EP0447528B1 - Fahrzeugkondensator - Google Patents

Fahrzeugkondensator Download PDF

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Publication number
EP0447528B1
EP0447528B1 EP90914931A EP90914931A EP0447528B1 EP 0447528 B1 EP0447528 B1 EP 0447528B1 EP 90914931 A EP90914931 A EP 90914931A EP 90914931 A EP90914931 A EP 90914931A EP 0447528 B1 EP0447528 B1 EP 0447528B1
Authority
EP
European Patent Office
Prior art keywords
elongated
plates
hollow portions
hollow
condenser
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 - Lifetime
Application number
EP90914931A
Other languages
English (en)
French (fr)
Other versions
EP0447528A1 (de
Inventor
Paul K. Beatenbough
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.)
Valeo Thermique Moteur SA
Valeo Engine Cooling Inc
Original Assignee
Valeo Thermique Moteur SA
Valeo Engine Cooling Inc
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 Valeo Thermique Moteur SA, Valeo Engine Cooling Inc filed Critical Valeo Thermique Moteur SA
Publication of EP0447528A1 publication Critical patent/EP0447528A1/de
Application granted granted Critical
Publication of EP0447528B1 publication Critical patent/EP0447528B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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
    • F28D1/0316—Assemblies of conduits in parallel
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
    • Y10S165/464—Conduits formed by joined pairs of matched plates
    • Y10S165/467—Conduits formed by joined pairs of matched plates with turbulence enhancing pattern embossed on joined plates
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49359—Cooling apparatus making, e.g., air conditioner, refrigerator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49396—Condenser, evaporator or vaporizer making

Definitions

  • the invention relates to a condenser for a motor vehicle and a method for producing it, this condenser having a particular application in uses where resistance to high internal pressures of a fluid is necessary.
  • the heat exchangers still used such as condensers for motor vehicle air conditioning systems usually comprise a tube configured in the form of a continuous coil inside which fluids can flow in gaseous and / or liquid forms.
  • a cooling means such as ambient air, passes over the tubes and fins allowing the heat exchange of the very hot fluid in the tube towards the cooling means.
  • the continuous tubes are made from U-shaped elements to allow insertion through the fins and, after assembly, the elements are connected to each other by U-shaped brackets of way to constitute a continuous serpentine tube.
  • the condensers comprise manifold boxes spaced apart and parallel to each other, said boxes being connected to each other by a multiplicity of parallel heat exchange tubes so as to allow the circulation of the fluid, such as a fluid in gaseous and / or liquid form between the manifolds.
  • the multiplicity of tubes are circular or rectangular in configuration and have fins of flat or corrugated shapes arranged through or between the tubes so as to increase the heat exchange efficiency of the heat exchange tubes.
  • the device is formed, in a known manner, by inserting the multiplicity of tubes into holes provided on the manifolds, by placing corrugated fins between the tubes and by welding or brazing the tubes to the manifolds and the fins to the tubes.
  • the refrigerant gas flows through the heat exchange tubes and is cooled or substantially condensed into a liquid by the flow of cooling air sweeping the tubes.
  • the direction of the refrigerant current and the flow of cooling air are generally perpendicular to each other.
  • the longitudinal dimension of one of the edges of the tube perpendicular to the air flow is the leading edge in contact with the air flow and the width of this leading edge is generally considered to be the transverse dimension of the tube. heat exchanger.
  • the transverse dimension of a tube is thus the average width of the tube.
  • a round tube has a transverse dimension equal to its diameter and a rectangular tube has a transverse dimension equal to the width of its leading edge.
  • the width of the leading edge represents an obstruction to the air flows and it is generally desired to minimize this obstruction.
  • the smallest round tubes used commercially have a diameter greater than 5.08mm (0.2 inches) creating a barrier causing the formation of a transverse dimension of less than 5.08mm (0.2 inches).
  • substantially rectangular heat exchange tubes In order to reduce the width of the leading edge, for example by reducing the transverse dimension, substantially rectangular heat exchange tubes have been proposed and have found a degree of acceptance in the industry thanks to the different rectangular configurations. variables.
  • US-A-4 615 385 although particularly relating to a manifold construction, describes a heat exchange tube of rectangular shape with a plurality of tubes connected in parallel between the manifolds.
  • the tube is described as being flat such that the smallest dimension of the rectangle includes a circular surface which is arranged in the device including the transverse dimension.
  • US-A-4,688,311 describes a method for manufacturing a heat exchange tube of rectangular shape which can be effective in resisting the high internal pressures of the fluid of an automobile air conditioning system.
  • a rectangular tube comprising the circular configuration of the transverse dimension of US-A-4 615 385 is connected internally with an insert in the form of a corrugated fin which is fixed with the inside of the tube along of its longitudinal dimension.
  • the internal fins serve as tension spacers to aid resistance to internal fluid pressures.
  • One of the objects of the invention is to provide heat exchange structures having effective resistances to air flows in their transverse dimensions.
  • Another object of the invention is to provide heat exchange structures having resistances to the internal pressures of the fluids.
  • Another object of the invention is to provide an automotive condenser having resistance to the internal pressures of the fluids.
  • the invention relates to a condenser for an automobile comprising elongated generally rectangular hollow heat exchange structures extending between manifolds, said hollow structures comprising first and second opposite elongated plates joined together along their elongated longitudinal edges to define a passage.
  • said opposite plates undulating in a transverse structure to define generally parallel recesses and bumps inclined obliquely to the longitudinal direction, the recesses of the first opposite plate being angularly arranged to cross the opposite recesses of said second plate being joined to all crossing points, characterized in that the maximum distance between the crossing points of the recesses does not exceed 5.08 mm (0.2 inches) and in that said bumps and recesses are arranged away from the longitudi edge nal contiguous said elongated plates and in that the outer longitudinal edge of the first plate covers the inner longitudinal edge of the second plate to form a passage extending longitudinally comprising a generally circular surface.
  • angles formed by the crossing of the hollows of the opposite plates are of the order of 20 to 170 °.
  • the longitudinally extending contiguous edges of the elongated plates have a transverse dimension of less than 3.15 mm (0.125 inches).
  • the elongated plates have a material thickness in the range of 0.30 to 0.76 mm (0.012 to 0.030 inches).
  • the bumps between the opposing hollows have a generally rectangular cross section.
  • the recesses are joined by brazing or welding means.
  • the condenser includes energy dissipating fins extending from the hollow structures elongated.
  • Figure 1 is a perspective view of the automobile condenser obtained according to the present invention.
  • Figure 2 is an enlarged partial sectional view taken approximately on line 2-2 of Figure 1.
  • Figure 3 is a plan view of the heat exchange structure obtained according to the present invention.
  • Figure 4 is an enlarged sectional view along line 4-4 of Figure 3.
  • FIG. 5 is a view similar to FIG. 4 but showing the parts in assembly condition, this view being taken on line 5-5 of FIG. 3.
  • FIG. 1 An embodiment of an automobile condenser according to the invention is illustrated in FIG. 1.
  • the present invention can be used in a plurality of other condensers in which a heat exchange structure is provided between the manifolds.
  • FIG. 1 where a condenser for an automobile is illustrated and comprises an intake manifold 11 and, disposed generally parallel thereto, being opposite, an exhaust manifold 12.
  • the intake manifold 11 includes an intake 13 and the exhaust manifold 12 includes an outlet 14.
  • a plurality of hollow heat exchange structures 15 extend between the opposite manifolds and, disposed between the structures, are inserted corrugated fins 16 in heat exchange relationship with the hollow heat exchange structures.
  • the plurality of heat exchange structures 15 are connected to the intake manifold 11 and to the exhaust manifold 12 by solder joints 17 as best shown in FIG. 2.
  • the corrugated fins 16 are inserted between the plurality of heat exchange structures and are in intimate contact therewith.
  • a first hot fluid and in gaseous form such as a refrigerant enters the intake manifold 11 through the intake 13 flows along the longitudinally extending passages of the plurality hollow heat exchange structures and inside the evacuation manifold 12.
  • the stream of gaseous fluid, along the exchange structures, is directed by the hollows and bumps, arranged angularly, opposite elongated plates, in a discontinuous and undulating circuit in which the flow of fluid is passively separated and mixed by the circuits intersecting recesses by increasing the contact of the fluid flow with the elongated plates.
  • the heat of the fluid is dissipated towards the opposite plates of the heat exchange structures and towards the corrugated fins in contact with them.
  • a second flow of fluid such as ambient air, flows through the condenser in such a way that the second fluid flows along the cross section of the heat exchange structures and along the corrugated fins.
  • Heat is dissipated from such structures and fins towards the second fluid sweeping them, when the heat of the second fluid is less important than the heat of the heat exchange structure and / or of the corrugated fins.
  • the first gaseous fluid condenses into a liquid which flows along the remaining length of the heat exchange structures to the outlet manifold 12 and via outlet 14 for processing in other parts of the system.
  • FIG. 2 illustrates a sectional view of the condenser of Figure 1, in which the inlet and outlet manifolds 11 and 12 are provided with a plurality of elongated holes 18 substantially parallel and separate , configured to receive the open ends of the plurality of elongated hollow heat exchange structures and allow circulation of gaseous and / or liquid material therebetween.
  • the exchange structures are sealed with the manifolds by suitable connecting means which provide sufficient structural integrity so as to withstand the pressures generated inside the system when the condenser is used.
  • solder joint 17 is illustrated as a preferred embodiment when the construction materials are aluminum.
  • the heat sink fins can be connected to the heat exchange structures, preferably, with a conductive material thermal, or can be linked to structures depending on the expected services of the system.
  • planar fins can generally be provided with elongated holes generally shaped in relation to the cross section of the heat exchange structures and can be inserted around these structures.
  • the corrugated dissipative fins or the flat fins comprise at least the same width as the heat exchange structures, said fins being in contact with the exchange structures as much as possible along the width of said exchange structures. thermal.
  • the heat sink fins are thin and made from high level thermal conductive material.
  • the fins 16 of the condenser 10 comprise a thin conductive material of approximately the same width as the heat exchange structures 15 and are intimately linked between the plurality of exchange structures to maintain their structural integrity in the condenser.
  • Figures 3, 4 and 5 illustrate a preferred embodiment of the heat exchange structures according to the invention in which the bumps generally form rectangular passages in the central section of the body of the structure and passages having a generally circular surface are formed with contiguous longitudinal edges.
  • a heat exchange structure 15 comprises an elongated corrugated upper plate 19 and an elongated corrugated lower plate 20 contiguous to the intersecting recesses 21 to form generally rectangular passages 22.
  • the undulations in the plate 19 are oblique with respect to the undulations of the plate 20.
  • passages 26 By joining the opposing plates by covering its outer longitudinal edge 24 with the inner longitudinal edge 25, there are formed passages 26 having a substantially circular surface.
  • the edges 24 and 25 can be carried together and be united in a common plane parallel to the main plane of the plates and can even comprise an elongated flat surface.
  • the longitudinal edges are brazed at the interface 28 and the intersecting recesses 21 are brazed at the intersecting point 29 to ensure the structural integrity of the hollow passages of the heat exchange structures.
  • the hollows and bumps of the elongated plates can be suitably formed by stamping, embossing or the like by forming the hollows of desired shape in the elongated plates.
  • the surface between the recesses includes adjacent bumps.
  • bumps can be stamped or otherwise formed in the plates in order to be erected above. above the plate plane.
  • the bumps and the hollows will present an oblique angle to the longitudinal direction of the elongated plate.
  • the oblique angle will be of the order of 10 to 85 ° considering the longitudinal direction of the plate and preferably of the order of 20 to 70 °.
  • the first and second opposite elongated plates having angularly arranged recesses, are assembled in such a way that the recesses of the first plate cross the opposite recesses of the second plate.
  • the hollows or bumps of the first plate it is not essential for the hollows or bumps of the first plate to be in the same oblique angle in the longitudinal direction as those of the second plate, although this is generally preferred.
  • angles of the intersection of the hollows which is an angle formed by the hollows crossing and opening in the longitudinal direction of the assembled plates, can generally be of the order of 20 to 170 °.
  • FIG. 3 illustrates elongate contiguous plates in which the intersecting hollows form an angle A of the order of 90 °.
  • An angle will approach 0 ° when the oblique angle of the hollows of the opposite elongated plates will approach the longitudinal direction and will approach 180 ° when the oblique angles will approach a perpendicular to the longitudinal direction.
  • the recesses in the opposite plates are preferably formed with a small radius of apex inside their apices.
  • the inner apex radius is preferably no greater than 1.5 times the thickness of the material from which the plate is made and most preferably less than the thickness of the material.
  • the width of a hump includes the dimension of the plate between the vertices of adjacent hollows and of such dimension is variable depending on the internal pressure considered inside the exchange structure and the extent of the junction of the hollow intersecting opposite plates.
  • the width of the bumps on a plate with a The defined number of contiguous intersecting depressions in a high internal pressure system will typically be smaller than that in a low internal pressure system.
  • the width of the bumps is preferably greater than two and a half times the thickness of the material from which the plate is produced and less than seven times this thickness.
  • the thickness of the material of the opposite plates is from 0.30 mm to 0.76 mm (0.012 to 0.030 inches) and preferably from 0.30 to 0, 71 mm (0.012 to 0.028 inches).
  • the internal radius of the recesses is preferably of the order of 1.5 times the thickness of the material of the thickness of the plate or less and the width of the bumps is preferably of 2.5 to 7 times the thickness of the material of the plaque.
  • the heat exchange structures having the configuration of the invention and dimensioned according to the preferred data can thus preferably be produced having a transverse dimension of the order of 3.17 mm (0.125 inches) or less.
  • the condensers of the invention may be constructed from a suitable material which will withstand the effects of corrosion and internal pressures of system fluid.
  • Typical materials include malleable materials such as aluminum and copper and in particular alloys.
  • the materials can be internally or externally plated, treated or other.
  • each of the components of a condenser is formed from the same material when joined together.
  • the plates used to make the heat exchange structures will be formed from the same material.
  • manifolds and heat exchange structures will also be formed from the same metal or a metal alloy when brazed or welded together.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (7)

  1. Fahrzeugkondensator, enthaltend hohle, längliche, allgemein rechteckige Wärmeaustauschkonstruktionen (15), die sich zwischen Sammelkästen (11, 12) erstrecken, wobei die genannten Hohlkonstruktionen einander gegenüberliegende, längliche erste und zweite Platten (19, 20) enthalten, die entlang ihrer länglichen Längskanten zusammengefügt sind, um so einen Durchtritt zu begrenzen, der sich in einer Längsrichtung erstreckt, wobei die genannten, einander gegenüberliegenden Platten wellenförmig in einer Querkonstruktion verlaufen, um Hohlräume (21) und allgemein parallel verlaufende Vorsprünge zu begrenzen, die im Verhältnis zur Längsrichtung schräg liegen, während die Hohlräume (21) der ersten gegenüberliegenden Platte im Winkel angeordnet sind, um so die gegenüberliegenden Hohlräume (21) der genannten zweiten Platte zu kreuzen, und dabei an allen Kreuzungspunkten aneinanderstoßen, dadurch gekennzeichnet, daß der größte Abstand zwischen den Kreuzungspunkten der Hohlräume (21) 5,08 mm (0,2 Zoll) nicht überschreitet und daß die genannten Vorsprünge und Hohlräume in einem Abstand zur angrenzenden Längskante der genannten länglichen Platten angeordnet sind und daß die äußere Längskante der ersten Platte die innere Längskante der zweiten Platte bedeckt, so daß ein Durchtritt (26) entsteht, der in Längsrichtung verläuft und eine allgemein kreisförmige Oberfläche aufweist.
  2. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß die von der Kreuzung der Hohlräume der gegenüberliegenden Platten gebildeten Winkel in der Größenordnung von 20 bis 170° liegen.
  3. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß die sich in Längsrichtung erstreckenden, aneinanderstoßenden Kanten der länglichen Platten eine Querabmessung von weniger als 3,17 mm (0,125 Zoll) aufweisen.
  4. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß die genannten länglichen Platten (19, 20) eine Materialdicke in der Größenordnung von 0,30 bis 0,76 mm (0,012 bis 0,030 Zoll) haben.
  5. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß die Vorsprünge zwischen den gegenüberliegenden Hohlräumen (21) einen allgemein rechteckigen Querschnitt haben.
  6. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß die genannten Hohlräume durch Hartlötung oder Schweißmittel verbunden sind.
  7. Kondensator nach Anspruch 1, dadurch gekennzeichnet, daß er Energieableitungsrippen (16) enthält, die von den länglichen Hohlkonstruktionen ausgehen.
EP90914931A 1989-10-04 1990-10-03 Fahrzeugkondensator Expired - Lifetime EP0447528B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US417049 1982-09-13
US07/417,049 US4932469A (en) 1989-10-04 1989-10-04 Automotive condenser

Publications (2)

Publication Number Publication Date
EP0447528A1 EP0447528A1 (de) 1991-09-25
EP0447528B1 true EP0447528B1 (de) 1993-11-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90914931A Expired - Lifetime EP0447528B1 (de) 1989-10-04 1990-10-03 Fahrzeugkondensator

Country Status (7)

Country Link
US (1) US4932469A (de)
EP (1) EP0447528B1 (de)
JP (1) JPH04505362A (de)
BR (1) BR9006944A (de)
CA (1) CA2037901A1 (de)
DE (1) DE69004793T2 (de)
WO (1) WO1991005211A1 (de)

Families Citing this family (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5279360A (en) * 1985-10-02 1994-01-18 Modine Manufacturing Co. Evaporator or evaporator/condenser
DE69023925T2 (de) * 1989-02-06 1996-05-23 Furukawa Electric Co Ltd Herstellungsverfahren einer halbleiter-kühlanordnung vom wärmerohr-typ.
US5271151A (en) * 1990-04-23 1993-12-21 Wallis Bernard J Method of making a high pressure condenser
US5129144A (en) * 1990-06-19 1992-07-14 General Motors Corporation Method of making a combination radiator and condenser apparatus for motor vehicle
JPH04177094A (ja) * 1990-11-13 1992-06-24 Sanden Corp 積層型熱交換器
US5125453A (en) * 1991-12-23 1992-06-30 Ford Motor Company Heat exchanger structure
US5185925A (en) * 1992-01-29 1993-02-16 General Motors Corporation Method of manufacturing a tube for a heat exchanger
KR950009505B1 (ko) * 1993-03-05 1995-08-23 주식회사두원공조 자동차의 에어콘용 열교환기의 제조방법
JP3364665B2 (ja) * 1993-03-26 2003-01-08 昭和電工株式会社 熱交換器用冷媒流通管
US5931226A (en) * 1993-03-26 1999-08-03 Showa Aluminum Corporation Refrigerant tubes for heat exchangers
US5784776A (en) * 1993-06-16 1998-07-28 Showa Aluminum Corporation Process for producing flat heat exchange tubes
US5441105A (en) * 1993-11-18 1995-08-15 Wynn's Climate Systems, Inc. Folded parallel flow condenser tube
JPH07180984A (ja) * 1993-12-21 1995-07-18 Sanden Corp 熱交換器及びその製造方法
CA2150437C (en) * 1995-05-29 1999-06-08 Alex S. Cheong Plate heat exchanger with improved undulating passageway
US5826646A (en) * 1995-10-26 1998-10-27 Heatcraft Inc. Flat-tubed heat exchanger
US5775412A (en) * 1996-01-11 1998-07-07 Gidding Engineering, Inc. High pressure dense heat transfer area heat exchanger
US5771964A (en) * 1996-04-19 1998-06-30 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
US6016864A (en) * 1996-04-19 2000-01-25 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
EP1223391B8 (de) * 1996-12-25 2005-12-21 Calsonic Kansei Corporation Kondensatoraufbaustruktur
AT407920B (de) * 1997-03-25 2001-07-25 Ktm Kuehler Gmbh Plattenwärmetauscher, insbesondere ölkühler
JP4122578B2 (ja) 1997-07-17 2008-07-23 株式会社デンソー 熱交換器
CA2215173C (en) * 1997-09-11 2004-04-06 Thomas F. Seiler Stepped dimpled mounting brackets for heat exchangers
US6155135A (en) * 1998-11-23 2000-12-05 American Axle & Manufacturing, Inc. Drive unit with lubricant cooling cover
US6401804B1 (en) * 1999-01-14 2002-06-11 Denso Corporation Heat exchanger only using plural plates
US6155339A (en) * 1999-06-18 2000-12-05 Grapengater; Richard B. Obround header for a heat exchanger
US6209202B1 (en) 1999-08-02 2001-04-03 Visteon Global Technologies, Inc. Folded tube for a heat exchanger and method of making same
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
US7011142B2 (en) * 2000-12-21 2006-03-14 Dana Canada Corporation Finned plate heat exchanger
US6523260B2 (en) 2001-07-05 2003-02-25 Harsco Technologies Corporation Method of making a seamless unitary body quadrilateral header for heat exchanger
JP5250924B2 (ja) * 2001-07-16 2013-07-31 株式会社デンソー 排気熱交換器
US6595273B2 (en) 2001-08-08 2003-07-22 Denso Corporation Heat exchanger
US6830100B2 (en) * 2001-11-02 2004-12-14 Thermalex, Inc. Extruded manifold
CA2372399C (en) * 2002-02-19 2010-10-26 Long Manufacturing Ltd. Low profile finned heat exchanger
US8087452B2 (en) * 2002-04-11 2012-01-03 Lytron, Inc. Contact cooling device
JP3812487B2 (ja) * 2002-04-16 2006-08-23 株式会社デンソー 熱交換器
CA2389119A1 (en) * 2002-06-04 2003-12-04 Christopher R. Shore Lateral plate finned heat exchanger
CA2423193A1 (en) * 2003-03-24 2004-09-24 Dana Canada Corporation Lateral plate surface cooled heat exchanger
US7311139B2 (en) * 2005-08-11 2007-12-25 Generac Power Systems, Inc. Heat exchanger
JP2007278558A (ja) * 2006-04-04 2007-10-25 Denso Corp 冷媒放熱器
JP5082120B2 (ja) * 2007-03-23 2012-11-28 国立大学法人 東京大学 熱交換器
DE102008064090A1 (de) * 2008-12-19 2010-08-12 Mahle International Gmbh Abgaskühler
SE534695C2 (sv) * 2009-12-23 2011-11-22 Fueltech Sweden Ab Ackumulatortank
KR20130065174A (ko) * 2011-12-09 2013-06-19 현대자동차주식회사 차량용 열교환기
US20150285569A1 (en) * 2014-04-04 2015-10-08 Delphi Technologies, Inc. Heat exchanger with dimpled manifold
US11333448B2 (en) * 2018-09-18 2022-05-17 Doosan Heavy Industries & Construction Co., Ltd. Printed circuit heat exchanger and heat exchange device including the same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4470455A (en) * 1978-06-19 1984-09-11 General Motors Corporation Plate type heat exchanger tube pass
US4615385B1 (en) * 1985-04-12 1994-12-20 Modine Mfg Co Heat exchanger
JPS625096A (ja) * 1985-06-28 1987-01-12 Nippon Denso Co Ltd 積層型熱交換器
US4805693A (en) * 1986-11-20 1989-02-21 Modine Manufacturing Multiple piece tube assembly for use in heat exchangers

Also Published As

Publication number Publication date
WO1991005211A1 (fr) 1991-04-18
DE69004793D1 (de) 1994-01-05
CA2037901A1 (fr) 1991-04-05
DE69004793T2 (de) 1994-03-17
BR9006944A (pt) 1991-10-08
US4932469A (en) 1990-06-12
EP0447528A1 (de) 1991-09-25
JPH04505362A (ja) 1992-09-17

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