tubes plats (101) et refroidis par de l'air de refroidissement qui s'écoule entre les nervures (102). Le refroidisseur de liquide de refroidissement possède une excellente capacité de refroidissement et présente un poids réduit. Selon l'invention, on obtient ce résultat grâce au fait que chaque tube plat (101) est constitué d'au moins deux rubans de tôle (a, b, c) façonnés, au moins l'un des rubans de tôle (a, b) formant la paroi du tube plat et l'autre ruban de tôle une garniture intérieure ondulée (c) qui forme des canaux (10), et grâce au fait que le rapport entre le facteur de rétrécissement du côté du liquide de refroidissement et le facteur de rétrécissement du côté de l'air de refroidissement est sensiblement compris dans la plage comprise entre 0,20 et 0,44, le diamètre hydraulique du côté du liquide de refroidissement étant compris sensiblement dans la plage comprise entre 0,8 et 1,5 mm.
EP08759324.0A 2007-07-17 2008-06-24 Refroidisseur pour liquide de refroidissement Not-in-force EP2047198B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007033177A DE102007033177A1 (de) 2007-07-17 2007-07-17 Kühlflüssigkeitskühler
PCT/EP2008/005065 WO2009010155A1 (fr) 2007-07-17 2008-06-24 Refroidisseur pour liquide de refroidissement

Publications (2)

Publication Number Publication Date
EP2047198A1 true EP2047198A1 (fr) 2009-04-15
EP2047198B1 EP2047198B1 (fr) 2016-10-26

Family

ID=39735353

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08759324.0A Not-in-force EP2047198B1 (fr) 2007-07-17 2008-06-24 Refroidisseur pour liquide de refroidissement

Country Status (6)

Country Link
US (1) US8522862B2 (fr)
EP (1) EP2047198B1 (fr)
CN (1) CN101755184B (fr)
BR (1) BRPI0813528B1 (fr)
DE (1) DE102007033177A1 (fr)
WO (1) WO2009010155A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001566A1 (de) * 2010-02-04 2011-08-04 Behr GmbH & Co. KG, 70469 Flachrohr für einen Niedertemperaturkühler
EP2670542B1 (fr) * 2011-01-31 2020-10-07 MAHLE International GmbH Procédé de fabrication de tube à double nez pour échangeur de chaleur
CN102116591A (zh) * 2011-03-09 2011-07-06 甘肃蓝科石化高新装备股份有限公司 一种空冷器用双面翅片板管结构
US20150144309A1 (en) * 2013-03-13 2015-05-28 Brayton Energy, Llc Flattened Envelope Heat Exchanger
PL228722B1 (pl) * 2014-12-30 2018-04-30 Valeo Autosystemy Spolka Z Ograniczona Odpowiedzialnoscia Żebro turbulizujące dla zespołu rurowo-żebrowego przystosowanego dla wymiennika ciepła, walec kształtujący żebro turbulizujące oraz zespół składający się z rury dla wymiennika ciepła i żebra turbulizującego oraz wymiennik ciepła
KR20170015146A (ko) * 2015-07-31 2017-02-08 엘지전자 주식회사 열교환기
JP2018009731A (ja) * 2016-07-13 2018-01-18 株式会社ティラド 熱交換器のコア部構造
NL2018753B1 (en) * 2017-04-20 2018-05-08 Apex Int Holding B V Gas Flow Conditioner Device for a Heat Exchanger
EP3473961B1 (fr) 2017-10-20 2020-12-02 Api Heat Transfer, Inc. Échangeur de chaleur
EP3521745B1 (fr) * 2018-02-06 2022-10-05 Valeo Autosystemy SP. Z.O.O. Ensemble ailette et tube plat d'un échangeur de chaleur

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Publication number Priority date Publication date Assignee Title
GB1027366A (en) * 1962-11-24 1966-04-27 Svenska Metallverken Ab An improved radiator and method of making it
JPS56155391A (en) 1980-04-30 1981-12-01 Nippon Denso Co Ltd Corrugated fin type heat exchanger
US4693307A (en) 1985-09-16 1987-09-15 General Motors Corporation Tube and fin heat exchanger with hybrid heat transfer fin arrangement
US5185925A (en) * 1992-01-29 1993-02-16 General Motors Corporation Method of manufacturing a tube for a heat exchanger
US5329988A (en) 1993-05-28 1994-07-19 The Allen Group, Inc. Heat exchanger
JP2001165587A (ja) * 1999-12-06 2001-06-22 Mitsubishi Heavy Ind Ltd 熱交換器用チューブ
JP2001165532A (ja) 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
WO2005022064A1 (fr) * 2003-08-26 2005-03-10 Valeo, Inc. Echangeur thermique en aluminium et son procede de fabrication

Non-Patent Citations (1)

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Title
See references of WO2009010155A1 *

Also Published As

Publication number Publication date
EP2047198B1 (fr) 2016-10-26
DE102007033177A1 (de) 2009-01-22
WO2009010155A1 (fr) 2009-01-22
CN101755184B (zh) 2013-01-23
BRPI0813528A2 (pt) 2014-12-23
US20100218926A1 (en) 2010-09-02
BRPI0813528B1 (pt) 2019-02-05
CN101755184A (zh) 2010-06-23
US8522862B2 (en) 2013-09-03

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