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WO2004023056A1 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

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Publication number
WO2004023056A1
WO2004023056A1 PCT/EP2003/008778 EP0308778W WO2004023056A1 WO 2004023056 A1 WO2004023056 A1 WO 2004023056A1 EP 0308778 W EP0308778 W EP 0308778W WO 2004023056 A1 WO2004023056 A1 WO 2004023056A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
manifold
flat tubes
exchanger according
flat
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.)
Ceased
Application number
PCT/EP2003/008778
Other languages
German (de)
English (en)
Inventor
Peter Geskes
Christoph Walter
Karl-Heinz Staffa
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and 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 and Co KG filed Critical Behr GmbH and Co KG
Priority to AU2003266971A priority Critical patent/AU2003266971A1/en
Priority to EP03747885A priority patent/EP1530703B1/fr
Priority to DE50308809T priority patent/DE50308809D1/de
Priority to US10/524,408 priority patent/US20050236149A1/en
Publication of WO2004023056A1 publication Critical patent/WO2004023056A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements

Definitions

  • the invention relates to a heat exchanger with a number of parallel and spaced flat tubes, in particular for an air conditioning system of a vehicle.
  • Heat exchangers are usually used in vehicles today, which heat from a fluid flowing through this primary side, e.g. Release carbon dioxide, water or refrigerant into air flowing through the heat exchanger on the secondary side. Conversely, the fluid flowing through the heat exchanger can absorb heat from the air.
  • the heat exchanger has, in particular, parallel flat tubes spaced apart from one another. For a sufficiently firm and above all stable mechanical arrangement of the heat exchanger, ribs or reinforcing webs are arranged between the flat tubes.
  • header boxes or header distributors To feed the flat tubes together with the fluid, they are connected at the end to so-called header boxes or header distributors.
  • the fluid designed as a coolant or refrigerant flows through channels running in the flat tubes and is then collected in the collecting boxes or tubes and, if necessary, deflected into adjacent flat tubes of the heat exchanger.
  • the collecting boxes usually have partitions.
  • Such a heat exchanger with flat tubes penetrated by so-called capillaries or small channels and which are fed via the collecting tank is known for example from EP 0 654 645 B1.
  • the flat tubes have the advantage that very small channels, also called cooling or fluid channels, can be provided, which are particularly pressure-stable.
  • the collection box or distribution manifold which performs a fluid collection and / or fluid distribution function, has to be of particularly large volume.
  • the heat exchanger must withstand a particularly high internal pressure, but a so-called burst pressure is clearly above a maximum permissible operating pressure. Therefore, when designing and designing the heat exchanger with regard to its maximum permissible compressive strength, care is taken to ensure that, in particular, the header box or the header pipe has a sufficiently thick wall.
  • the heat exchanger is used for an air conditioning circuit with carbon dioxide or the so-called R 134 A fluid as the cooling medium
  • the heat exchanger and its header tank have very thick-walled header pipes or header manifolds with partially pronounced beads due to the high pressures that are usual here.
  • the disadvantage here is that this results in the area of
  • Collection box due to the large thick walls, a high amount of material is given, which is particularly time consuming when soldering the flat tubes to the collection box.
  • a heat exchanger designed in this way is particularly cost-intensive and in terms of. the freedom of design, especially for the underlying collection box.
  • a heat exchanger designed in this way has a particularly high weight.
  • the invention is therefore based on the object of specifying a heat exchanger, in particular for an air conditioning system of a vehicle, which is of particularly simple design and has a low weight.
  • the object is achieved according to the invention in a heat exchanger with a number of flat tubes which are arranged parallel to one another and spaced apart from one another and which have at least one end via a collecting tube.
  • mel distributor can be supplied with a fluid, the flat tubes in the manifold being arranged at least partially in a form-fitting manner.
  • the invention is based on the consideration that a particularly thick-walled design of a header tank or header manifold for flat tubes of a heat exchanger through which a fluid, in particular cooling medium can flow, should be dimensioned in such a way that they are particularly simple and light in design.
  • the flat tubes ending in the manifold and held there should at the same time enable the manifold to be stiffened, so that the latter is additionally designed to be pressure-resistant or pressure-stable via the design or shape of the ends of the flat tubes.
  • the flat tubes in the manifold are preferably arranged at least partially positively.
  • the flat tubes are largely completely guided in the manifold, so that in addition to a form fit, they can also absorb a force fit, in particular a tensile and / or compressive force.
  • an outer contour representing the end of the respective flat tube is at least partially adapted to an inner contour representing the manifold.
  • an outer contour representing the end of the respective flat tube is preferably at least partially adapted to an outer contour representing the manifold.
  • the outer contour of the flat tube adapted to the inner contour of the manifold when at least one end of one of the flat tubes is adapted to the outer contour of the manifold, the respective flat tube can be inserted into the heat exchanger from the outside and thus be mounted.
  • the manifold with at least one recess is expedient provided for the passage of one of the flat tubes.
  • the recess is designed to receive the flat tube in particular as a slot-like recess.
  • the end of the flat tube in question is expediently held in a cohesive manner at the recess of the manifold.
  • the end of the flat tube is compressed or crimped and soldered together in the recess of the manifold.
  • soldering from the outside of the flat tubes to the manifold ensures that the heat exchanger is sufficiently well sealed with respect to the fluid flowing through it, so that humidification of the air flowing through the heat exchanger on the secondary side is reliably avoided.
  • one end of at least one of the flat tubes is provided with webs on the outside.
  • the flat tube can serve at the end as a completely circumferential reinforcement and support of the manifold or manifold.
  • the end of the flat tube in question is provided with an opening or recess.
  • the opening or the webs are formed by punching, punching or water jet methods.
  • the perforated opening or the opening formed by the webs serves for supplying the fluid, in particular for the passage of coolant or refrigerant into the capillaries or channels of the flat tube exposed through the opening.
  • the bores or capillaries running in the respective flat tube are fed via the fluid guided in the opening of the flat tube end.
  • the end of at least one of the flat tubes is centered with another, provided arranged web.
  • a two-part manifold can be formed in a particularly simple manner by an end of the flat tube that has two outer and a central web when it is fully inserted and thus fully form-fit with the manifold, one by the split formed chamber can be used to supply the fluid and the other chamber can be used to discharge the fluid.
  • the chambers of a collecting distributor divided in this way are fed in the same way, a plurality of flat tubes combined into a group can be fed separately from one another, as a result of which different types of flow through the heat exchanger are made possible.
  • the end of the respective flat tube is preferably at least partially guided in a recess running in the inner contour.
  • the inside of the manifold has a channel-shaped bead or a groove in which the end of the respective flat tube is guided and inserted.
  • the end of the respective flat tube is expediently held integrally on the manifold.
  • the end of the respective flat tube is held on the manifold with or without filler material.
  • the end of the flat tube is soldered along the recess of the manifold.
  • the end of the respective flat tube can be glued or welded.
  • the manifold is expediently divided into at least two areas along and / or across.
  • the collecting box or collecting distributor is preferably divided two or more times.
  • a partition is arranged in the manifold for this purpose.
  • the end of at least one of the flat tubes is expediently provided with a slot for receiving the partition.
  • the partition wall expediently has a passage opening.
  • the ends of the flat tubes are designed differently.
  • a number of flat tubes, which are arranged adjacent to one another are provided at least at one end with the annular and / or U-shaped passage opening for the fluid, a next flat tube being designed at the end as a solid profile and thus not punched through, so that this acts as a partition. This eliminates the need for additional partition walls. This enables the heat exchanger to be made even lighter than in the prior art.
  • the flat tubes can end at the end in an associated manifold.
  • the flat tubes can be fed on one side and / or on both sides, that is to say when the flat tubes are fed on one side, for example a two-part manifold with a chamber for supplying and a further chamber for discharging the fluid is arranged on one end of the flat tubes.
  • a single manifold is provided on the end for feeding and on the other for discharging the fluid.
  • one of the manifolds can serve as a feed and discharge and the opposite manifold can serve as a deflection channel for deflecting the fluid between two adjacent flat tubes.
  • the manifolds arranged at the end of the flat tubes are preferred uniformly trained. This ensures a sufficiently good and uniform flow of fluid through the flat tubes.
  • the advantages achieved by the invention are, in particular, that the form of a flat arrangement of the flat tubes in the manifold or manifold, in particular by a complete positive connection in the circumferential direction of the manifold, is designed with significantly smaller wall thicknesses.
  • Such a form-fitting arrangement of the flat tubes in the manifold dissipates tensile and / or compressive forces acting on the heat exchanger in the manner of a tension or composite anchor in the flat tubes.
  • flat tubes inserted into the manifold at a stop or flush are particularly simple to install and easy to handle.
  • FIGS. 1A-1C schematically show a heat exchanger with a plurality of flat tubes arranged in a form-fitting manner in a manifold
  • FIGS. 3A-3C schematically show a heat exchanger with flat tubes provided at the ends with webs
  • FIG. 4 schematically shows a heat exchanger according to FIGS. 3A-3C in a perspective view
  • FIGS. 5A-5B and 6A-6B schematically show different heat exchangers with manifolds having different cross-sectional shapes
  • FIGS. 7A-7B schematically show a heat exchanger with flat tubes inserted from the outside
  • FIGS. 8A-8B schematically show a heat exchanger with two openings with flat tubes
  • FIG. 9 schematically shows a heat exchanger with a dividing wall in the manifold intended for different flows
  • Figure 10 schematically shows a heat exchanger with two manifolds arranged at the ends of the flat tubes.
  • FIGS. 1A to 1C show a heat exchanger arrangement 1 with a number of flat tubes 2 arranged parallel to one another and spaced apart from one another.
  • the flat tubes 2 are provided with fluid channels 4 for the flow through them with a fluid F, for. B. a coolant or refrigerant flow for an air conditioning system of a vehicle.
  • the fluid channels 4 have a particularly small diameter and are designed in the manner of capillaries.
  • the flat tubes 2 in the manifold 6 are at least partially positively arranged.
  • the end 8 of the respective flat tube 2 and an outer contour 10 representing this end 8 are adapted to an inner contour 12 representing the manifold 6.
  • the end 8 of at least one of the flat tubes 2 is provided with an opening 13 (FIG. 1B).
  • Such a frame-like, e.g. ring-shaped design of the flat tube end 8 enables the outer contour 10 with the inner contour 12 of the manifold 6 to be sufficiently positively protected against mechanical stresses by a stiffening and support that largely completely surrounds the manifold 6. This leads to a particularly thin-walled design of the manifold 6.
  • the opening 13 introduced at the end 8 of the flat tube 2 in question serves itself as a flow channel of the manifold 6 for supplying and / or discharging the fluid F.
  • the opening 13 can be made by punching, punching, drilling or any other suitable type.
  • the opening 13 in the case of flat tubes 2 which have already been joined together and form a component of the heat exchanger 1 and which are of identical design with regard to the opening 13, the opening 13 can be introduced in a single method step by punching out or punching.
  • the flat tubes 2 of a single heat exchanger 1 which can be flowed through in different ways and which are designed differently at the ends, i.e. with and / or without opening 13, the flat tubes 2 can be produced separately or in groups.
  • Figure 2 shows an alternative heat exchanger 1 with a flat tube 2, the end 8 is adapted with its outer contour 10 to the inner contour 12 of the manifold 6.
  • the end 8 of the respective flat tube 2 is at least partially guided in a recess 14 of the manifold 6 running in the inner contour 12.
  • this can be designed as a channel-shaped bead or groove.
  • the recess 14 can run partially or completely along the inner contour 12 of the manifold 6. That is, the recess 14 can run around the entire inner contour 12 of the manifold 6, the recess 14 being designed as an opening only in the region of the feed of the flat tube 2.
  • the recess 14 is designed as a bead or groove.
  • the end 8 of the respective flat tube 2 is for assembly in the
  • Heat exchanger 1 inserted through the recess 14 and held positively in the manifold 6.
  • the end 8 of the respective flat tube 2 is held integrally on the manifold 6.
  • the end 8 of the respective flat tube 2 is preferably soldered along the recess 14 of the manifold 6.
  • the end 8 can be glued or welded.
  • the collection manifold 6 here in two regions 16 is divided, which transversely ng to Luftströmungsrichtu 'extend L.
  • Such a two-part manifold 6, also called a two-part collecting box enables differentiated and separate feeding of the individual flat tubes 2.
  • a rib 18 is arranged between the spaced apart flat tubes 2.
  • FIGS 3A to 3C show an alternative embodiment for the
  • Heat exchanger 1 The end 8 of the respective flat tube 2 is provided with outside webs 20, which are sufficient for good strength and rigidity in a heat exchanger 1 designed for a low pressure. Depending on the type and design of the webs 20, the opening 13 of the end 8 of the flat tube 2 in question, which represents this, can also be produced by punching or punching.
  • the flat tube 2 is positively connected to the manifold 6 in the area of the webs 20.
  • FIG. 4 shows a perspective view of the heat exchanger 1 according to FIGS. 3A to 3C, this heat exchanger 1 having only a simple manifold 6.
  • FIGS. 5A to 5B and 6A to 6B show different cross-sectional shapes for the manifold 6 and, as a result, for the opening 13 provided in the end 8 of the respective flat tube 2.
  • the manifold 6 has z. B. a round cross-sectional shape.
  • the cross-section of the manifold 6 is designed as a rectangle or square.
  • FIGS. 7A and 7B show an alternative embodiment for the heat exchanger 1.
  • the end 8 of the respective flat tube 2, in particular its outer contour 10, is at least partially adapted to an outer contour 22 representing the manifold 6.
  • the flat tube 2 is inserted into this from an externally accessible recess 24 of the collecting distributor 6 and / or via the opening 14 of the collecting distributor 6 opening in the direction of the flat tubes 2, the end of the flat tube 2 during assembly in the heat exchanger 1 being 8 the surface of the manifold 6 protrudes.
  • the end 8 of the flat tube 2 projecting beyond the manifold 6 is then compressed and / or soldered to the outer contour 22 of the manifold 6.
  • Figures 8A and 8B show an alternative embodiment for the heat exchanger 1.
  • the manifold 6 is formed in one piece.
  • the end 8 of the respective flat tube 2 is provided with a divided opening 13 for a differentiated flow through the fluid channels 4.
  • This divided opening 13 is brought about in one production step, for example by punching holes in the end 8 of the respective flat tube 2.
  • FIG. 9 shows a possible embodiment for a heat exchanger 1 with a rectangular manifold 6, in which a plurality of flat tubes 2 having uniform ends 8 are held in a form-fitting and / or integral manner.
  • the manifold 6 is divided longitudinally and transversely into areas 16a to 16d by means of a partition wall 26.
  • the manifold 6 is designed as a four-part manifold 6 due to the subdivision into the areas 16a to 16d, so that a heat exchanger 1 resulting therefrom has only one manifold 6 arranged at one end 8 of the flat tubes 2 for supplying and discharging the fluid F.
  • the manifold 6 comprises an inlet channel 28 and an outlet channel 30 for supplying and discharging the fluid F into regions 16a to 16d which are separated from one another by the partition wall 26 and in which the openings 13 of the relevant flat tubes 2 arranged therein serve as flow channels 36. Due to the introduction of the partition wall 26 and the resulting subdivision into regions 16a, 16c and 16b, 16d running in the longitudinal direction, the channels 4 arranged within a single flat tube 2 are likewise flowed through in countercurrent by the fluid F. Due to the subdivision of the manifold 6 into the areas 16a, 16b and 16c, 16d, adjacent flat tubes 2 are flowed through in the counterflow principle. For a like-minded flow through the channels 4 of an individual flat tube 2, the partition wall 26 comprises at least one passage opening 32.
  • the respective flat tube 2 is provided with a slot 34.
  • the slot 34 serves both to guide the partition 26 and to secure it, e.g. by
  • the flat tubes 2 can be flowed through differently, for example in cross-countercurrent, in cross-countercurrent, in countercurrent and / or in cocurrent.
  • Figure 10 shows a further alternative embodiment for a heat exchanger 1, the flat tubes 2 are flowed through in different directions.
  • the dividing wall 26 according to FIG. 9 can be omitted in that the flat tubes 2 themselves serve as dividing walls due to a correspondingly different design of the relevant ends 8.
  • several flat tubes 2a are provided at the ends with openings 13 for the fluid F to flow through.
  • a flat tube 2b serving as a partition has a closed end 8.
  • the ends of the flat tubes 2 each end 8 in one
  • the upper manifold 6a serves both the supply and the discharge of the fluid F via a single flow channel 36, which is designed as an inlet channel 28 and an outlet channel 30 and is formed through the openings 13 of the respective flat tubes 2, the fluid F being U-shaped in the longitudinal direction Flows through heat exchanger 1.

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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)
  • Separation By Low-Temperature Treatments (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention vise à mettre en oeuvre un échangeur thermique de construction simple et de poids réduit, comportant une pluralité de tubes plats parallèles et espacés. A cet effet, les tubes plats (2) peuvent recevoir un fluide (F) au niveau d'au moins une extrémité (8), alimenté par un collecteur (6), lesdits tubes plats (2) étant logés en engagement au moins partiellement positif dans le collecteur (6).
PCT/EP2003/008778 2002-08-13 2003-08-07 Echangeur thermique Ceased WO2004023056A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU2003266971A AU2003266971A1 (en) 2002-08-13 2003-08-07 Heat exchanger
EP03747885A EP1530703B1 (fr) 2002-08-13 2003-08-07 Echangeur thermique
DE50308809T DE50308809D1 (de) 2002-08-13 2003-08-07 Wärmeübertrager
US10/524,408 US20050236149A1 (en) 2002-08-13 2003-08-07 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10237648.4 2002-08-13
DE10237648A DE10237648A1 (de) 2002-08-13 2002-08-13 Wärmeübertrager

Publications (1)

Publication Number Publication Date
WO2004023056A1 true WO2004023056A1 (fr) 2004-03-18

Family

ID=30775359

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/008778 Ceased WO2004023056A1 (fr) 2002-08-13 2003-08-07 Echangeur thermique

Country Status (6)

Country Link
US (1) US20050236149A1 (fr)
EP (1) EP1530703B1 (fr)
AT (1) ATE380994T1 (fr)
AU (1) AU2003266971A1 (fr)
DE (2) DE10237648A1 (fr)
WO (1) WO2004023056A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007016423A2 (fr) 2005-08-01 2007-02-08 Girindus America Inc. Procede d'hydrogenation enantioselective de chromenes

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008019117A2 (fr) * 2006-08-05 2008-02-14 Modine Manufacturing Company Échangeur de chaleur et méthode
CN101936670B (zh) * 2009-06-30 2013-05-15 王磊 一种微通道、平行流、全铝扁管焊接式结构换热器及应用
WO2014056587A1 (fr) * 2012-10-09 2014-04-17 Linde Aktiengesellschaft Mesure de température au moyen d'un guide d'ondes lumineuses dans un échangeur de chaleur à plaques

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04131696A (ja) * 1990-09-21 1992-05-06 Sanden Corp 熱交換器及びその製造方法
EP0654645B1 (fr) 1993-11-24 1999-01-07 Showa Aluminum Corporation Echangeur de chaleur
EP0943884A1 (fr) * 1996-12-05 1999-09-22 Showa Aluminum Corporation Echangeur de chaleur
EP0947792A2 (fr) * 1998-04-03 1999-10-06 Denso Corporation Evaporateur pour réfrigérant et sa méthode de fabrication
US6032728A (en) * 1998-11-12 2000-03-07 Livernois Research & Development Co. Variable pitch heat exchanger
EP1014027A1 (fr) * 1998-12-23 2000-06-28 MAGNETI MARELLI CLIMATIZZAZIONE S.p.A. Condenseur pour systèmes de climatisation de véhicules
US6196304B1 (en) * 1996-08-31 2001-03-06 Behr Gmbh & Co. Tube-block-type heat transfer device and method of making same
JP2001280884A (ja) * 2000-03-30 2001-10-10 Calsonic Kansei Corp 熱交換器

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1847743A (en) * 1929-12-05 1932-03-01 Hart & Hutchinson Company Radiator header and tube connection
US5009262A (en) * 1990-06-19 1991-04-23 General Motors Corporation Combination radiator and condenser apparatus for motor vehicle
US5174373A (en) * 1990-07-13 1992-12-29 Sanden Corporation Heat exchanger
JP2968063B2 (ja) * 1991-02-20 1999-10-25 サンデン株式会社 熱交換器
US5111878A (en) * 1991-07-01 1992-05-12 General Motors Corporation U-flow heat exchanger tubing with improved fluid flow distribution
DE4122961A1 (de) * 1991-07-11 1993-01-14 Kloeckner Humboldt Deutz Ag Waermeaustauscher
EP0586037B1 (fr) * 1992-09-03 1997-05-21 Modine Manufacturing Company Echangeur de chaleur
DE69419197T2 (de) * 1993-04-30 1999-11-25 Sanden Corp., Isesaki Wärmetauscher
FR2705143B1 (fr) * 1993-05-11 1995-06-23 Valeo Thermique Moteur Sa Echangeur de chaleur notamment pour vehicule automobile.
JPH07305990A (ja) * 1994-05-16 1995-11-21 Sanden Corp 多管式熱交換器
FR2721099B1 (fr) * 1994-06-08 1996-07-19 Valeo Thermique Moteur Sa Echangeur de chaleur utile notamment pour le refroidissement d'un flux d'air à haute température.
JPH08254399A (ja) * 1995-01-19 1996-10-01 Zexel Corp 熱交換器
FR2737287B1 (fr) * 1995-07-25 1997-09-12 Valeo Thermique Moteur Sa Echangeur de chaleur a boite collectrice sous forme d'un empilement
US5941303A (en) * 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
JP4107051B2 (ja) * 2002-02-19 2008-06-25 株式会社デンソー 熱交換器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04131696A (ja) * 1990-09-21 1992-05-06 Sanden Corp 熱交換器及びその製造方法
EP0654645B1 (fr) 1993-11-24 1999-01-07 Showa Aluminum Corporation Echangeur de chaleur
US6196304B1 (en) * 1996-08-31 2001-03-06 Behr Gmbh & Co. Tube-block-type heat transfer device and method of making same
EP0943884A1 (fr) * 1996-12-05 1999-09-22 Showa Aluminum Corporation Echangeur de chaleur
EP0947792A2 (fr) * 1998-04-03 1999-10-06 Denso Corporation Evaporateur pour réfrigérant et sa méthode de fabrication
US6032728A (en) * 1998-11-12 2000-03-07 Livernois Research & Development Co. Variable pitch heat exchanger
EP1014027A1 (fr) * 1998-12-23 2000-06-28 MAGNETI MARELLI CLIMATIZZAZIONE S.p.A. Condenseur pour systèmes de climatisation de véhicules
JP2001280884A (ja) * 2000-03-30 2001-10-10 Calsonic Kansei Corp 熱交換器

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 016, no. 395 (M - 1299) 21 August 1992 (1992-08-21) *
PATENT ABSTRACTS OF JAPAN vol. 2002, no. 02 2 April 2002 (2002-04-02) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007016423A2 (fr) 2005-08-01 2007-02-08 Girindus America Inc. Procede d'hydrogenation enantioselective de chromenes

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US20050236149A1 (en) 2005-10-27
DE10237648A1 (de) 2004-02-26
AU2003266971A1 (en) 2004-03-29
DE50308809D1 (de) 2008-01-24
EP1530703B1 (fr) 2007-12-12
EP1530703A1 (fr) 2005-05-18

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