WO2005066566A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

Info

Publication number
WO2005066566A1
WO2005066566A1 PCT/EP2004/013832 EP2004013832W WO2005066566A1 WO 2005066566 A1 WO2005066566 A1 WO 2005066566A1 EP 2004013832 W EP2004013832 W EP 2004013832W WO 2005066566 A1 WO2005066566 A1 WO 2005066566A1
Authority
WO
WIPO (PCT)
Prior art keywords
degrees
rib according
gills
section
inflow
Prior art date
Application number
PCT/EP2004/013832
Other languages
German (de)
English (en)
Inventor
Wolfgang Kramer
Original Assignee
Behr Gmbh & Co. Kg
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 Behr Gmbh & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to US10/585,665 priority Critical patent/US20080190589A1/en
Priority to EP04803542A priority patent/EP1706698A1/fr
Publication of WO2005066566A1 publication Critical patent/WO2005066566A1/fr

Links

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
    • 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
    • F28F3/027—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 with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • 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
    • F28F1/24—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
    • F28F2225/00—Reinforcing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped elements

Definitions

  • the invention relates to a heat exchanger, such as, in particular, a flat tube heat exchanger, and a fin, such as, in particular, a corrugated fin, for example for a flat tube heat exchanger, in particular for a coolant, charge air cooler or condensers or evaporators for motor vehicles according to the preamble of patent claim 1.
  • a heat exchanger such as, in particular, a flat tube heat exchanger
  • a fin such as, in particular, a corrugated fin, for example for a flat tube heat exchanger, in particular for a coolant, charge air cooler or condensers or evaporators for motor vehicles according to the preamble of patent claim 1.
  • Corrugated fins and flat tubes form a soldered cooling system in which a medium to be cooled, e.g. B. a coolant or charge air flows through the flat tubes and a cooling medium, eg. B. Ambient air flows over the corrugated fins.
  • a medium to be cooled e.g. B. a coolant or charge air flows through the flat tubes and a cooling medium, eg. B. Ambient air flows over the corrugated fins.
  • Such soldered cooling systems are used for coolant coolers for cooling an internal combustion engine or as charge air coolers for cooling the compressed intake air of internal combustion engines in motor vehicles.
  • Radiators or condensers or evaporators are also constructed similarly, for example.
  • Ribs can also be used in mechanically joined heat exchangers in which the ribs and the tubes of the heat exchangers are mechanically connected to one another.
  • the trend of development goes in the direction of higher pressures for the medium to be cooled, in particular in the coolant circuit, the flat tubes Because of the lower air pressure drop, they are extremely slim and therefore extremely unstable against increased internal pressure.
  • the flat tubes therefore tend to "inflate”, ie bulge when subjected to internal pressure. This bulge can be counteracted from the inside and outside
  • the flat tubes are covered with gills to improve the heat transfer, which has disadvantages in terms of strength.
  • the corrugated fins therefore buckle when the flat tubes are subjected to higher internal pressure.
  • EP 0 547 309 B1 from the applicant discloses a corrugated fin for flat tubes, in which a stiffening bead is arranged between two gill panels and in the middle of the flat tube, i. H. where the greatest buckling stress occurs for the corrugated fin.
  • a stiffening bead is arranged between two gill panels and in the middle of the flat tube, i. H. where the greatest buckling stress occurs for the corrugated fin.
  • this only results in a selective stiffening of the corrugated fin, which is no longer sufficient with increasing stress as a result of increased internal pressure.
  • the stiffening means are integrated in the gills, ie basically all gills of the corrugated fin contribute to the support effect.
  • the flat tubes are thus supported over their entire length by a stiffened corrugated fin.
  • Each individual gill advantageously has a kink-resistant profile, which gives the entire corrugated fin increased security against kinking.
  • the profile of each gill has an S-shaped cross section. This gives the advantage of a greater section modulus against buckling without significantly increasing the air-soapy pressure drop across the corrugated fin - on the contrary. a lower pressure drop can be expected.
  • the gill which is S-shaped in cross-section, thus has a variable gill angle - compared to the prior art - which initially rises from a very low value to a maximum value in the middle of the gill length and then decreases again to a minimum value. This results in a "gentle" deflection of the air flow without - as in the prior art - lossy eddies occurring at the leading and trailing edge of the gills.
  • An advantage is an unexpected combination effect in that the kink stiffness of the gills increases and whose pressure drop is reduced at the same time.
  • the cross section of the gills is angled twice and has an approximately Z-shaped course, i. H.
  • the gill angled according to the invention has three gill angles, the gill angle jumping from a low to a high value at the first kink and back to the low value at the second kink.
  • the Z-shape has an inconsistent course of the gill angle over the gill length compared to the S-shape, which simplifies production technology.
  • the advantage of increased buckling rigidity combined with a reduced pressure drop is also achieved here.
  • advantageous angular dimensions are given both for the S-shaped and for the Z-shaped cross section of the gill.
  • the low inflow and outflow angle is particularly advantageous because, as already mentioned, this avoids eddy formation behind the inflow and outflow edge.
  • the heat transfer performance of the corrugated fin is not deteriorated, since the thermal boundary layer is still started up on each leading edge of a gill. This mechanism is responsible for a large part of the heat transfer. This ultimately also has the advantage that the entire heat exchanger is improved in terms of its performance.
  • FIG. 1 shows a corrugated fin with gills according to the prior art in a view from the front
  • FIG. 2 shows the corrugated fin according to the prior art in a plan view
  • FIG. 3 shows a section through the corrugated fin according to FIG. 2 along the line III-III
  • FIG. 5 a corrugated fin according to the invention with an S-shaped cross section
  • FIG. 6 a corrugated fin according to the invention with a double kink cross section
  • Fig. 7 shows a detail X from Fig. 5 and
  • FIG. 8 shows a detail Y from FIG. 6.
  • Fig. 1 shows a corrugated fin 1 with gills 2 seen in the air flow direction.
  • the corrugated fin 2 is part of a cooling system, not shown, consisting of corrugated fins and flat tubes 3, which are indicated by dashed lines.
  • the corrugated fins are each arranged between two tubes.
  • the tubes are in turn connected in a fluid-tight manner to header boxes at their end regions.
  • the pipes are typically inserted into openings in the collecting box and connected to them in a fluid-tight manner.
  • the tubes are preferably pushed into a tube plate with openings and connected in a sealed manner, so that the fluid can get from one header box through the fluid connections within the tubes to the other header box.
  • the corrugated fin 1 and the flat tubes 3 preferably each consist of an aluminum material and are soldered to one another.
  • FIG. 2 shows the corrugated fin 1 in a plan view, the direction of air flow being represented by an arrow L.
  • the gills 2 form two gill arrays with front gills 2a and rear gills 2b.
  • Fig. 3 shows a section along the line III-III and the opposite gill angles ⁇ 1 and ⁇ 2 of the front gills 2a and the rear gills, 2b.
  • Fig. 4 shows the corrugated fin 1 according to the prior art and its loading by the flat tubes, not shown here, when these are subjected to internal pressure.
  • the load on the corrugated fin 1 is represented by arrows P1, P2, which each act on a fin arch 1 a, 1 b.
  • FIG. 5 shows a corrugated fin 5 according to the invention with front gills 6a and rear gills 6b, which have an S-shaped cross section.
  • the S-shaped cross-section is characterized by a constantly changing gill angle from the inlet to the outlet of the air flow.
  • An enlarged cross section is shown as detail X in FIG. 7 and is described in more detail there.
  • FIG. 6 shows a further embodiment of the invention, namely a corrugated fin 7 with front gills 8a and rear gills 8b, which are each angled twice, ie have a double kink.
  • the gill angle changes discontinuously in this double-knee gill 8a, 8b, ie in each case at the kink point.
  • An enlarged view is shown as detail Y in FIG. 8 and is described in more detail there.
  • FIG. 7 shows the detail X from FIG. 5, ie the gill 6a, which is arranged symmetrically upwards and downwards relative to a central plane e of the corrugated fin 5.
  • the S-shape of the gill 6a has an approximately sinusoidal shape and is characterized by three sections, namely an inflow area 9, a central deflection area 10 and an outflow area 11.
  • the slopes of the individual areas 9, 10, 11 are represented by straight lines a, b, c.
  • the inflow section 9 forms an inflow angle ⁇ s with the central plane e
  • the outflow region 11 forms an outflow angle ⁇ s with the central plane e, ie the angle between the straight lines c and e.
  • the central cross-sectional area 10 that is to say the deflection area, forms a deflection angle ⁇ s with the center plane e (angle between the straight lines b and e).
  • the angles ⁇ s are in a range from 0 to 10 degrees, preferably in a narrower range from 0 to 5 degrees.
  • the deflection angle ⁇ s is in a range from 15 to 35 degrees and preferably in a range from 20 to 30 degrees.
  • the air flow marked by an arrow L thus meets an extremely small inflow angle ⁇ s in the inflow region 9, so that no detachments and eddies form on the rear or suction side of the gill profile.
  • the inflow angle ⁇ s which corresponds to the gill angle ⁇ in the prior art, changes with increasing flow around the gill 6a up to the value ⁇ s and then decreases again to the value ⁇ s in the region 11. This also results in a non-detachable outflow of air.
  • the S-shaped cross section of the gill 6a results in an increased section modulus against buckling, ie a higher permissible buckling load - in comparison to the known rectangular cross section.
  • FIG. 8 shows the detail Y from FIG. 6, ie the corrugated fin 7 with gills 8a, which are angled twice and have a double kink cross section or an approximately Z-shaped course.
  • the center plane of the corrugated fin 7 is also marked with e here, ie as a reference plane for the individual angles.
  • the cross-section of the gill 8a is divided into three sections, namely an inflow section 12, a central deflection section 13 and an outflow section 14, all three sections 12, 13, 14 being approximately rectilinear and connected to one another by radii r.
  • the slopes of the individual sections 12, 13, 14 are marked by straight lines a, b, c and form the inflow and outflow angles ⁇ z and the deflection angle ßz with the reference plane e.
  • the air flow is again represented by an arrow L, and it can be seen that the inflow angle ⁇ z is relatively small, so that there are no or hardly any signs of separation of the flow on the suction side of the inflow section 12 and also the deflecting section 13. The air flow can therefore also be present on the suction side of the gill 8a, which results in a low pressure drop.
  • the inflow and outflow angles ⁇ z are in the range from 0 to 25 or preferably in the range from 5 to 15 degrees, and the deflection angle ⁇ z is in the range from 15 to 35 degrees or preferably in the range from 20 to 30 degrees.
  • This Z-shaped profile of the gill 8a also results in an increased resistance moment against buckling, which, with the number of gills, adds up to an increased total resistance moment against buckling for the entire rib.

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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)

Abstract

L'invention concerne un échangeur de chaleur et une nervure (1), notamment une nervure ondulée (1), destinée notamment à un échangeur de chaleur à tubes plats, en particulier un radiateur ou un refroidisseur d'air de suralimentation pour véhicules automobiles. La nervure ondulée (1) est placée entre des tubes plats (3) de l'échangeur de chaleur, raccordée à ces derniers par liaison de matière, pourvue d'ailettes (6,8), peut être exposée à un flux d'air et présente des moyens de renforcement moulés.
PCT/EP2004/013832 2004-01-07 2004-12-06 Echangeur de chaleur WO2005066566A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/585,665 US20080190589A1 (en) 2004-01-07 2004-12-06 Heat Exchanger
EP04803542A EP1706698A1 (fr) 2004-01-07 2004-12-06 Echangeur de chaleur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004001306A DE102004001306A1 (de) 2004-01-07 2004-01-07 Wärmeübertrager
DE102004001306.3 2004-01-07

Publications (1)

Publication Number Publication Date
WO2005066566A1 true WO2005066566A1 (fr) 2005-07-21

Family

ID=34716367

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/013832 WO2005066566A1 (fr) 2004-01-07 2004-12-06 Echangeur de chaleur

Country Status (4)

Country Link
US (1) US20080190589A1 (fr)
EP (1) EP1706698A1 (fr)
DE (1) DE102004001306A1 (fr)
WO (1) WO2005066566A1 (fr)

Cited By (5)

* 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
JP2012237537A (ja) * 2011-05-13 2012-12-06 Daikin Industries Ltd 熱交換器
DE102015205902A1 (de) 2015-04-01 2016-10-06 Mahle International Gmbh Rippe für einen Wärmeübertrager
US20190162483A1 (en) * 2017-11-29 2019-05-30 Honda Motor Co., Ltd. Cooling apparatus
DE112014003247B4 (de) 2013-07-12 2024-05-29 Denso Corporation Rippe für Wärmetauscher

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070240865A1 (en) 2006-04-13 2007-10-18 Zhang Chao A High performance louvered fin for heat exchanger
CN101846475B (zh) * 2009-03-25 2013-12-11 三花控股集团有限公司 用于热交换器的翅片以及采用该翅片的热交换器
JP5499957B2 (ja) * 2009-07-24 2014-05-21 株式会社デンソー 熱交換器
US20110226782A1 (en) * 2010-03-17 2011-09-22 Gm Global Technology Operations, Inc. Gas temperature moderation within compressed gas vessel through heat exchanger
EP2725311B1 (fr) 2012-10-29 2018-05-09 Samsung Electronics Co., Ltd. Échangeur de chaleur
JP6046558B2 (ja) * 2013-05-23 2016-12-14 カルソニックカンセイ株式会社 熱交換器
JP6327271B2 (ja) * 2015-04-17 2018-05-23 株式会社デンソー 熱交換器
DE102016210159A1 (de) * 2016-06-08 2017-12-14 Mahle International Gmbh Rippenelement für einen Wärmeübertrager
DE102017208324A1 (de) * 2017-05-17 2018-11-22 Mahle International Gmbh Wärmeübertrager
US11326842B2 (en) * 2018-09-21 2022-05-10 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner having the same

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US4365667A (en) * 1979-02-07 1982-12-28 Hitachi, Ltd. Heat exchanger
JPS5893A (ja) * 1981-06-24 1983-01-05 Hitachi Ltd 熱交換器用フイン
JPS59185992A (ja) * 1983-04-06 1984-10-22 Mitsubishi Electric Corp 熱交換器
JPS6152589A (ja) * 1984-08-22 1986-03-15 Nippon Denso Co Ltd 空気用熱交換器
US4614230A (en) * 1983-07-29 1986-09-30 Mitsubishi Denki Kabushiki Kaisha Heat exchanger
EP0234942A1 (fr) * 1986-02-28 1987-09-02 Showa Aluminum Kabushiki Kaisha Echangeur de chaleur à plaques
US5099914A (en) * 1989-12-08 1992-03-31 Nordyne, Inc. Louvered heat exchanger fin stock
EP0881450A1 (fr) * 1996-12-04 1998-12-02 Zexel Corporation Echangeur de chaleur
DE102004012796A1 (de) * 2003-03-19 2004-11-11 Denso Corp., Kariya Wärmetauscher und Wärmeübertragungselement mit symmetrischen Winkelabschnitten

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US4693307A (en) * 1985-09-16 1987-09-15 General Motors Corporation Tube and fin heat exchanger with hybrid heat transfer fin arrangement
US4958681A (en) * 1989-08-14 1990-09-25 General Motors Corporation Heat exchanger with bypass channel louvered fins
DE4142019A1 (de) * 1991-12-19 1993-06-24 Behr Gmbh & Co Wellrippe fuer flachrohrwaermetauscher
US6805193B2 (en) * 2002-01-24 2004-10-19 Valeo, Inc. Fin louver design for heat exchanger

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4365667A (en) * 1979-02-07 1982-12-28 Hitachi, Ltd. Heat exchanger
JPS5893A (ja) * 1981-06-24 1983-01-05 Hitachi Ltd 熱交換器用フイン
JPS59185992A (ja) * 1983-04-06 1984-10-22 Mitsubishi Electric Corp 熱交換器
US4614230A (en) * 1983-07-29 1986-09-30 Mitsubishi Denki Kabushiki Kaisha Heat exchanger
JPS6152589A (ja) * 1984-08-22 1986-03-15 Nippon Denso Co Ltd 空気用熱交換器
EP0234942A1 (fr) * 1986-02-28 1987-09-02 Showa Aluminum Kabushiki Kaisha Echangeur de chaleur à plaques
US5099914A (en) * 1989-12-08 1992-03-31 Nordyne, Inc. Louvered heat exchanger fin stock
EP0881450A1 (fr) * 1996-12-04 1998-12-02 Zexel Corporation Echangeur de chaleur
DE102004012796A1 (de) * 2003-03-19 2004-11-11 Denso Corp., Kariya Wärmetauscher und Wärmeübertragungselement mit symmetrischen Winkelabschnitten

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PATENT ABSTRACTS OF JAPAN vol. 007, no. 071 (M - 202) 24 March 1983 (1983-03-24) *
PATENT ABSTRACTS OF JAPAN vol. 009, no. 046 (M - 360) 27 February 1985 (1985-02-27) *
PATENT ABSTRACTS OF JAPAN vol. 010, no. 211 (M - 501) 24 July 1986 (1986-07-24) *

Cited By (5)

* 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
JP2012237537A (ja) * 2011-05-13 2012-12-06 Daikin Industries Ltd 熱交換器
DE112014003247B4 (de) 2013-07-12 2024-05-29 Denso Corporation Rippe für Wärmetauscher
DE102015205902A1 (de) 2015-04-01 2016-10-06 Mahle International Gmbh Rippe für einen Wärmeübertrager
US20190162483A1 (en) * 2017-11-29 2019-05-30 Honda Motor Co., Ltd. Cooling apparatus

Also Published As

Publication number Publication date
DE102004001306A1 (de) 2005-08-04
US20080190589A1 (en) 2008-08-14
EP1706698A1 (fr) 2006-10-04

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