EP0030072A2 - Echangeur de chaleur et procédé pour sa fabrication - Google Patents

Echangeur de chaleur et procédé pour sa fabrication Download PDF

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Publication number
EP0030072A2
EP0030072A2 EP80303431A EP80303431A EP0030072A2 EP 0030072 A2 EP0030072 A2 EP 0030072A2 EP 80303431 A EP80303431 A EP 80303431A EP 80303431 A EP80303431 A EP 80303431A EP 0030072 A2 EP0030072 A2 EP 0030072A2
Authority
EP
European Patent Office
Prior art keywords
tube
projections
heat exchanger
strip
fins
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP80303431A
Other languages
German (de)
English (en)
Other versions
EP0030072B1 (fr
EP0030072A3 (en
Inventor
Naonori Kanda
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.)
Denso Corp
Original Assignee
NipponDenso Co Ltd
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
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Application filed by NipponDenso Co Ltd filed Critical NipponDenso Co Ltd
Publication of EP0030072A2 publication Critical patent/EP0030072A2/fr
Publication of EP0030072A3 publication Critical patent/EP0030072A3/en
Application granted granted Critical
Publication of EP0030072B1 publication Critical patent/EP0030072B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—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
    • 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
    • F28D1/0391—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 a single plate being bent to form one or more conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0096—Radiators for space heating

Definitions

  • This invention relates to heat exchangers, more particularly, but not exclusively, for use as radiators for dissipating heat from the cooling water of engines of automotive vehicles.
  • the invention also relates to methods of fabricating such heat exchangers.
  • the radiators of automotive vehicle engines have to withstand vibrations transmitted from the vehicle bodies and also internal pressure caused by a rise in the temperature of the engine cooling water.
  • the tubes of such radiators need to have high endurance strength.
  • US patent 2,011,854 discloses a corrugated fin type radiator including a flat tube formed on its outer surface with ribs or spherical projections.
  • US patent 1,993,872 also discloses a corrugated fin type radiator including a flat tube formed on its surface with irregularities of a large size to increase the area of contact with corrugated fins. In these two radiators, the irregularities on the surface of the flat tube are of large size, so that difficulties would be encountered in bringing the irregularities of the tube into contact with the fins.
  • a heat exchanger comprising:
  • FIG. 1 shows in a front view one embodiment of the heat exchanger in conformity with the invention.
  • the heat exchanger shown is used as a radiator of an engine of an automotive vehicle.
  • the numeral 1 designates an inlet tank made of synthetic resinous material or brass for receiving engine cooling water through a cooling water inlet pipe 2 and distributing it to a tube 3.
  • the inlet tank 1 is formed with an inlet port 4 for injecting the engine cooling water therethrough into the inlet tank 1.
  • the numeral 5 designates corrugated fins thermally connected to the tube 3 along its length as by welding.
  • the corrugated fins 5 and the tube 3 form a radiator core which is a heat dissipating portion of a radiator 6.
  • the numeral 7 designates an outlet tank made of a synthetic resinous material or brass for collecting the engine cooling water which is led from the tank 7 through a cooling water outlet pipe 8 to an engine, not shown.
  • the tube 3 is formed by shaping a brass strip (having a thickness of 0.13 mm, for example) into a flat tube as shown in Figure 2.
  • the flat tube 3 is arranged in such a manner that the longitudinal cross section of the tube 3 is parallel to an air current W supplied to the radiator 6 from a blower, not shown. Only one row is arranged with respect to the direction of air current as shown in Figure 2.
  • the width C of the corrugated fins 5 is not much different from the length A (major dimension) of the tube 3, so that the thickness of the radiator 6 can be greatly reduced.
  • the tube 3 has a width D (minor dimension) which is about 2 mm.
  • the tube 3 is formed with a multiplicity of projections 3A each forming the vertex of a triangle and arranged substantially perpendicular to the axis of the tube in strip form.
  • the projections 3A each have a height B smaller than the thickness of the wall of the tube 3 and may be 0.02 mm, for example.
  • the projections 3A are spaced apart from each other by a spacing interval Tp of about 0.87 mm.
  • a process for shaping the tube 3 will be described.
  • an apparatus shown schematically in Figure 4 is used.
  • a metal strip 10 is paid out of a coil 9 of metal strip and supplied to a first forming roller group 11A, 11B, 11C and 11D which successively bends the metal strip 10 into shapes shown in Figures 5A to 5E.
  • the pair of rollers 11A disposed nearest the coil 9 is formed with elevations 11' as shown in Figure 6, so that the strip 10 is formed with the projections 3A when it passes between the rollers 11A.
  • the strip 10 is bent by the first forming roller group 11A, 11B, 11C and 11D into the shape shown in Figure 5E and then has its seam portion 10A (see Figure 7) compressed by seamer rollers 12.
  • a second forming roller group 13 forms the strip 10 into the shape shown in Figure 5F.
  • the strip 10 thus seamed is introduced into a solder tank 14 to have a coat of solder applied thereto, and then introduced into a cooling tank 15 where the solder-coated strip 10 is suddenly cooled. Thereafter the strip 10 is supplied to a finishing roller group 16 which gives finishing touches to the strip 10 to give a desired shape to the tube 3.
  • the tube 3 is cut into predetermined lengths in a cutting section 17, thereby completing the operation of forming the tube 3.
  • the numeral 18 designates a pulse generator for controlling cutting of the tube 3 into the desired lengths in the cutting section 17.
  • the strip 10 is formed with the projections 3A by the first forming roller group 11A, 11B, 11C and 11D to provide the tube 3 with the projections 3A, so that a number of projections 3A are formed in the seam portion 10A.
  • the presence of the projections 3A enables the solder to penetrate deep into the seam portion 10A when the strip 10 is introduced into the solder tank 14. In this type of seamed tube, a lack of solder in the seam portion 10A tends to cause leaks from the tube 3, and it has hitherto been customary to apply a coat of solder of a thickness greater than is necessary to ensure that the accident of cooling water leaks from the tube 3 does not occur.
  • the presence of the projections 3A enables the seam portion 10A to be soldered with enough strength to prevent cooling water leaks from taking place by minimizing the amount of the solder used. This is conducive to increase strength of the tube 3 and reduced cost thereof.
  • the corrugated fins 5 are formed by shaping a strip of copper (having a thickness of 0.05 to 0.06 mm, for example) in such a manner that the fins have a spacing interval Fp of about 2.0 to 3.5 mm as shown in Figure 2.
  • the fins 5 are each formed with a plurality of louvres 5A by cutting and raising the material at an angle of 20 to 30 0 .
  • the corrugated fins 5 and the tube 3 are joined to one another as follows.
  • the tube 3 has a coat of solder applied to its surface as aforesaid.
  • the lengths of tube 3 are assembled with the corrugated fins 5 by using a jig.
  • the tube 3 and fin 5 assembly is placed in a furnace and heated to melt the coat of solder on the tube 3, so that the corrugated fins 5 are rigidly joined to the lengths of tube 3 by the molten solder.
  • the tube 3 is formed with the projections 3A arranged in strip form.
  • the height B of the projections 3A is only about 0.02 mm which is small as compared with the minor dimension D of the tube 3 and is smaller than the thickness of the wall of the tube 3. Thus no special attention need be paid to the positions of the projections 3A when the tube 3 is assembled with the corrugated fins 5.
  • the radiator 6 including the tube 3 and corrugated fins 5 assembled as described hereinabove has the advantage that the tube 3 has high bending rigidity by virtue of the presence of a multiplicity of projections 3A arranged in strip form.
  • the tube 3 shown in Figure 3 was formed to have the projections 3A having a height B of 0.02 mm and a spacing interval Tp of 0.37 mm, and a tube formed with no projections was also formed.
  • Tp 0.37
  • the tube formed with no projections was also formed.
  • the values of the height B and spacing interval Tp of the projections 3A described hereinabove are given as one example. It has been ascertained that the tube 3 of high strength can be produced when the height B is in the range between 0.02 and 0.1 mm and the spacing interval Tp is in the range between 0.87 and 1.0 mm. Stated differently, if the height B of the projections 3A is smaller than the thickness of the wall of the tube 3, the minor dimension D of the tube will not show large variations depending on the position of the projections 3A. Consequently, no special attention need be paid to the position of the projections 3A when the corrugated fins 5 are joined to the tube 3, in obtaining satisfactory assembling of the fins 5 with the tube 3.
  • the tube 3 has greatly increased strength.
  • the tube 3 can have sufficiently high endurance strength to have a prolonged service life even if the thickness of the wall is reduced as compared with tubes of the prior art. This is conducive to material conservation and reduced cost.
  • the tube 3 can have its wall thickness reduced as compared with the wall thickness of tubes of the prior art, the amount of heat dissipated through the wall of the tube 3 is increased and the efficiency with which heat exchange takes place is increased.
  • the provision of the projections 3A greatly increases the surface area of the tube 3, thereby also contributing to increased efficiency with heat exchange takes place through the wall of the tube 3.
  • the tube 3 has increased rigidity, so that the side of the tube 3 coming into direct contact with the fins 5 can be kept in a 'straight line without curving.
  • the fins 5 can be positively maintained in contact with the tube 3 along its entire length. This enables good transfer of heat from the tube 3 to the fins 5 to be obtained, thereby further increasing the efficiency with which heat exchange takes place through the tube 3.
  • the lengths of tube 3 necessarily have a large axial dimension.
  • the provision of the projections 3A in the tube of a heat exchanger, such as the radiator 6 shown in Figure 2, has the great effect of increasing the strength of the tube 3.
  • the projections 3A are each formed in Figure 3 as constituting the vertex of a triangle.
  • the invention is not limited to this form of projections 3A, and each projection may constitute the top point of an arc as shown in Figure 8 or a trapezoid as shown in Figure 9.
  • the projections 3A are of a shape such that the bending rigidity of the tube 3 can be increased.
  • the projections 3A are formed by working the strip 10 from both sides thereof by means of the first pair of forming rollers 1A shown in Figure 6.
  • the projections 3A may be formed by working the strip 10 only from one side as shown in Figure 10 and 11.
  • Figure 11 there is shown a modification of the embodiment in which large irregularities are formed in the seam_portion 10A so that a large quantity of solder will penetrate deep into the seam portion 10A.
  • the projections 3A have been described as being formed on the entire periphery of the tube 3.
  • the side of the tube that is brought into contact with the fins shows a greatest reduction in strength. Therefore, the projections 3A may be formed only on the side of the tube 3 that comes into contact with the fins 5.
  • the multiplicity of projections 3A have been described as being arranged in strip form in a direction perpendicular to the axis of the tube 3.
  • the projections 3A may be arranged, as shown in Figure 12, in strip form in a direction oblique to the axis of the tube 3B, or, as shown in Figures 13 and 14, in wave form as in tubes 3C and 3D.
  • the fins 5 are each joined to the tube 3 by straddling a plurality of projections 3A.
  • the projections 3A are filled with solder on their undersides and a strong joint is formed thermally between the tube 3 and fins 5.
  • the tube 3 has been described as being shaped by subjecting the strip 10 to seaming. However, the tube 3 may be first formed by drawing or welding without forming the seal portion 10A as in tubes 3E and 3F shown in Figures 15 and 16 respectively, and the projections 3A may be formed in the tube 3 as shown in Figure 17 after the tube 3 has been formed.
  • the numeral 19 designates a stationary core for imparting a correct shape to the tube 3.
  • the core 19 is inserted in the tube 3 which is held between rollers 20 for forming the projections 3A on its surface while being pressed into a flat shape.
  • the tube 3F shown in Figure 16 is elliptic in cross section.
  • the tube of a heat exchanger is generally very small in wall thickness. Even if the tube is elliptic in cross section like the tube 3F, the small wall thickness renders the side of the tube planar when the tube is assembled with the fins.
  • Brass has been described as being used for making the tube 3.
  • the invention is not limited to a specific material for making the tube 3, and other suitable material, such as aluminium or stainless steel, may be used.
  • the spacing interval Tp between the adjacent projections 3A has been described as being smaller than the spacing interval Fp between the adjacent fins 5. However, even if the spacing interval Tp between the projections 3A is equal to or larger than the spacing interval Fp between the fins 5, the effects described as being achieved can be achieved to a certain extent.
  • the heat exchanger has been described as being used as a radiator of an engine of an automotive vehicle for dissipating heat from engine cooling water.
  • the heat exchanger is not limited to a radiator of the type described and may be used as a heat dissipator for warm water suitable for use with heating equipment for houshold use or for use in a motor vehicle, or in many other applications.
  • the heat exchanger comprises a tube of a flat cross-sectional shape formed with a multiplicity of projections arranged in strip form in a direction that intersects the axis of the tube at least on a surface thereof on which the tube is in thermal contact with corrugated fins.
  • the tube has its strength greatly increased and the endurance strength of the tube can be greatly increased by using material of a small thickness for making the tube while at the same time improving the efficiency with which heat exchange takes place. Formation of the projections increases the surface area of the tube, thereby to further increase heat exchanging efficiency.
  • the projections formed on the surface of the flat tube each extend by less than the thickness of the wall of the tube which is small enough, as compared with the minor dimension of the tube, not to make it necessary to pay special attention to the position of the projections when the tube is joined to the corrugated fins. Thus fabrication of the heat exchanger is facilitated.

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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)
EP19800303431 1979-11-30 1980-09-29 Echangeur de chaleur et procédé pour sa fabrication Expired EP0030072B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP15607079A JPS5680698A (en) 1979-11-30 1979-11-30 Heat exchanger
JP156070/79 1979-11-30

Publications (3)

Publication Number Publication Date
EP0030072A2 true EP0030072A2 (fr) 1981-06-10
EP0030072A3 EP0030072A3 (en) 1981-12-16
EP0030072B1 EP0030072B1 (fr) 1983-11-23

Family

ID=15619638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800303431 Expired EP0030072B1 (fr) 1979-11-30 1980-09-29 Echangeur de chaleur et procédé pour sa fabrication

Country Status (5)

Country Link
EP (1) EP0030072B1 (fr)
JP (1) JPS5680698A (fr)
AU (1) AU521345B2 (fr)
CA (1) CA1133892A (fr)
DE (1) DE3065701D1 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0109393A1 (fr) * 1982-05-19 1984-05-30 Ford Motor Co Tube de radiateur a turbulence pour une construction de radiateur.
EP0162827A2 (fr) * 1984-05-24 1985-11-27 Armaturjonsson AB Tube pour échangeur de chaleur
EP0519334A2 (fr) * 1991-06-20 1992-12-23 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Echangeur de chaleur à tubes plats, procédé pour sa fabrication, applications et tubes plats pour échangeur de chaleur
FR2709816A1 (fr) * 1993-09-07 1995-03-17 Valeo Thermique Moteur Sa Echangeur de chaleur brasé utile notamment comme condenseur de climatisation pour véhicule.
EP0650023A1 (fr) * 1993-10-22 1995-04-26 Zexel Corporation Echangeur de chaleur à plusieurs tubes
DE4446754A1 (de) * 1994-12-24 1996-06-27 Behr Gmbh & Co Verfahren zur Herstellung eines Wärmetauschers
EP0773419A3 (fr) * 1995-11-13 1998-08-19 Denso Corporation Echangeur de chaleur
US5992514A (en) * 1995-11-13 1999-11-30 Denso Corporation Heat exchanger having several exchanging portions
US6892806B2 (en) 2000-06-17 2005-05-17 Behr Gmbh & Co. Heat exchanger for motor vehicles
US7059399B2 (en) * 2003-09-04 2006-06-13 Lg Electronics Inc. Heat exchanger with flat tubes
FR2906355A1 (fr) * 2006-09-21 2008-03-28 Valeo Systemes Thermiques Tube pour echangeur de chaleur,echangeur comportant un tel tube et procede de fabrication d'un tel tube
DE102007008535A1 (de) * 2007-02-21 2008-08-28 Modine Manufacturing Co., Racine Wärmetauschernetz, Herstellungsverfahren und Walzenstraße
DE102008013018A1 (de) 2008-03-07 2009-09-10 Modine Manufacturing Co., Racine Flaches Wärmetauscherrohr
DE19758886B4 (de) * 1997-05-07 2017-09-21 Valeo Klimatechnik Gmbh & Co. Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
DE102004045018B4 (de) 2003-09-30 2019-08-01 Mahle International Gmbh Verfahren zur Herstellung eines flachen Rohres für einen Wärmetauscher eines Kraftfahrzeugs, flaches Rohr, Verfahren zur Herstellung eines Wärmetauschers und Wärmetauscher
FR3126760A1 (fr) * 2021-09-03 2023-03-10 Valeo Systemes Thermiques Echangeur de chaleur d’une boucle de fluide refrigerant.
EP4206746A1 (fr) * 2021-12-31 2023-07-05 Nuctech Company Limited Structure de dissipation de chaleur et appareil d'inspection

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6361891A (ja) * 1986-09-03 1988-03-18 Nippon Denso Co Ltd 熱交換器
US5292056A (en) * 1990-12-08 1994-03-08 Gea Luftkuhler Gmbh method of welding heat exchangers
JPH0624326U (ja) * 1992-06-08 1994-03-29 三機工業株式会社 クリーンルームの壁面の配線貫通部の気密構造
US6595273B2 (en) 2001-08-08 2003-07-22 Denso Corporation Heat exchanger
EP1938034A1 (fr) * 2005-10-14 2008-07-02 Behr GmbH & Co. KG Echangeur de chaleur
FR3040478B1 (fr) * 2015-08-25 2017-12-15 Valeo Systemes Thermiques Echangeur de chaleur

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1993872A (en) * 1932-04-06 1935-03-12 Gen Motors Corp Radiator core
US2011854A (en) * 1934-03-23 1935-08-20 Gen Motors Corp Method of making radiator cores
GB489061A (en) * 1937-06-05 1938-07-19 Peter Heiss Radiator for internal combustion engines
FR1586070A (fr) * 1968-10-24 1970-02-06
FR2243037A1 (fr) * 1973-09-06 1975-04-04 Chausson Usines Sa
DE2912723A1 (de) * 1978-04-03 1979-10-11 Mulock Bentley & Ass Waermetauscher

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50101261U (fr) * 1974-01-23 1975-08-21
JPS51163574U (fr) * 1975-06-20 1976-12-27

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1993872A (en) * 1932-04-06 1935-03-12 Gen Motors Corp Radiator core
US2011854A (en) * 1934-03-23 1935-08-20 Gen Motors Corp Method of making radiator cores
GB489061A (en) * 1937-06-05 1938-07-19 Peter Heiss Radiator for internal combustion engines
FR1586070A (fr) * 1968-10-24 1970-02-06
FR2243037A1 (fr) * 1973-09-06 1975-04-04 Chausson Usines Sa
GB1482288A (en) * 1973-09-06 1977-08-10 Chausson Usines Sa Tubular heat exchangers
DE2912723A1 (de) * 1978-04-03 1979-10-11 Mulock Bentley & Ass Waermetauscher

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0109393A1 (fr) * 1982-05-19 1984-05-30 Ford Motor Co Tube de radiateur a turbulence pour une construction de radiateur.
EP0109393A4 (fr) * 1982-05-19 1984-09-19 Ford Motor Co Tube de radiateur a turbulence pour une construction de radiateur.
EP0162827A2 (fr) * 1984-05-24 1985-11-27 Armaturjonsson AB Tube pour échangeur de chaleur
EP0162827A3 (fr) * 1984-05-24 1986-10-01 Armaturjonsson AB Tube pour échangeur de chaleur
EP0519334A2 (fr) * 1991-06-20 1992-12-23 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Echangeur de chaleur à tubes plats, procédé pour sa fabrication, applications et tubes plats pour échangeur de chaleur
EP0519334A3 (en) * 1991-06-20 1993-04-21 Thermal-Werke Waerme-, Kaelte-, Klimatechnik Gmbh Flat tube heat exchanger, process for manufacturing same, applications and flat tubes for heat exchanger
US5251692A (en) * 1991-06-20 1993-10-12 Thermal-Werke Warme-, Kalte-, Klimatechnik Gmbh Flat tube heat exchanger, method of making the same and flat tubes for the heat exchanger
FR2709816A1 (fr) * 1993-09-07 1995-03-17 Valeo Thermique Moteur Sa Echangeur de chaleur brasé utile notamment comme condenseur de climatisation pour véhicule.
EP0650023A1 (fr) * 1993-10-22 1995-04-26 Zexel Corporation Echangeur de chaleur à plusieurs tubes
DE4446754A1 (de) * 1994-12-24 1996-06-27 Behr Gmbh & Co Verfahren zur Herstellung eines Wärmetauschers
US5709028A (en) * 1994-12-24 1998-01-20 Behr Gmbh & Co. Process of manufacturing a heat exchanger
US5992514A (en) * 1995-11-13 1999-11-30 Denso Corporation Heat exchanger having several exchanging portions
EP0773419A3 (fr) * 1995-11-13 1998-08-19 Denso Corporation Echangeur de chaleur
DE19758886B4 (de) * 1997-05-07 2017-09-21 Valeo Klimatechnik Gmbh & Co. Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
US6892806B2 (en) 2000-06-17 2005-05-17 Behr Gmbh & Co. Heat exchanger for motor vehicles
US7347254B2 (en) 2000-06-17 2008-03-25 Behr Gmbh & Co. Heat exchanger for motor vehicles
DE10127084B4 (de) 2000-06-17 2019-05-29 Mahle International Gmbh Wärmeübertrager, insbesondere für Kraftfahrzeuge
US7059399B2 (en) * 2003-09-04 2006-06-13 Lg Electronics Inc. Heat exchanger with flat tubes
DE102004045018B4 (de) 2003-09-30 2019-08-01 Mahle International Gmbh Verfahren zur Herstellung eines flachen Rohres für einen Wärmetauscher eines Kraftfahrzeugs, flaches Rohr, Verfahren zur Herstellung eines Wärmetauschers und Wärmetauscher
FR2906355A1 (fr) * 2006-09-21 2008-03-28 Valeo Systemes Thermiques Tube pour echangeur de chaleur,echangeur comportant un tel tube et procede de fabrication d'un tel tube
DE102007008535A1 (de) * 2007-02-21 2008-08-28 Modine Manufacturing Co., Racine Wärmetauschernetz, Herstellungsverfahren und Walzenstraße
DE102008013018A1 (de) 2008-03-07 2009-09-10 Modine Manufacturing Co., Racine Flaches Wärmetauscherrohr
FR3126760A1 (fr) * 2021-09-03 2023-03-10 Valeo Systemes Thermiques Echangeur de chaleur d’une boucle de fluide refrigerant.
EP4206746A1 (fr) * 2021-12-31 2023-07-05 Nuctech Company Limited Structure de dissipation de chaleur et appareil d'inspection

Also Published As

Publication number Publication date
AU521345B2 (en) 1982-03-25
EP0030072B1 (fr) 1983-11-23
EP0030072A3 (en) 1981-12-16
CA1133892A (fr) 1982-10-19
DE3065701D1 (en) 1983-12-29
AU6263980A (en) 1981-06-25
JPS5680698A (en) 1981-07-02
JPH0118353B2 (fr) 1989-04-05

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