EP0714008A2 - Echangeur de chaleur avec boîte à eau - Google Patents

Echangeur de chaleur avec boîte à eau Download PDF

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Publication number
EP0714008A2
EP0714008A2 EP95117762A EP95117762A EP0714008A2 EP 0714008 A2 EP0714008 A2 EP 0714008A2 EP 95117762 A EP95117762 A EP 95117762A EP 95117762 A EP95117762 A EP 95117762A EP 0714008 A2 EP0714008 A2 EP 0714008A2
Authority
EP
European Patent Office
Prior art keywords
slot
tube
walls
heat exchanger
collecting
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.)
Withdrawn
Application number
EP95117762A
Other languages
German (de)
English (en)
Other versions
EP0714008A3 (fr
Inventor
Herbert Dr. Damsohn
Wolfgang Gerlach
Walter Dipl.-Ing. Wolf
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
Publication of EP0714008A2 publication Critical patent/EP0714008A2/fr
Publication of EP0714008A3 publication Critical patent/EP0714008A3/xx
Withdrawn legal-status Critical Current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
    • 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
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • 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
    • F28F9/0243—Header boxes having a circular cross-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
    • 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
    • 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
    • F28D2021/0084—Condensers

Definitions

  • the invention relates to a heat exchanger with a header pipe according to the preamble of claim 1 and a method for producing a slot in such a header pipe according to the preamble of claim 12.
  • Such a heat exchanger is known from US Pat. No. 5,265,672, which shows two parallel manifolds, between which flat tubes through which fluid flows are arranged.
  • the flat tubes each open into a slot in the header, which is arranged in a plane approximately perpendicular to the longitudinal axis of the header.
  • the heat exchanger fluid flows through the flat tubes to give off the heat, the collecting tubes serving as a connection between two adjacent flat tubes.
  • reinforced retaining rails are arranged, which are guided through the slots in the collecting tubes and axially close the interior of the collecting tube as a partition.
  • the slots are delimited on their narrow sides by slot walls of the collecting tube arranged parallel to one another, the slot walls extending approximately along a tangent to a circle around the tube longitudinal axis.
  • the slot length determined by the spacing of the slot walls corresponds to the inside diameter of the collecting tube, in order to ensure that a flat tube or a closure element such as a partition wall can be inserted into the slot without problems.
  • the introduced Component is encompassed over the length of the slot walls arranged parallel to one another on the narrow sides of the slot and can be firmly connected to the collecting tube, for example by soldering.
  • the diaphragm walls become ever thinner and border approximately at an acute angle to the outer jacket of the collector pipe.
  • the slotted walls can no longer provide the required stability and the material can tear, which can be caused by comparatively small forces which can arise, for example, when a flat tube is inserted into the slit.
  • a tight and pressure-resistant connection is not ensured, so that the entire collecting pipe must be replaced.
  • the invention has for its object to provide a heat exchanger with a manifold with which a stable and tight connection of a laterally opening component is guaranteed with the smallest possible diameter and high pressure resistance; in addition, a method is to be specified with which a header pipe for such a heat exchanger can be manufactured.
  • the diaphragm walls are identical to the deformed walls of the collecting tube, they have a constant wall thickness over their entire wall length.
  • the diaphragm walls are therefore made considerably more stable than in the prior art, as a result of which the risk of material failure is substantially reduced.
  • Such a slot can be produced according to the invention by first introducing a slot with a slot length smaller than the inside diameter of the collecting tube, for example by sawing, milling, punching or the like, and in a second step the collecting tube walls delimiting the narrow sides of the slot with the aid of a slot die enlarged and calibrated to the final slot length.
  • Such slots are quick and easy to manufacture in terms of production technology.
  • the widened diaphragm walls expediently extend at least from a central plane through the collector tube to an intersection of the tangent to the diaphragm wall with the outer jacket of the collector tube.
  • a slot is made in the header, the slot length of which is reduced by at least twice the wall thickness of the header compared to the inside diameter of the header. It is thereby ensured that the component inserted into the slot is held on its narrow sides by the slot walls over a minimum length, and the component is securely positioned due to the larger connecting surface held and a pressure-tight connection can be made.
  • a circumferential groove forming the slot bottom is formed on the inner jacket of the collecting tube in the area of the slot plane, the bottom of the groove being at a greater distance from the longitudinal axis than the inner tube jacket.
  • a flat tube or a partition can be inserted, which has a greater width than the inner diameter of the header.
  • the widened groove can be produced with the aid of the slot punch, which is sunk into the tube interior and presses the slot bottom radially outwards.
  • the groove runs in a semicircle concentric to the inner jacket of the header; the end sections of the groove adjoining the semicircle are advantageously formed by the slot walls.
  • the distance of the groove base of the widened groove to the inner tube shell in the direction of the slot bottom is continuously reduced, so that the side of the inner jacket which is at a maximum distance from the slot opening is not or only slightly widened.
  • the diaphragm walls are offset radially outwards with respect to the inner tube shell, so that a shoulder is formed between the diaphragm walls and the inner tube shell, by which the insertion depth of the component to be inserted laterally into the collecting tube is limited.
  • the collecting tube can have a shape that deviates from the circular shape, in particular one with respect to a longitudinal cross-sectional axis have symmetrical cross section.
  • the cross section is expediently formed from two circular sections with different radius, which are connected to one another by straight wall sections aligned approximately parallel to the longitudinal axis of the cross section.
  • the slot opening can be introduced on the circular section with a larger radius, the slot walls extending on the straight wall sections. The insertion depth is limited by the circular section with a smaller radius opposite the slot opening.
  • Fig. 1 shows a section transverse to the longitudinal axis 5 of a one-piece manifold 2, which is used in a heat exchanger 1, not shown.
  • the collecting tube 2 has a slot 3 which lies in a plane 4 approximately perpendicular to the longitudinal axis 5 of the collecting tube.
  • a plurality of slots arranged in parallel are introduced over the axial length of the header pipe, into which flat tubes can be inserted, through which heat exchanger fluid flows.
  • the heat exchanger fluid of a flat tube flows into the interior of the header tube and is deflected into the adjacent flat tube.
  • partition walls can be inserted into further slots in the header, which tightly seal the header cross section.
  • the narrow sides of the slot 3 are delimited by slot walls 8a, 8b of the collecting tube 2 which are arranged parallel to one another and extend approximately along a tangent 9a, 9b to one Circle 10 lying in the tube inner jacket 14 extends around the tube longitudinal axis 5.
  • the slot length a is determined by the distance between the slot walls 8a, 8b and corresponds to the inner diameter d of the header tube 2.
  • the slotted walls 8a, 8b are formed from the deformed walls 11a, 11b of the header tube 2 and have a constant wall thickness s over their wall length l.
  • the outer sides 12a, 12b of the slot walls run largely outside the outer jacket 13 of the collecting tube 2.
  • a flat tube with the same cross-section as the cross-section of the slot can be inserted into the slot 3, the insertion depth being limited by a tube center plane 15 which is between the semicircular slot bottom 16 and the adjoining diaphragm walls 8a, 8b.
  • a partition is inserted into the slot, which abuts the inner jacket 14 of the collecting tube in the area of the slot.
  • Flat tubes and partitions can be firmly anchored in the slot by soldering.
  • the wall thickness of the diaphragm walls 8a, 8b which in the exemplary embodiment according to FIG. 1 is identical to the wall thickness s of the collecting tube, is constant over the entire length l of the diaphragm walls; the diaphragm walls can therefore also absorb high transverse loads in the area of their axially open ends without the risk of material breakage.
  • the risk of cracking when the diaphragm walls are widened to their final dimension a is also significantly reduced.
  • the burst pressure of such a trained The collecting tube can be up to 120 bar and possibly even more.
  • FIG. 2 shows a top view of the collecting tube 2 in the area of the slot 3.
  • the slot walls 8a, 8b can be designed in the form of a slot groove 25 in the shape of a part circle, into which the correspondingly shaped flat tube or the partition wall can be inserted.
  • the slot groove 25 allows a secure insertion of the component to be inserted along the slot plane 4.
  • the slot walls 8a, 8b advantageously extend at least from the tube center plane 15 to an intersection A or B of the tangents 9a and 9b with the outer jacket 13 of the collecting tube, in order to ensure that the flat tube or the partition wall is held in the slot 3 over a minimum length is.
  • a further advantageous embodiment of the slot in the header is shown.
  • a circumferential groove 17 forming the slot bottom 16 is formed in the area of the slot plane 4, the bottom 18 of which groove has a greater distance c to the tube longitudinal axis 5 than the inner tube jacket 14.
  • the groove bottom 18 forms a concentric circle with the inner jacket 14 and is offset radially outwards from the inner jacket by the amount of the groove depth t.
  • the axial end sections 19a, 19b of the groove 17 are expediently formed by the slot walls 8a, 8b, the semicircular groove 17 merging into the tangential slot groove 25.
  • a partition wall can advantageously be inserted into the groove 17 and is securely guided in the slot 3 down to the slot bottom 16.
  • the slot length a is increased by twice the groove depth t compared to the inner pipe diameter d.
  • 5a and 5b also has a radially widened groove 17 lying in the slot plane 4, the groove depth t between the groove base 18 and the inner tube jacket 14 decreasing with increasing distance from the slot opening 20 to the slot bottom 16. As shown in FIG. 5b, the groove depth t then decrease completely to zero, that is to say that the groove base 18 merges into the inner jacket 14; 5a, the groove depth t on the slot bottom 16 can have a residual dimension.
  • the slot length a is determined by the distance between the slot walls 8a, 8b.
  • FIG. 6 shows a further expedient embodiment of the slot 3 in the collecting tube 2.
  • the slotted walls 8a, 8b are offset radially outwards by an amount f with respect to the inner tube jacket 14; a shoulder 21a, 21b is formed between the inner tube jacket 14 and the slot walls, which advantageously slopes away as a ramp-shaped transition between the slot wall and the inner jacket.
  • the ramp-shaped design of the shoulder keeps material stresses low, which can arise due to the slot enlargement in the tube wall of the collecting tube.
  • the flat tube inserted into the slot 3 can be supported on the shoulder 21a, 21b, as a result of which a predetermined insertion depth is determined.
  • the shoulder 21a, 21b also prevents liquid items to be soldered from flowing between the slotted walls 8a, 8b and the narrow sides of the flat tube during the soldering process and from entering the interior of the collecting tube 2.
  • the slot length a is in this design by twice the amount of the offset f between the inner jacket and diaphragm wall expanded compared to the inner pipe diameter d.
  • the cross section is advantageously symmetrical with respect to a cross-sectional longitudinal axis 22, FIG. 7. It is composed of two circular sections 27, 28 with different radius r, R, which are connected to one another by two wall sections 26a, 26b aligned approximately parallel to the cross-sectional longitudinal axis 22.
  • the slot opening 20 is expediently introduced on the circular section 28 with a larger radius R, the slot walls 8a, 8b extending on the straight wall sections 26a, 26b and, in particular, being offset radially outward by the amount f with respect to the inner pipe jacket 14.
  • the slot length a is therefore expanded by twice the amount f compared to the inner width of the header pipe - measured along the transverse axis 23.
  • the slot walls 8a, 8b extend on both sides of the transverse axis 23.
  • This design of the header has the advantage that the overall height h of the header 2 can be varied depending on the length of the wall sections 26a, 26b. If the wall sections 26a, 26b completely disappear, the overall height h is reduced compared to a round pipe cross-section with the same cross-sectional area of the header pipe.
  • the circular section 28 with an enlarged radius R rests in the form of a slightly rounded cover on both sides of the slot opening 20, as a result of which the overall height h is reduced.
  • FIG. 8 shows the collecting tube according to FIG. 7 with a flat tube 6 inserted into the slot 3, which as a multi-chamber profile with several parallel individual channels 29 is formed.
  • the narrow sides of the flat tube 6 are slightly rounded and are guided in the slot grooves 25 of the slot walls 8a, 8b.
  • FIG. 9 shows a further perspective illustration of the collecting pipe 2 from FIG. 7, a larger axial section of the collecting pipe being shown.
  • a plurality of parallel slots 3, which are arranged at approximately the same distance, are introduced into the collecting tube and, as described above, have either slot walls offset radially outwards or a radially widened groove.
  • partitions 7a and 7b can be inserted into the slots, which have a contour adapted to the interior of the tube in the area of the slot.
  • the partition 7a is designed as a plate, the thickness of which corresponds approximately to the slot width and which has an approximately rectangular shape with a semicircular end section; the partition 7a can be inserted into a slot designed according to FIGS. 3, 5a or 5b.
  • the partition 7b also has an approximately rectangular shape, the end section being designed as a circular section with a smaller diameter than the rectangle width. This results in a shoulder in the transition region of the circular section to the rectangle, which is complementary to the shoulder 21a, 21b of the slot according to FIG. 6 or FIG. 7.
  • Non-circular cross-sectional shape has the same non-circular cross-sectional shape over the entire section shown; According to an embodiment which is not shown, it can also be expedient to make only individual segments of the collecting tube out of round in the region of the slots and to manufacture the remaining collecting tube sections in a circular manner.
  • the Non-circular sections can be produced by reshaping.
  • FIG. 10 shows a side view of the illustration according to FIG. 9, a further slot 3 ′ being arranged on the collecting tube 2, which is located on the opposite side of a previous slot 3.
  • a mutual arrangement of the slots on opposite sides of the header can be particularly useful in the case that flat tubes are inserted into the slots on a header side and partition walls are inserted into the slots on the opposite side.
  • FIG. 11a shows a section through an undeformed collecting tube 2, into which a slot 3 is introduced in FIG. 11b by sawing, milling, punching or the like.
  • the slot 3 introduced in a first step has a smaller slot length e than the inner tube diameter d.
  • the collecting tube therefore has a circular section shape in the region of the slot, which extends beyond a semicircular shape.
  • the manifold walls 11a, 11b delimiting the narrow sides of the slot 3 are enlarged and calibrated to the final slot length a by means of a slot punch 24, see FIG. 11c.
  • the manifold walls 11a, 11b form the slot walls 8a, 8b arranged parallel to one another.
  • the slot length e introduced in the first step is reduced by at least twice the wall thickness s of the collecting pipe 2 compared to the inside pipe diameter d. This ensures that when the manifold walls are enlarged to the final dimension End region of the slit walls 8a, 8b lies outside the outer jacket 13 of the collecting tube 2.
  • the slot walls 8a, 8b can be displaced radially outward so far that the slot length a determined by the spacing of the slot walls 8a, 8b is greater than the inner tube diameter d, see FIGS. 6 and 7 in this regard 24 is constructed similarly to the partition 7b described above for this purpose, it consists of an approximately rectangular base body 30, which is followed by an approximately semicircular end section 31 adapted to the pipe cross section.
  • the end section 31 advantageously has a smaller diameter than the rectangular base body 30 of the slot die 24, the diameter advantageously being reduced by twice the wall thickness s.
  • an intermediate section 32 can be inserted between the base body 30 and the end section 31 into the slot punch 24, which has approximately the length l of the slot walls 8 a, 8 b and has the same width as the diameter of the end section 31.
  • the end section 31 can also connect directly to the base body 30 via an oblique transition 33;
  • a slot punch 24 can advantageously be used to produce the radially outwardly offset slot walls 8a, 8b of FIGS. 6 and 7, the end section 31 having the same diameter as the inside diameter of the collecting tube and being completely sunk into the inside of the collecting tube.
  • the device and the method according to the invention are expediently used in all-metal heat exchangers such as oil coolers, charge air coolers, in radiators and flat tube condensers, regardless of whether they are single-flow or multi-flow.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP95117762A 1994-11-25 1995-11-11 Echangeur de chaleur avec boîte à eau Withdrawn EP0714008A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4442040 1994-11-25
DE4442040A DE4442040A1 (de) 1994-11-25 1994-11-25 Wärmetauscher mit einem Sammelrohr

Publications (2)

Publication Number Publication Date
EP0714008A2 true EP0714008A2 (fr) 1996-05-29
EP0714008A3 EP0714008A3 (fr) 1996-06-12

Family

ID=6534170

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95117762A Withdrawn EP0714008A2 (fr) 1994-11-25 1995-11-11 Echangeur de chaleur avec boîte à eau

Country Status (4)

Country Link
US (1) US5743329A (fr)
EP (1) EP0714008A2 (fr)
JP (1) JPH08226787A (fr)
DE (1) DE4442040A1 (fr)

Cited By (5)

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FR2793014A1 (fr) * 1999-04-28 2000-11-03 Valeo Thermique Moteur Sa Echangeur de chaleur pour fluide sous pression elevee
EP1515109A2 (fr) * 2003-09-10 2005-03-16 Delphi Technologies, Inc. Echangeur de chaleur et procédé de fabrication d'un collecteur d'un échangeur de chaleur
EP1953490A2 (fr) 2007-02-03 2008-08-06 Behr GmbH & Co. KG Chambre collectrice et échangeur de chaleur doté d'une telle chambre collectrice
WO2008151680A1 (fr) * 2007-06-15 2008-12-18 Modine Manufacturing Company Échangeur de chaleur
EP3923399A4 (fr) * 2019-03-18 2022-04-20 Contemporary Amperex Technology Co., Limited Bloc-batterie et système de refroidissement associé

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JPH11226685A (ja) * 1998-02-16 1999-08-24 Denso Corp 熱交換器およびヘッダタンクの製造方法
DE19911334A1 (de) 1999-03-15 2000-09-21 Behr Gmbh & Co Sammelrohr für einen Wärmeübertrager und Herstellungsverfahren hierfür
US6289980B1 (en) 1999-12-16 2001-09-18 Norsk Hydro, A.S. Baffle for heat exchanger manifold
JP2002048488A (ja) * 2000-08-04 2002-02-15 Showa Denko Kk 熱交換器
US6854511B2 (en) * 2000-08-04 2005-02-15 Showa Denko K.K. Heat exchanger
WO2002035170A1 (fr) * 2000-10-25 2002-05-02 Showa Denko K.K. Echangeur thermique
DE10103176B4 (de) * 2001-01-22 2010-06-02 Behr Gmbh & Co. Kg Verfahren zum Einbringen von Flachrohreinsteckschlitzen in ein Sammelrohr
JP4107051B2 (ja) * 2002-02-19 2008-06-25 株式会社デンソー 熱交換器
KR20040037683A (ko) * 2002-10-29 2004-05-07 엘지전자 주식회사 열교환기의 냉매 균일 분배 장치
DE60331342D1 (de) * 2002-11-15 2010-04-01 Zexel Valeo Climate Contr Corp Sammelkasten für wärmetauscher
DE102004007686A1 (de) * 2004-02-16 2005-09-01 Behr Gmbh & Co. Kg Verfahren zur Herstellung von Durchzügen in Sammelrohren und Vorrichtung zur Durchführung des Verfahrens
BRPI0519904A2 (pt) * 2005-02-02 2009-09-08 Carrier Corp trocador de calor
MX2007009253A (es) * 2005-02-02 2007-09-04 Carrier Corp Colector de termointercambiador de minicanal.
KR20070111456A (ko) * 2005-02-02 2007-11-21 캐리어 코포레이션 헤더 내에서의 유체 팽창에 의한 열교환기
ATE498812T1 (de) * 2005-02-02 2011-03-15 Carrier Corp Wärmetauscher mit perforierter platte in endkammer
MX2007009255A (es) * 2005-02-02 2007-09-04 Carrier Corp Termointercambiador de tubo plano de canal multiple.
ATE507452T1 (de) * 2005-02-02 2011-05-15 Carrier Corp Wärmetauscher mit mehrstufiger flüssigkeitsausdehnung im kollektor
ATE483145T1 (de) * 2005-12-10 2010-10-15 Delphi Tech Inc Wärmetauscher und verfahren zu deren herstellung
US20070204981A1 (en) * 2006-03-02 2007-09-06 Barnes Terry W Modular manifolds for heat exchangers
US20070204982A1 (en) * 2006-03-02 2007-09-06 Barnes Terry W Manifolds and manifold connections for heat exchangers
ATE510179T1 (de) * 2006-03-15 2011-06-15 Behr France Hambach Sarl Wärmeübertrager, insbesondere kondensator für klimaanlagen, insbosondere von kraftfahrzeugen
US9328966B2 (en) * 2007-11-01 2016-05-03 Modine Manufacturing Company Heat exchanger with a baffle reinforcement member
US9470461B2 (en) * 2007-11-01 2016-10-18 Modine Manufacturing Company Heat exchanger with a tank reinforcement member
DE102009049483A1 (de) * 2009-10-15 2011-04-21 Modine Manufacturing Co., Racine Wärmetauscher und Dichtungsanordnung dafür
JP6394202B2 (ja) * 2013-11-27 2018-09-26 株式会社デンソー 熱交換器
EP2960609B1 (fr) * 2014-06-26 2022-10-05 Valeo Autosystemy SP. Z.O.O. Collecteur, en particulier pour une utilisation dans un système de refroidissement d'un refroidisseur
JP5850118B1 (ja) * 2014-09-30 2016-02-03 ダイキン工業株式会社 熱交換器および空気調和装置
DE102015104180B4 (de) * 2015-03-20 2023-10-05 Halla Visteon Climate Control Corporation Vorrichtung für einen Wärmeübertrager zum Sammeln und Verteilen eines Wärmeträgerfluids

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2793014A1 (fr) * 1999-04-28 2000-11-03 Valeo Thermique Moteur Sa Echangeur de chaleur pour fluide sous pression elevee
WO2000066964A1 (fr) * 1999-04-28 2000-11-09 Valeo Thermique Moteur Echangeur de chaleur pour fluide sous pression elevee
US6564863B1 (en) 1999-04-28 2003-05-20 Valeo Thermique Moteur Concentrated or dilutable solutions or dispersions, preparation method and uses
EP1515109A2 (fr) * 2003-09-10 2005-03-16 Delphi Technologies, Inc. Echangeur de chaleur et procédé de fabrication d'un collecteur d'un échangeur de chaleur
EP1515109A3 (fr) * 2003-09-10 2009-05-06 Delphi Technologies, Inc. Echangeur de chaleur et procédé de fabrication d'un collecteur d'un échangeur de chaleur
EP1953490A2 (fr) 2007-02-03 2008-08-06 Behr GmbH & Co. KG Chambre collectrice et échangeur de chaleur doté d'une telle chambre collectrice
DE102007005392A1 (de) 2007-02-03 2008-08-07 Behr Gmbh & Co. Kg Sammelkasten und Wärmeübertrager mit einem solchen Sammelkasten
EP1953490A3 (fr) * 2007-02-03 2013-07-03 Behr GmbH & Co. KG Chambre collectrice et échangeur de chaleur doté d'une telle chambre collectrice
WO2008151680A1 (fr) * 2007-06-15 2008-12-18 Modine Manufacturing Company Échangeur de chaleur
DE102007027706A1 (de) * 2007-06-15 2008-12-18 Modine Manufacturing Co., Racine Wärmetauscher
EP3923399A4 (fr) * 2019-03-18 2022-04-20 Contemporary Amperex Technology Co., Limited Bloc-batterie et système de refroidissement associé

Also Published As

Publication number Publication date
EP0714008A3 (fr) 1996-06-12
DE4442040A1 (de) 1996-05-30
JPH08226787A (ja) 1996-09-03
US5743329A (en) 1998-04-28

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