EP0889299A2 - Wärmetauscher mit Doppelrohrkonstruktion - Google Patents

Wärmetauscher mit Doppelrohrkonstruktion Download PDF

Info

Publication number
EP0889299A2
EP0889299A2 EP98112413A EP98112413A EP0889299A2 EP 0889299 A2 EP0889299 A2 EP 0889299A2 EP 98112413 A EP98112413 A EP 98112413A EP 98112413 A EP98112413 A EP 98112413A EP 0889299 A2 EP0889299 A2 EP 0889299A2
Authority
EP
European Patent Office
Prior art keywords
double pipe
heat exchanger
pipe type
passage
type heat
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
EP98112413A
Other languages
English (en)
French (fr)
Other versions
EP0889299B1 (de
EP0889299A3 (de
Inventor
Tatsuo Denso Corp. Intel. Pro. Dept. Sugimoto
Akira Denso Corp. Intel. Pro. Dept. Uchikawa
Takaaki Denso Corp. Intel. Pro. Dept. Sakane
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
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of EP0889299A2 publication Critical patent/EP0889299A2/de
Publication of EP0889299A3 publication Critical patent/EP0889299A3/de
Application granted granted Critical
Publication of EP0889299B1 publication Critical patent/EP0889299B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial 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
    • F28F9/0234—Header boxes; End plates having a second heat exchanger disposed there within, e.g. oil cooler

Definitions

  • the present invention relates to a heat exchanger applied to an oil cooler installed in a vehicle radiator and having a double pipe construction, in which a circle-like fluid passage through which a second fluid flows to be heat exchanged with first fluid is formed thereinside.
  • a double pipe type oil cooler 100 is well known.
  • This oil cooler 100 is installed in a lower tank 102 of a vehicle radiator for cooling vehicle engine cooling water.
  • This oil cooler 100 cools lubrication oil by carrying out heat exchange between the cooling water introduced from a tube 103 of the radiator and the lubrication oil flowing in the oil cooler 100.
  • the oil cooler 100 includes an outer cylindrical pipe 104, an inner cylindrical pipe 105, an oil passage 106, an inner fin 107 provided in the oil passage 106, and a connecting member 109 for connecting the outer cylindrical pipe 104 to an external connecting pipe 108.
  • the outside wall surface of the outer cylindrical pipe 104 contacts the cooling water flowing from the tube 103.
  • the inner cylindrical pipe 105 is disposed inside the outer cylindrical pipe 104, and the center axis of the inner cylindrical pipe 105 is concentric to that of the outer cylindrical pipe 104.
  • the oil passage 106 is formed between the outer cylindrical pipe 104 and the inner cylindrical pipe 105.
  • the lubrication-oil flows into the oil cooler 100 through the connecting pipe 108 and circulates therein.
  • the diameter of the oil cooler 100 is set larger than the width (WT) of the tube 103, for attaining a sufficient radiation area. Therefore, the cooling water stagnates around the lower portion of the oil cooler 100. Thus, the cooling water flow speed decreases around the lower portion of the oil cooler 100, and the cooling water side heat transmitting efficiency is lessened. Further, in the conventional oil cooler, the cooling water flow flowing from the tube 103 into the lower tank 102 is not used efficiently for improving the cooling performance of the oil cooler 100.
  • JP-U-58-46969 discloses a double pipe type oil cooler installed in a radiator tank, which includes cross sectional 8-shaped outer and inner cylindrical pipes. However, in this reference, no relation between the radiator tube and the oil cooler is disclosed.
  • JP-U-58-524623 discloses a double pipe type oil cooler that is installed into a radiator tank, and that includes cross sectional flat or rectangular shaped outer and inner cylindrical pipes.
  • this double pipe type oil cooler the longitudinal axis of the oil cooler is arranged perpendicularly relative to the cooling water flow direction flowing from the tube, and the latitudinal axis thereof is arranged along the cooling water flow direction. Therefore, the cooling water stagnates around the bottom portion of the oil cooler. Thus, the cooling water flow speed decreases around the bottom portion of the oil cooler and the cooling water side heat transmitting efficiency is lessened. That is, the cooling water flowing from the tube into the radiator tank is not used efficiently. Further, when the radiating area thereof is set the same as the conventional cylindrical double pipe type oil cooler, the width dimension of the tank needs to be large, and the width dimension of the radiator is made large.
  • JP-U-59-71071 discloses a double pipe type oil cooler installed in a radiator tank, which includes cross sectional elliptic shaped outer and inner cylindrical pipes. Further, JP-A-3-233129 discloses a double pipe type oil cooler which includes cross sectional substantially U-shaped outer and inner cylindrical pipes. In these oil coolers, as the diameter of the oil cooler is larger than the width of the radiator tube, the position of maximum cooling water flow speed is not used efficiently for cooling.
  • a double pipe type heat exchanger is disposed within lines extending from both sides of an upstream side fluid passage, which defines the width dimension thereof. That is, the double pipe type heat exchanger is located at a position where the flow speed of a first fluid is a maximum. Thereby, as the first fluid flows from the upstream side fluid passage and is used efficiently for heat exchanging, the heat exchanging performance of the entire double pipe type heat exchanger is further improved.
  • a double pipe type heat exchanger is formed into s flat shaped double pipe in which the longitudinal axis thereof is more twice as long as the latitudinal axis thereof, and the latitudinal axis of the heat exchanger is smaller than the width dimension of an upstream side fluid passage.
  • the outside wall surface area of the double pipe type heat exchanger contacting the cooling water can be made large.
  • a double pipe type oil cooler 1 cools lubrication oil for a vehicle engine by carrying out heat exchange between the lubrication oil and cooling water for the vehicle engine.
  • the double pipe type oil cooler 1 is installed in a lower tank 3 of a vehicle radiator.
  • the lower tank 3 is connected to the lower ends of a plurality of tubes 2 of the radiator disposed at the position, where the radiator is likely to receive an air generated by running dynamic pressure of the vehicle.
  • Each tube 2 is made of a metal, such as an aluminum alloy, that has superior heat transmitting performance, and that is formed into a flat oval shape.
  • the tube 2 forms an upstream side cooling water passage 4 through which the cooling water flows downwardly. When the cooling water flows through the upstream side cooling water passage 4, the cooling water is heat exchanged with the air passing by the outside surface of the tube 2 and is cooled.
  • a corrugated fin (not illustrated) is provided between each pair of adjacent tubes 2 for improving the heat transmitting performance.
  • a lower tank 3 includes a core plate 5 made of aluminum alloy, a capsule 7 made of resin, and a downstream side cooling water passage 8 into which the cooling water flows from the plural tubes 2.
  • the capsule 7 is fixed to the core plate 5 by crimping, through a sealing member 6 such as rubber packing.
  • the core plate 5 includes a plurality of insertion holes 5a into which the downstream side ends of the plural tubes 2 are inserted.
  • the downstream side ends of the tubes 2 are brazed with the core plate 5.
  • the capsule 7 is made of resin such as nylon and formed into vessel-shape, that is, the cross sectional shape thereof is formed into a substantially U-shaped configuration.
  • the capsule 7 includes two circle-shaped insertion holes 7a into which a nipple 10 of the oil cooler 1 is inserted.
  • the insertion holes 7 are formed on the side wall of the capsule 7.
  • the capsule 7 may be made of metal.
  • the double-pipe type oil cooler 1 includes two nipples 10 as connecting members, an outer cylindrical pipe 11, an inner cylindrical pipe 12, an oil passage 13 through which the lubrication oil circulates, a cooling water passage 14 through which the cooling water circulates, and an inner fin 15.
  • the outer cylindrical pipe 11 is formed to separate into double members 11a, 11b, and is connected to the nipple 10.
  • the inner cylindrical pipe 12 is provided inside the outer cylindrical pipe 11.
  • the oil passage 13 is formed between the outer cylindrical pipe 11 and the inner cylindrical pipe 12.
  • the cooling water passage 14 is formed inside the inner cylindrical pipe 12.
  • the inner fin 15 is disposed inside the oil passage 13.
  • Each nipple 10 is inserted into the insertion hole 7a of the capsule 7, and a seal member 16 such as an O-ring is disposed between the nipple 10 and the inside wall of the capsule 7.
  • An outer peripheral screw portion 19 is formed at the outer periphery of a cylindrical pipe portion protruding from the outside wall of the capsule 7.
  • a nut 17 and an external connecting pipe 18 are screwed on the outer peripheral screw portion 19.
  • One is an inlet side external connecting pipe 18, and the other is an outlet side external connecting pipe 18.
  • the inlet side external connecting pipe 18 connects to the oil cooler 1 and a torque converter (not illustrated) of a vehicle automatic transmission.
  • the outlet side external connecting pipe 18 connects to an oil-pump or an oil pan (not illustrated).
  • the oil flows from the torque converter, through the oil cooler 1, and into the oil pump or the oil pan, or flows from the oil pump or the oil pan, through the oil cooler 1, and into the torque converter.
  • the outer cylindrical pipe 11 is made of metal, such as an aluminum alloy or brass, and formed into a flat shape.
  • the outer cylindrical pipe 11 is formed by crimp-connecting a pair of saucer-like metal plates 11a, 11b facing each other at the outer peripheries thereof.
  • the metal plates 11a, 11b include concave portions, and these concave portions face each other.
  • the outer cylindrical pipe 11 is formed into a configuration that is oval in cross-section, the longitudinal axis direction of which is along the cooling water flow direction from the tube 2 to the lower tank 3. That is, the latitudinal axis of the oval shape is perpendicular to the cooling water flow direction.
  • the longitudinal axis length (HO) is more twice as long as the latitudinal axis length (WO).
  • HO is 3.4 times as long as WO.
  • the upper and lower ends of the outer cylindrical pipe 11 are formed into an arc-like portion 20, and the center portion of the outer cylindrical pipe 11 is formed into a generally portion 21 having a length LS.
  • the outer peripheral pipe 11 is disposed inside the downstream side cooling water passage 8 in the lower tank 3 in such a manner that a crimp portion 22 is located on the center axis of the tube 2.
  • the outer cylindrical pipe 11 is fixed to the nipple 10 such that the outer cylindrical pipe 11 is located within lines (dotted chain lines in FIG. 1) extending from the outer surfaces of the tube 2.
  • the width dimension WT between these lines is the width dimension of the tube 2 (for example, the outer diameter of the tube 2).
  • the inner cylindrical pipe 12 is made of a metal, such as an aluminum alloy or brass, and formed into an oval shape that is concentric to the outer cylindrical pipe 11.
  • the oil passage 13 is formed into an oval ring shape, and between the outer and inner cylindrical pipes 11, 12.
  • the cooling water passage 14 opens at both ends of the inner cylindrical pipe 11 in the rowing direction of the plural tubes 2.
  • the cooling water flowing in the downstream side cooling water passage 8 flows through the cooling water passage 14.
  • the inner fin 15 is disposed in the oil passage 13 for improving the oil side heat transmitting efficiency.
  • the lubrication oil flows through the inlet side external connecting pipe 18, and into the oil passage 13.
  • the lubrication oil circulates in the oil passage 13, heat exchanges with the cooling water, and flows out of the oil cooler 1 through the outlet side external connecting pipe 18.
  • the inner fin 15 is provided inside the oil passage 13, the oil side heat transmitting efficiency is high.
  • the cooling water flowing from the water jacket of the vehicle engine flows into the upper tank of the radiator.
  • the cooling water is distributed into each tube 2, and flows through the tube 2 while being cooled by heat exchanging with cooling air. After that, the cooling water flows from the lower end of the tube 2 and into the lower tank 3.
  • the cooling water is evenly divided by the crimp portion 22 of the oil cooler 1 into both sides of the outer cylindrical pipe 11.
  • the oil cooler 1 is disposed at the position where the flow speed of the cooling water is maximum, and has the straight portion 21.
  • the cooling water contacting the outside wall surface of the outer cylindrical pipe 11 flows smoothly without stagnating. Thereby, water side heat transmitting efficiency is further improved, and the lubrication-oil circulating in the oil passage 13 is cooled efficiently.
  • the oil cooler 1 is located at the position where the flow speed of the cooling water is maximum. That is, the oil cooler 1 is disposed within lines extending from the outer surfaces of the tube 2. The width dimension WT between these lines is the width dimension of the tube 2 (for example, the outer diameter of the tube 2). As the cooling water flowing from each tube 2 is used efficiently for cooling, the radiating performance of the entire oil cooler 1 is further improved.
  • the oil cooler 1 is formed into an oval flat shaped double pipe in which the longitudinal axis (HO) is more than twice as long as the latitudinal axis (WO), and the latitudinal axis of the oil cooler 1 is smaller than the outer diameter of the tube 2.
  • the outside wall surface area contacting the cooling water can be made large.
  • the latitudinal axis (WO) of the oil cooler 1 is set to be smaller than the outer diameter (WT) of the tube 2, the radiating performance of the oil cooler 1 is maintained.
  • the width dimensions of the tube 2 and the lower tank 3 are maintained, thereby maintaining the width dimension of the radiator.
  • the width dimension of the lower tank 3 is set substantially the same as that of the tube 2
  • the oil cooler 1 can be disposed inside the downstream side tank.
  • the width dimension of the downstream side tank such as a lower tank 3
  • the oil cooler 1 is disposed inside the lower tank 3 of the down-flow tyke radiator.
  • the oil cooler 1 may be provided inside the downstream side tank of a cross-flow type radiator instead.
  • the flow speed of the cooling water flowing from each tube in the cross-flow type radiator is higher than that in the down-flow type radiator, because the number of tubes in the cross-flow type radiator is smaller than that of the down-flow type radiator.
  • the flow speed of the cooling water flowing from each tube is high, because the flow amount of the cooling water circulating in the radiator increases. Therefore, when the oil cooler 1 of the present embodiment is used under these conditions, the cooling water side heat transmitting efficiency is improved more than under the condition in the present embodiment, and the radiating performance of the entire oil cooler 1 is further improved.
  • the double pipe type oil cooler 1 is installed in the lower tank 3 of the radiator.
  • the oil cooler 1 is disposed inside the lower tank 3 of the down flow type radiator in which the tubes 2 are arranged in two rows in a front and rear direction of the vehicle.
  • the inner fin provided in the oil passage 13 is not illustrated in FIG. 6.
  • the latitudinal axis length (WO) of the oil cooler 1 is set shorter than the width length (WT) of the tubes 2 arranged in two rows.
  • the oil cooler 1 is disposed inside the lower tank 3 in such a manner that the outer cylindrical pipe 11 is located within lines (one dotted chain lines in FIG. 6) extending from the outside surfaces of the tubes 2.
  • the width dimension WT between these lines is the width dimension between the outside surfaces of the tubes 2 arranged in two rows.
  • the upper end lower ends of the oil cooler 1 are formed into a shape that is half elliptic in cross section.
  • the heat exchanger of the present invention is applied to an oil cooler for cooling the torque converter oil of the vehicle automatic transmission.
  • the heat exchanger may be applied for cooling lubrication-oil for an engine installed into a vehicle, ship, air-plane, or railroad vehicle.
  • the heat exchanger of the present invention may be applied to a refrigerant condenser to carry out a heat exchange between the refrigerant and cooling medium for condensing the refrigerant, or a refrigerant evaporator to carry out a heat exchange between the refrigerant and heating medium for evaporating the refrigerant.
  • the heat exchanger may be applied for carrying out a heat exchange between a first gas flowing outside the outer cylindrical pipe and a second gas flowing inside the outer cylindrical pipe, and may be applied for heat exchanging between a liquid flowing outside the outer cylindrical pipe and a gas flowing inside the outer cylindrical pipe.
  • the oil cooler 1 is formed into an oval shape in cross section.
  • the oil cooler 1 may instead be formed into a semi-elliptical shape having a straight portion 21, or into a simple elliptical cross-sectional shape.
  • the oil cooler 1 may be formed into a pentagonal shape having a straight portion 21, or a trianglular shape having a straight portion 21 in cross section. Further, the oil cooler 1 may be formed into other polygon shapes such as a rectangular-shape.
  • the oil cooler 1 is, as shown in FIG. 9A, located within the outer diameter (WT) of the tube 2.
  • the oil cooler 1 may be located within the inner diameter (WT) of the tube 2 instead. That is, the width dimension of the tube 2 may be based on either the outer diameter or the inner diameter of the tube 2.
  • the width dimension (WT) may be based on the width of lines elongating from the center of the wall forming the tube 2 in the thickness direction thereof.
  • the width dimension of the tube 2 is based on the outer diameter of the tube 2, because the cooling water flows from the downstream side end of the tube 2 into the lower tank 3 while expanding.
  • a double pipe type oil cooler 1 installed in a vehicle radiator in which a tube 2 is used as an upstream side cooling water passage pipe, and a lower tank 3 is used as a downstream side cooling water passage pipe.
  • this heat exchanger may be applied to a triple pipe type heat exchanger (triple pipe type oil cooler) having an inlet side passage as the upstream side passage and an outermost cylindrical pipe as the downstream side passage.
  • a metal pipe, resin pipe or rubber hose may be used as the upstream side passage.
  • a metal tank, tube, oil-pan shaped vessel, metal pipe or resin pipe may be used as the downstream side passage.
  • the upstream side passage may be formed into a circlular, polygonal, or flat shape such as an ellipse, an oval, a rectangle or the like.

Landscapes

  • 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)
EP19980112413 1997-07-04 1998-07-03 Wärmetauscher mit Doppelrohrkonstruktion Expired - Lifetime EP0889299B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP179273/97 1997-07-04
JP17927397 1997-07-04
JP17927397A JPH1123185A (ja) 1997-07-04 1997-07-04 二重管式熱交換器

Publications (3)

Publication Number Publication Date
EP0889299A2 true EP0889299A2 (de) 1999-01-07
EP0889299A3 EP0889299A3 (de) 1999-02-03
EP0889299B1 EP0889299B1 (de) 2002-10-02

Family

ID=16062966

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980112413 Expired - Lifetime EP0889299B1 (de) 1997-07-04 1998-07-03 Wärmetauscher mit Doppelrohrkonstruktion

Country Status (3)

Country Link
EP (1) EP0889299B1 (de)
JP (1) JPH1123185A (de)
DE (1) DE69808387D1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1715280A1 (de) * 2005-04-21 2006-10-25 Delphi Technologies, Inc. Sammelrohr für Aluminium-Radiatoren mit nietartiger Befestigungskonstruktion
EP2402694A1 (de) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Kondensator insbesondere für ein Klimaanlagensystem eines Kraftfahrzeugs, und mit einem solchen Kondensator ausgestatteter Wärmetauscher
FR2962200A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Unite d'echange d'un faisceau d'echange d'un echangeur de chaleur de, faisceau d'echange et echangeur de chaleur
FR2962205A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Boitier collecteur d'un echangeur de chaleur conduisant un fluide caloporteur et comprenant un faisceau d'echange d'un fluide refrigerant
US8936320B2 (en) 2008-06-17 2015-01-20 Pinnacle Potash International, Ltd. Method and system for solution mining

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7357208B2 (ja) * 2019-11-26 2023-10-06 株式会社ノーリツ 熱交換器およびこれを備えた温水装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5846969A (ja) 1981-09-14 1983-03-18 株式会社初田製作所 消火用の濃厚液
JPS5971071A (ja) 1982-10-15 1984-04-21 Canon Inc 定着装置
JPH03233129A (ja) 1990-02-06 1991-10-17 Showa Alum Corp オイルクーラ付きラジエータ

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1167318A (en) * 1966-11-08 1969-10-15 Marston Radiators Ltd Heat Exchange Unit
FR2521277B1 (fr) * 1982-02-08 1987-07-24 Valeo Echangeur de chaleur, en particulier pour un circuit de refroidissement de moteur a combustion interne
US5067561A (en) * 1990-11-30 1991-11-26 General Motors Corporation Radiator tank oil cooler
US5186245A (en) * 1992-04-06 1993-02-16 General Motors Corporation Flow control baffle for radiator in-tank cooler
JPH08177493A (ja) * 1994-12-21 1996-07-09 Nippondenso Co Ltd 熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5846969A (ja) 1981-09-14 1983-03-18 株式会社初田製作所 消火用の濃厚液
JPS5971071A (ja) 1982-10-15 1984-04-21 Canon Inc 定着装置
JPH03233129A (ja) 1990-02-06 1991-10-17 Showa Alum Corp オイルクーラ付きラジエータ

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1715280A1 (de) * 2005-04-21 2006-10-25 Delphi Technologies, Inc. Sammelrohr für Aluminium-Radiatoren mit nietartiger Befestigungskonstruktion
US7188664B2 (en) 2005-04-21 2007-03-13 Delphi Technologies, Inc. Aluminum radiator tank with oil cooler clinch fitting
US8936320B2 (en) 2008-06-17 2015-01-20 Pinnacle Potash International, Ltd. Method and system for solution mining
EP2402694A1 (de) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Kondensator insbesondere für ein Klimaanlagensystem eines Kraftfahrzeugs, und mit einem solchen Kondensator ausgestatteter Wärmetauscher
FR2962200A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Unite d'echange d'un faisceau d'echange d'un echangeur de chaleur de, faisceau d'echange et echangeur de chaleur
FR2962205A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Boitier collecteur d'un echangeur de chaleur conduisant un fluide caloporteur et comprenant un faisceau d'echange d'un fluide refrigerant
FR2962199A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile.

Also Published As

Publication number Publication date
EP0889299B1 (de) 2002-10-02
JPH1123185A (ja) 1999-01-26
EP0889299A3 (de) 1999-02-03
DE69808387D1 (de) 2002-11-07

Similar Documents

Publication Publication Date Title
US5078206A (en) Tube and fin circular heat exchanger
JP3988889B2 (ja) 自動車用熱交換器
US7191824B2 (en) Tubular charge air cooler
US6289981B1 (en) Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes
US20080185130A1 (en) Heat exchanger with extruded cooling tubes
US4936379A (en) Condenser for use in a car cooling system
CA2272804C (en) Heat exchanger with dimpled bypass channel
US20080173428A1 (en) Automatic transmission fluid cooler and associated method
JPH10206074A (ja) 一体型熱交換器
US9151547B2 (en) Heat exchanger utilizing chambers with sub-chambers having respective medium directing inserts coupled therein
US5318111A (en) Integral baffle assembly for parallel flow heat exchanger
EP0889299B1 (de) Wärmetauscher mit Doppelrohrkonstruktion
EP0857935A2 (de) Kombinierte Wärmetauscher
KR101663382B1 (ko) 열전달 장치
JPS6317393A (ja) 熱交換器
JP2006138538A (ja) 偏平伝熱管および該伝熱管を組込んでなる多管式熱交換器並びに多管式熱交換型ｅｇｒガス冷却装置
JPH05215482A (ja) 熱交換器
KR100723810B1 (ko) 열교환기
KR200372348Y1 (ko) 오일쿨러내장형라디에이터
JPS63217197A (ja) 熱交換器
RU2047076C1 (ru) Теплообменник
JP2000220982A (ja) 熱交換器
KR100332300B1 (ko) 오일냉각장치
KR20200077003A (ko) 열교환기
KR0129787Y1 (ko) 열교환기

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 19990429

AKX Designation fees paid

Free format text: DE FR GB

17Q First examination report despatched

Effective date: 20010213

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20021002

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 69808387

Country of ref document: DE

Date of ref document: 20021107

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030703

EN Fr: translation not filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030703

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20030703