EP0203458B1 - Platten- und Rippenwärmetauscher - Google Patents

Platten- und Rippenwärmetauscher Download PDF

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Publication number
EP0203458B1
EP0203458B1 EP19860106558 EP86106558A EP0203458B1 EP 0203458 B1 EP0203458 B1 EP 0203458B1 EP 19860106558 EP19860106558 EP 19860106558 EP 86106558 A EP86106558 A EP 86106558A EP 0203458 B1 EP0203458 B1 EP 0203458B1
Authority
EP
European Patent Office
Prior art keywords
projections
heat exchanger
projection
arched
connecting wall
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.)
Expired
Application number
EP19860106558
Other languages
English (en)
French (fr)
Other versions
EP0203458A1 (de
Inventor
Kaoru Hasegawa
Suzushi Hashimoto
Shozo Uto
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.)
Showa Aluminum Can Corp
Original Assignee
Showa Aluminum Corp
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
Priority claimed from JP60104768A external-priority patent/JPS61262593A/ja
Priority claimed from JP8447386A external-priority patent/JPS62238996A/ja
Application filed by Showa Aluminum Corp filed Critical Showa Aluminum Corp
Publication of EP0203458A1 publication Critical patent/EP0203458A1/de
Application granted granted Critical
Publication of EP0203458B1 publication Critical patent/EP0203458B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • 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
    • F28D1/0366—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 spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers

Definitions

  • the present invention relates to heat-exchangers of the plate fintype, for example, for use in oil coolers and the like.
  • aluminum as herein used includes aluminum and aluminum alloys.
  • Conventional oil coolers made, for example, of aluminum have first flow channels for passing an oil therethrough and second flow channels for passing air therethrough in a direction intersecting the first channels at right angles therewith, the first and second channels being arranged alternately one above the other as separated by a flat plate.
  • Each of these flow channels is formed by a pair of flat plates disposed in parallel with each other at a specified spacing, spacer bars provided between the flat plates and serving as opposite side walls, and corrugated fins arranged between the spacer bars.
  • the spacer bars and the corrugated fins are joined together, for example, by vacuum brazing, as held between the flat plates each comprising an aluminum brazing sheet.
  • the conventional oil cooler is composed of a large number of parts, therefore requires much time for setting the parts, is not easily settable automatically, is inefficient to fabricate and is heavy.
  • the conventional oil cooler has fins such as mul- tientry fins (offset fins) within the oil passing first flow channels.
  • the conventional fins which have projections at a small spacing, afford a relatively large amount of heat exchange to achieve a high efficiency, whereas they result in a very great pressure loss, consequently requiring an increased pump output pressure to maintain the desired oil pressure and entailing a corresponding increase in equipement cost as well as in power cost.
  • the pressure loss may be diminished by increasing the spacing between the fin projections, but a reduced heat exchange efficiency will then result.
  • a heat exchanger of the type specified in the first part of claim 1 is disclosed in the document FR-A-2 365 092.
  • the side walls of each flow channel are formed integrally with one of the adjoining flat plates.
  • the free ends of the side walls are bent inwardly to press a corrugated fin member interposed in the flow channel as well as the side edges of the nextflat plate.
  • the necessity of bending the side walls during the assembly of the heat exchanger requires a complicated production process.
  • the fin member is corrugated in the transverse direction of the flow passage and only provides a poor heat exchange.
  • the document DE-B-1 074 063 discloses a plate like fin member which is provided with rows of alternating upward and downward arched projections that are arranged in rows in the transverse direction of the flow passage.
  • the adjacent projections of each row are interconnected through flat portions that extend in the direction of fluid flow.
  • the upward and downward projections of the different rows are arranged in a staggered relationship, so that an upward projection of one row is adjacent to a downward projection of the neighbouring row.
  • the projections form continuous flow channels in the direction of a fluid flow, so that the amount of tur- bulance caused by the projections and hence the heat exchange efficiency is comparatively small.
  • the main object of the present invention is to provide a heat exchanger of the plate fin type which is free of the foregoing problems.
  • this object is achieved by a heat exchanger that has the features specified in claim 1.
  • the plate fin heat exchanger of the present invention is composed of a decreased number of parts which are readily settable automatically within a greatly shortened period of time.
  • the heat exchanger can therefore be manufactured with an increased efficiency.
  • the heat exchanger permits oil or like fluid to pass therethrough as disturbed fully and very effectively while allowing the fluid to smoothly flow therethrough with a greatly reduced pressure loss to achieve an increased amount of heat exchange without necessitating a higher pump output pressure. Accordingly, the heat exchanger is low in equipment costs and power cost and is economical, while the device can be fabricated with a reduced amount of material, which renders the device lightweight and less costly.
  • a plate fin heat exchanger 1 of the present invention is used, for example, as an oil cooler and has first flow channels A and second flow channels B arranged alternately one above another and separated by plates 2 each comprising an aluminum brazing sheet. An oil is passed through the first flow channels A, while air is passed through the second flow channels B.
  • the channels A and B are so arranged that the fluids are passed in directions intersecting each other at right angles.
  • Each first flow channel A is formed by two adjacent flat plates 2 positioned one above the other and opposed right and left side walls 3 provided between the plates 2.
  • the side walls 3 and a platelike connecting wall 4 interconnecting these walls are integrally made of an aluminum extruded material.
  • the connecting wall 4 has a multiplicity of arched projections 5 having an upwardly projecting and approximately inverted V-shaped section and a multiplicity of like projections 5 having a downwardly projecting and approximately V-shaped section.
  • the wall 4 has a fluid passage 6 opposed to each arched projection 5.
  • each flow channel B is formed by two adjacent flat plates 2 positioned one above the other and opposed front and rear side walls 8 provided between these plates 2 and made of extruded aluminum material.
  • a louvered corrugated fin 9 Provided between the opposed front and rear walls 8 is a louvered corrugated fin 9 having ridges and furrows in parallel with these walls 8.
  • the connecting wall 4 of the present embodiment has a plurality of rows R of such projections, each row R including a multiplicity of upwardly and downwardly projecting arched projections 5 arranged in the front-to-rear direction.
  • Each of the arched projections 5 has a wall thickness t of 0.5 to 1.5 mm, a width W of t to 10t and a height H of 2to 10 mm.
  • the projections 5 in each row R are arranged at a pitch P of 3 to 30 mm.
  • the wall thickness t of the arched projection 5 is less than 0.5 mm, the projection, which is excessively thin, is likely to break while it is being so shaped, whereas if it is more than 1.5 mm, the projection 5 is too thick and difficult to shape, necessitating an increased amount of aluminum material to result in an increased cost.
  • the width W of the arched projection 5 is as small as less than t (equal to the wall thickness), a lower heat exchange efficiency will result, whereas if it is in excess of 10t (10 times the wall thickness), the excessively wide projections result in a greater pressure loss.
  • the projections 5 result in an impaired heat exchange efficiency and provide narrow fluid passages to impede smooth flow of the fluid.
  • Heights H exceeding 10 mm are not desirable since the strength against pressure will then decrease. If the pitch P of the projections 5 is as small as less than 3 mm, an increased pressure loss will then result, while the projections 5 will not be shaped satisfactorily. When the pitch P is in excess of 30 mm, reduced strength against pressure and impaired heat exchange efficiency will result, hence objectionable.
  • each projection row R of the connecting wall 4 there remains a horizontal portion 7 between each upwardly projecting arched projection 5a and the downwardly projecting arched projection 5b immediately adjacent thereto.
  • the oil through the first flow channel A flows in the direction of the rows R, and the walls of the arched projections 5a and 5b are opposed to the flow of the oil.
  • the upward projections 5a, as well as the downward projections 5b, of the rows R immediately adjacent to each other transversely of the rows are in a staggered arrangement, and each upward projection 5a is immediately adjacent to the downward projection 5b in the transverse direction.
  • the arched projection 5 may be in the shape of ⁇ or v .
  • the fluid passage 6 opposed to each arched projection 5 communicates with an opening at each side of the projection 5, permitting the oil to readily flow into the passage 6.
  • the opposed side walls 3 and the platelike wall 4 interconnecting these walls 3 are made integrally of an extruded aluminum material.
  • the multiplicity of upward and downward arched projections 5a, 5b are shaped in the connecting wall 4 by a press or forming rolls while forming the fluid passages 6 identical in number to the number of projections, with horizontal portions 7 of specified width left between the projections 5a and 5b. Since the multiplicity of projections 5a, 5b are formed by cutting and raising the planar connecting wall 4, the flow channel can be formed with use of a reduced amount of material, consequently rendering the heat exchanger 1 lightweight.
  • the heat exchanger 1 can be fabricated by arranging in superposed layers flat plates 2 each in the form of an aluminum brazing sheet, pairs of opposed side walls 3 each having the connecting wall 4 formed with arched projections 5, and pairs of front and rear walls 8 each having the louvered corrugated fin 9, and joining the components together, for example, by vacuum brazing.
  • the smallest heat exchanger 1 theoretically has one first flow channel A and one second flow channel B.
  • the heat exchanger 1 if small, has 3 to 20 first flow channels A and 3 to 20 second flow channels B.
  • the heat exchanger is 21 to 50 in the number of channels A as well as of channels B.
  • the number is 51 to 100 for heat exchangers of large size. Since the flow channels A and B are arranged alternately, the two types of channels are equal in number, or one is larger than the other in number by only one.
  • Such numbers of channels A and B are mentioned only as examples; the number of channels A, as well as of channels B, is determined according to the size and efficency of the contemplated heat exchanger 1.
  • a plurality of channels of one type are arranged as superposed for each of channels of the other type.
  • the top ends of the arched projections 5 of the connecting wall 4 are usually joined to the flat plate 2 by the brazing material layer, but the projection top ends may be held out of contact with the flat plate 2.
  • the heat exchanger can be fabricated alternatively by using aluminum plates as the flat plates 2 in place of aluminum brazing sheets, applying with a brush a brazing material to the upper and lower surfaces of the opposed side walls 3 and of front and rear walls 8, and joining the parts together with the layer of brazing material.
  • the opposite ends of the oil passing first flow channels A are made to communicate with an unillustrated header tank, and oil is passed through the channels A by a pump having a predetermined output pressure.
  • the air passing second flow channels B are left open at their opposite ends, and air is passed through the cannels B forcedly by a fan or spontaneously owing to the travel of the vehicle or the like in which the exchanger is installed.
  • the horizontal portion 7 of specified width is provided between each two adjacent projections 5a, 5b in each row R, the upward projections 5a and the downward projections 5b of the rows R immediately adjacent to each other transversely of the rows are in a staggered arrangement, each upward projection 5a is adjacent to two downward projections 5b at its right and left sides, each downward projection 5b is adjacent to two upward projections 5a at its right and left sides, and each of the projections 5a, 5b has at each side thereof a wide space S corresponding to one projection 5 and front and rear two horizontal portions 7.
  • This arrangement permits the oil to flow around the opposite sides of each projection 5 very smoothly without resulting in pressure loss.
  • the heat exchanger 1 of the above embodiment was equivalent to or up to 7% higher,than conventional oil coolers in heat release efficiency (heat exchange efficiency) and was 10 to 30% smaller in pressure loss. Accordingly, the heat exchanger is usable with a pump of lower output pressure and assures savings in equipment cost and power cost.
  • the heat exchanger 1 described above is useful as an oil cooler, for example, for cooling engine oil, for cooling industrial machines and for cooling the oil of various hyraulic systems.
  • the lengthwise direction of the arched projections 5a, 5b in each row R matches the direction of flow of oil in the case of the illustrated heat exchanger 1
  • these projections 5a, 5b may be arranged as inclined by a small angle with respect to the direction of the oil flow insofar as the oil can be disturbed and agitated effectively as desribed above.
  • the first flow channel A only is composed of two flat plates 2 positioned one above the other and opposed side walls 3 provided between the plates 2 and having a connecting wall 4 formed with a multiplicity of arched projections 5a, 5b and fluid passages 6, whereas the second flow channel B also may have the same construction as the channel A when so required.
  • first and second flow channels A, B of the illustrated heat exchanger 1 are arranged in directions intersecting each other at right angles, the two types of channels A, B may be arranged in parallel. In this case, two fluids are passed through the channels A, B concurrently or in opposite directions.
  • the illustrated heat exchanger 1 is useful as an oil cooler of the horizontal type with the first flow channels A in a horizontal position, the heat exchanger 1 may alternatively be used as an oil cooler of the vertical type with the first flow channels A positioned vertically. Further the heat exchanger, which is useful as an oil cooler, is also usable for various applications for effecting heat exchange between different kinds of gases and fluids.

Claims (6)

1. Platten- und Rippenwärmetauscher mit einem ersten Strömungskanal (A) und einem zweiten Strömungskanal (B), die durch wenigstens drei parallel in vorgegebenem Abstand zueinander angeordnete flache Platten (2) und zwischen den benachbarten flachen Platten vorgesehene gegenüberliegende Seitenwände (3, 8) gebildet werden, und einer plattenförmigen Verbindungswand (4), die in wenigstens einem der ersten und zweiten Strömungskanäle (A, B) angeordnet ist und die gegenüberliegenden Seitenwände verbindet, dadurch gekennzeichnet, dass
- die Seitenwände (3, 8) und die Verbindungswand (4) in einem Stück aus einem extrudierten Aluminiummaterial gebildet und zwischen den benachbarten flachen Platten (2) eingefügt sind,
- und dass die Verbindungswand (4) mit einer Anzahl bogenförmiger Vorsprünge (5) versehen ist, die mehrere in Strömungsrichtung des Fluids angeordnete Reihen (R) von Vorsprüngen bilden, wobei zwischen den in Längrichtung zueinander benachbarten bogenförmigen Vorsprüngen flache Abschnitte (7) verbleiben, die im wesentlichen rechtwinklig zu den Reihen (R) von Vorsprüngen verlaufen.
2. Wärmetauscher nach Anspruch 1, bei dem jeder der bogenförmigen Vorsprünge (5) der Verbindungswand eine Wanddicke von 0,5 bis 1,5 mm, eine Breite vom 1 - bis 1 Ofachen der Wanddicke und eine Höhe von 2 bis 10 mm aufweist und die Vorsprünge in Längsrichtung des Wärmetauschers in Abständen von 3 bis 30 mm angeordnet sind.
3. Wärmetauscher nach Anspruch 1 oder 2, bei dem die bogenförmigen Vorsprünge der Verbindungswand (4) in jeder Reihe (R) abwechselnd nach oben und nach unten weisen.
4. Wärmetauscher nach Anspruch 3, bei dem die nach oben weisenden bogenförmigen Vorsprünge (5a) sowie die nach unten weisenden bogenförmigen Vorsprünge (5b) der zueinander benachbarten Reihen (R) in Querrichtung der Reihen gestaffelt angeordnetsind und jeder nach oben weisende Vorsprung in Querrichtung einem nach unten weisenden Vorsprung benachbart ist.
5. Wärmetauscher nach einem der vorstehenden Ansprüche, mit abwechselnd angeordneten ersten Strömungskanälen (A) und zweiten Strömungskanälen (B).
6. Verfahren zum Herstellen eines Wärmetauschers nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass
- die gegenüberliegenden Seitenwände (3, 8) der plattenförmigen Verbindungswand (4) einstückig aus einem extrudierten Aluminiummaterial hergestellt werden und die bogenförmigen Vorsprünge (5) durch Einschneiden und Ausbiegen der Verbindungswand geformt werden.
EP19860106558 1985-05-15 1986-05-14 Platten- und Rippenwärmetauscher Expired EP0203458B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP104768/85 1985-05-15
JP60104768A JPS61262593A (ja) 1985-05-15 1985-05-15 熱交換器
JP84473/86 1986-04-11
JP8447386A JPS62238996A (ja) 1986-04-11 1986-04-11 プレート・フィン型熱交換器

Publications (2)

Publication Number Publication Date
EP0203458A1 EP0203458A1 (de) 1986-12-03
EP0203458B1 true EP0203458B1 (de) 1988-08-24

Family

ID=26425512

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860106558 Expired EP0203458B1 (de) 1985-05-15 1986-05-14 Platten- und Rippenwärmetauscher

Country Status (2)

Country Link
EP (1) EP0203458B1 (de)
DE (1) DE3660604D1 (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3641458A1 (de) * 1986-12-04 1988-06-09 Funke Waerme Apparate Kg Plattenwaermeaustauscher
JPH0539323Y2 (de) * 1987-05-29 1993-10-05
DE3936800A1 (de) * 1989-11-04 1991-05-08 Funke Waerme Apparate Kg Plattenwaermeaustauscher
CA2214255C (en) * 1997-08-29 2004-11-02 Long Manufacturing Ltd. Heat exchanger turbulizers with interrupted convolutions
FR2845152B1 (fr) * 2002-10-01 2005-06-17 Air Liquide Echangeur de chaleur a plaques comportant une ailette epaisse, et utilisation d'un tel echangeur de chaleur.
FR2845153B1 (fr) * 2002-10-01 2005-11-18 Nordon Cryogenie Snc Ailette pour echangeur de chaleur a plaques, procedes de fabrication d'une telle ailette, et echangeur de chaleur comportant une telle ailette
DE102010046913A1 (de) 2010-09-29 2012-03-29 Hydac Cooling Gmbh Wärmetauscher
ITPR20120081A1 (it) * 2012-11-22 2014-05-23 Orlandi Radiatori S R L Scambiatore di calore e metodo per realizzarlo
DE102013010867B4 (de) * 2013-06-28 2015-11-12 Protonet GmbH Anordnung zum Kühlen von in einem Gehäuse anordnenbaren elektrischen und/oder elektronischen Bauteilen und Rechner mit einer solchen
FR3063767B1 (fr) 2017-03-13 2019-04-26 Safran Aircraft Engines Aube directrice de sortie pour turbomachine d'aeronef, a fonction amelioree de refroidissement de lubrifiant

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1074063B (de) * 1960-01-28 GEA-I uftkuhler Gesellschaft m b H Bochum Plattenwarmeaustauscher mit einteiligen die Platten distanzierenden Flachengittern die quer zur Stromungsnchtung nach entgegengesetzten Seiten herausgebogene Flachenabschmite auf weisen
US1899080A (en) * 1931-10-29 1933-02-28 Res & Dev Corp Heat exchange device
DE1104542B (de) * 1955-10-17 1961-04-13 Modine Mfg Co Waermeaustauscher aus zwei ineinandergesteckten Rohren, in deren ringfoermigem Mantelraum zur Verwirbelung dienende Einlagen vorgesehen sind
FR2085173A1 (en) * 1969-12-24 1971-12-24 Nord Aviat Monobloc heat exchanger prodn - esp for aircraft cabin air conditioner circuits
US3768149A (en) * 1972-10-30 1973-10-30 Philco Ford Corp Treatment of metal articles
CH610648A5 (en) * 1976-09-21 1979-04-30 Sulzer Ag Heat exchanger, in particular for ventilating equipment
WO1981000148A1 (en) * 1977-05-19 1981-01-22 E Dubrovsky Lamellar-type heat exchanger
SU1022765A1 (ru) * 1980-12-10 1983-06-15 Предприятие П/Я А-1697 Устройство дл изготовлени ленты с гофрами,расположенными в шахматном пор дке
JPS58156197A (ja) * 1982-03-10 1983-09-17 Sumitomo Light Metal Ind Ltd 超高圧用プレ−トフイン型熱交換器
FR2536524A1 (fr) * 1982-11-19 1984-05-25 Nibart Jean Clair Element de garnissage pour echangeur de chaleur et echangeur de chaleur le comprenant
GB2132748B (en) * 1982-12-24 1986-04-30 Terence Peter Nicholson Improvements relating to heat exchangers

Also Published As

Publication number Publication date
EP0203458A1 (de) 1986-12-03
DE3660604D1 (en) 1988-09-29

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