EP1972879B1 - Échangeur de chaleur, en particulier radiateur pour liquide de refroidissement dans un véhicule automobile - Google Patents

Échangeur de chaleur, en particulier radiateur pour liquide de refroidissement dans un véhicule automobile Download PDF

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Publication number
EP1972879B1
EP1972879B1 EP08004214.6A EP08004214A EP1972879B1 EP 1972879 B1 EP1972879 B1 EP 1972879B1 EP 08004214 A EP08004214 A EP 08004214A EP 1972879 B1 EP1972879 B1 EP 1972879B1
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EP
European Patent Office
Prior art keywords
gutter
heat exchanger
wall thickness
wall
tubes
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.)
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Application number
EP08004214.6A
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German (de)
English (en)
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EP1972879A2 (fr
EP1972879A3 (fr
Inventor
Haymo BRÖDER
Florin Moldovan
Hicham Rouhana
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
Mahle Behr GmbH and Co KG
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Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP1972879A2 publication Critical patent/EP1972879A2/fr
Publication of EP1972879A3 publication Critical patent/EP1972879A3/fr
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Publication of EP1972879B1 publication Critical patent/EP1972879B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F9/0219—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
    • F28F9/0226—Header boxes formed by sealing end plates into covers with resilient gaskets

Definitions

  • the invention relates to a heat exchanger, in particular a coolant radiator according to the preamble of claim 1.
  • heat exchangers of motor vehicles for. B. coolant radiator, refrigerant condensers or intercooler air side by side to arrange, in a preassembled module, which is also referred to as a cooling module.
  • the cooling module is arranged in the vehicle in the front region of the engine compartment, where in particular, seen in the air flow direction, relatively little space is available.
  • the individual heat exchangers must therefore be arranged as close as possible one behind the other - but this is not always possible - due to the different design of the individual heat exchanger. For example, results in mechanically joined heat exchangers such asdeffenksselem a so-called supernatant of the coolant boxes with respect to the front sides of the radiator block, which is constructed from pipes and ribs.
  • the coolant boxes thus have a greater depth in the direction of air flow than the block of the coolant cooler, for which reason the distance to the adjacent heat exchanger is determined by the projection of the box relative to the face of the block. This distance thus increases the depth of a cooling module and is not necessary for thermodynamic reasons.
  • the known coolers have a block consisting of tubes and ribs, which can be mechanically joined or soldered.
  • the tubes of this block each open into a collection or distribution box, also called coolant box, which is joined from a metallic bottom and a plastic lid with the interposition of a seal to a sealed container.
  • the bottom has an inner region in which passages for receiving the pipe ends are arranged, which can be connected by mechanical expansion or a solder joint with the passages.
  • the outer portion of the bottom has a circumferential groove in which an elastomeric seal is inserted, which seals the bottom against the 'plastic lid.
  • the connection between bottom and lid is exemplary in the DE 28 52 408 B2 and is referred to as a so-called Wellenschlitzbördelung because slots are arranged in the bottom edge and the bottom edge is wavy deformed.
  • Wellenschlitzbördelung is described, which is characterized by a raised Wasserkastenfuß with upper tool attachment surfaces, so-called locking balconies. At these surfaces grip when connecting lid and bottom closing tools, eg. B. stamp and exert to generate a bias a compressive force on the seal.
  • the supernatant designated X is composed of a series of individual dimensions, where x1 is the distance of the channel from the front side of the block or the tubes is designated. x1 is thus the gap between the face of the block and the wall of the groove. According to the invention, this dimension x1 is reduced to a value of less than 0.5 mm, preferably: 0.1 ⁇ x1 ⁇ 0.5 mm. Thus, the gap between the block and the gutter is reduced to a minimum, so that a joining of the tubes in the ground or its passages is still possible. This results in a first significant contribution to reducing the supernatant and reducing the depth of the heat exchanger.
  • the wall thickness x3 of the outer wall corresponds to the wall thickness of the sheet material for the floor, while the wall thickness x2 of the inner wall is reduced, ie x2 ⁇ x3.
  • the partial dilution of the bottom wall thickness in the region of the inner channel wall results in a further reduction of the projection X.
  • the wall thickness x2 is reduced by 0.2 mm with respect to the wall thickness x3 on the outside. This measure also takes into account the stress of the soil material in these two areas:
  • the outer wall with the wall thickness x3 is due to the flare, z. B.
  • the overall dimension of the supernatant X is also a further measure x4, which relates to the clear width of the circumferential groove. According to a preferred embodiment, this measure is also reduced compared with the prior art, which at the same time necessitates a reduction of the sealing diameter and the width of the cover flange which is received by the groove.
  • the lid also called plastic box or water tank
  • a circumferential flange, too Called Wasserkastenfuß, on which is provided with projections, also called locking balconies, provided.
  • these projections are corresponding to the pipe pitch, ie the distance of the tubes arranged to each other.
  • a projection or locking balcony preferably on the inside of the water box each having a recess for the two tubes is provided, whereby the foot or flange of the lid can be narrowed overall.
  • so-called insertion beads are arranged in the inner bottom region, which extend with their end faces into the region of the circumferential groove on the longitudinal sides of the floor.
  • the entire supernatant X is smaller than 8 mm, preferably equal to or smaller than 6 mm.
  • the overall dimension X of the supernatant is composed of the individual dimensions x1, x2, x3, x4, wherein - as stated above - x1 the distance of the channel from the block, x2 the wall thickness of the inner channel wall, x3 the wall thickness of the outer channel wall and x4 the clear width of the gutter is.
  • these dimensions - without affecting the function of the connection between the bottom and the box - optimized so that a reduction of the supernatant X compared to the prior art results in up to 3 mm.
  • the supernatant thus has a dimension X of about 6 mm. This makes it possible, in particular in the arrangement of the heat exchanger in a cooling module to realize a smaller distance between the end surfaces of adjacent heat exchanger and thus to achieve a gain in space.
  • Fig. 1 shows a cross section through a coolant box 1 of a not fully shown coolant radiator, which is used for cooling an internal combustion engine of a motor vehicle.
  • the coolant radiator 1 is preferably part of a cooling module, not shown, which can be installed in the front engine compartment of a motor vehicle, and is flowed through by ambient air.
  • the coolant box 1 consists of a plastic lid 2, which has an approximately U-shaped cross-section and is mechanically connected to a metallic bottom 3.
  • the bottom 3, also called tube plate has an approximately rectangular floor plan with a circumferential groove-like depression, hereinafter called gutter 4, in which a round cord seal 5 is inserted, whose diameter is designated x6.
  • the cover 2 has a circumferential thickened flange 6, also called foot, which rests on the seal 5 and is inserted into the channel 4.
  • the width of the flange 6 is marked x5.
  • the bottom 3 has an inner, bounded by the channel 4 region 3a, in which passages 7 are formed, which extend over the entire width of the bottom portion 3a and flat tubes 8 (only hinted) record.
  • the flat tubes 8 form with not shown corrugated fins also not shown block, also called network, which is flowed through the secondary side of air.
  • the depth of the block in the air flow direction corresponds approximately to the depth of the flat tube 8.
  • the flat tubes 8 are soldered to the corrugated fins and the ends of the flat tubes 8 with the passages 7 of the bottom 3.
  • the bottom 3 has in its inner region 3a also formed in beads 9 for stiffening.
  • the entire bottom 3 is made of a sheet material, preferably an aluminum sheet by chipless forming.
  • Fig. 2 shows a segment of the lid 2, which is made as a plastic injection molded part.
  • On the outside of the lid 2 and above the flange 6 are projections 10, so-called locking balconies, arranged on which locking tools, not shown, engage in the connection of the bottom 3 and cover 2.
  • a corresponding closing method is in the above-mentioned prior art ( DE 38 41 470 A1 the applicant).
  • 2 recesses 11 are formed on the inside of the lid, in which engage the flat tubes 8, not shown here with their narrow sides. The recesses 11 are thus arranged at a distance of the pipe pitch. Through the recesses 11, the width of the coolant box 1 can be reduced.
  • Fig. 3 shows a segment of the bottom 3 in a view from the side of the block, not shown, ie with a view to the so-called air side of the bottom 3. It can be seen extending transversely to the bottom 3 stiffening beads 9, which are arranged between the passages 7, wherein the Passages have an insertion bevel 7a.
  • the pipes 8 not shown here are therefore introduced from the air side in the passages 7 of the bottom 3.
  • two insertion beads 12 are formed, which reach as far as the groove 4 and appear here as depressions.
  • Fig. 4 shows the ground segment according to Fig. 3 rotated by 180 °, ie looking at the "coolant side" of the bottom 3. It can be seen that the passages 7 towards the coolant side (in the drawing above) from the bottom area 3a are formed. In the central region (viewed in the longitudinal direction of the bottom 3), the two insertion beads 12, here raised, can be seen.
  • the two Ein Industriessicken 12 extend to the inner wall 4a of the channel 4 and have the function to expand the lid 2 and its flange 6 when inserted into the channel 4 or to spread. Due to the injection process in the manufacture of the lid 2, it may happen that the inside width of the lid 2 is reduced, the lid 2 is "collapsed". So that during assembly ie during the closing process of the lid 2 and bottom 3 no clamping occurs, the insertion of the lid 2 is facilitated by the two Ein Industriessicken 12 in the trough 4.
  • Fig. 5 shows a cross section through the bottom 3 in the region of the channel 4 and the passage 7.
  • the flat tube 8 has a pipe end 8a, which is received by the passage 7 and materially connected to the passage 7.
  • the channel 4 is bounded by the inner wall 4a with the wall thickness x2 and the outer wall 4b with the wall thickness x3, wherein a clear width of the dimension x4 is left between the wall 4a and the wall 4b.
  • a gap 13 is left, which is marked with the dimension x1.
  • the sum of the dimensions x1, x2, x3, x4 gives the total dimension X, which characterizes the so-called projection of the coolant box 1 or the bottom 3 relative to the block of the coolant radiator, wherein for the front side of the block here the tube 8 is representative.
  • the cut here narrow side of the flat tube 8 lies in the end face of the block.
  • the illustrated dimensions x1 to x4 are optimized in the manner, ie, substantially reduced, such that the overall dimension X, that is to say the supernatant, becomes as small as possible.
  • the dimension x1 for the gap 13 is reduced over the prior art and has a range of 0.1 to 0.5 mm.
  • the dimension x4, ie the inside width of the channel 4 has been reduced by 0.5 mm compared to the prior art.
  • the wall thickness x2 of the inner wall 4a has been reduced by 0.1 to 0.3 mm compared to the wall thickness x3 of the outer wall 4b, ie x2 ⁇ x3 - 0.2.
  • the wall thickness x3 of the outer wall 4b corresponds to the wall thickness of the sheet material for the bottom 3, while the inner wall 4a thus has a smaller, on average 0.2 mm smaller wall thickness, resulting in the production of the bottom 3, for example by stretching the material can be achieved.
  • the reduction of the Flanschureses x5 was also possible due to the arrangement of the recesses 11 on the inside of the lid 2.
  • the dimensions x1, x2, x4 are reduced compared to the prior art, resulting in a total reduction for the supernatant X - due to the inventive measures, the supernatant X could be reduced to about 6 mm.
  • the coolant radiator 1 thus has a bilateral floor overhang of a total of about 12 mm.
  • Fig. 6 shows a further illustration of a section of the bottom 3 with a circumferential edge strip 13, which corresponds to the outer wall 4b of the channel 4 in the preceding figures. From the skirt 13 slots or slots 14 are punched out, so that the bottom 3 by a so-called Wellenschlitzbördelung - as described in the aforementioned prior art - can be connected to the flange 4 of the lid 2.

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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)

Claims (7)

  1. Echangeur de chaleur, en particulier radiateur à liquide de refroidissement, de préférence pour des véhicules automobiles, ledit échangeur de chaleur présentant
    - un bloc comprenant des tubes (8) et en particulier des ailettes, ledit bloc ayant au moins une face frontale,
    - un fond (3) présentant des passages (7) servant au logement des tubes (8) et une rigole périphérique (4) servant au logement d'un joint d'étanchéité en élastomère (5) et / ou d'un couvercle (2),
    - un couvercle (2) fabriqué de préférence en matière plastique, couvercle qui est assemblé avec le fond (3), via le joint d'étanchéité en élastomère (5), l'assemblage étant réalisé mécaniquement, en particulier par frottement ou par complémentarité de forme et / ou par continuité de matière, en particulier réalisé par brasage ou par soudage,
    - où le fond (3) présente au moins un bord extérieur (4b) qui forme, par rapport à la face frontale au moins au nombre de un, une partie en saillie ayant une dimension totale X qui comprend plusieurs dimensions individuelles (x1 - x4),
    - où une première dimension individuelle (x1) concerne la distance comprise entre le bloc ou les tubes (8), et la rigole (4, 4a),
    - une deuxième dimension individuelle (x2) concerne l'épaisseur de paroi de la paroi intérieure de la rigole (4),
    - une troisième dimension individuelle (x3) concerne l'épaisseur de paroi de la paroi extérieure de la rigole (4),
    - et une quatrième dimension individuelle (x4) concerne la largeur intérieure de la rigole (4),
    où la première dimension individuelle (x1), qui concerne la distance comprise entre le bloc ou les tubes (8), et la rigole (4, 4a), est égale ou inférieure à 0,5 mm (x1 ≤ 0,5 mm), et où x1 ≥ 0,1 mm, caractérisé en ce que la rigole (4) présente une paroi extérieure (4b) ayant l'épaisseur de paroi x3, ainsi qu'une paroi intérieure (4a) ayant l'épaisseur de paroi x2, et en ce que x2 est inférieure à x3 (x2 < x3).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que l'épaisseur de paroi x2 est de 0,2 mm inférieure à l'épaisseur de paroi x3 (x2 = x3 - 0,2 mm).
  3. Echangeur de chaleur selon l'une des revendications 1 ou 2, caractérisé en ce que le couvercle (2) présente une bride périphérique (6) ayant des parties saillantes (10) pour des outils de fermeture, et en ce que des évidements (11) se trouvant sur le côté intérieur du couvercle (2) sont disposés dans la zone des passages (7).
  4. Echangeur de chaleur selon la revendication 3, caractérisé en ce que les tubes (8) présentent une répartition tubulaire (t), et en ce que les parties saillantes (10) et les évidements (11) sont disposés de façon correspondant à la répartition tubulaire (t).
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le fond (3) présente une zone intérieure (3a) délimitée par la rigole (4), ladite zone intérieure ayant des grands côtés qui se font face, et en ce que des moulures d'introduction (12), disposées dans la zone des grands côtés, sont formées de préférence à partir de la zone intérieure (3a) du fond (3).
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les moulures d'introduction (12) sont disposées de façon diamétralement opposée l'une par rapport à l'autre et placées entre les passages (7).
  7. Echangeur de chaleur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la partie en saillie (X) est égale à la somme des dimensions individuelles (x1 + x2 + x3 + x4), et en ce que X est < 8 mm, en particulier X est ≤ 6 mm.
EP08004214.6A 2007-03-21 2008-03-07 Échangeur de chaleur, en particulier radiateur pour liquide de refroidissement dans un véhicule automobile Active EP1972879B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007013483A DE102007013483A1 (de) 2007-03-21 2007-03-21 Wärmeübertrager, insbesondere Kühlmittelkühler für Kraftfahrzeuge

Publications (3)

Publication Number Publication Date
EP1972879A2 EP1972879A2 (fr) 2008-09-24
EP1972879A3 EP1972879A3 (fr) 2014-01-08
EP1972879B1 true EP1972879B1 (fr) 2017-11-01

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EP08004214.6A Active EP1972879B1 (fr) 2007-03-21 2008-03-07 Échangeur de chaleur, en particulier radiateur pour liquide de refroidissement dans un véhicule automobile

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EP (1) EP1972879B1 (fr)
DE (1) DE102007013483A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4332492A1 (fr) * 2022-09-01 2024-03-06 Valeo Systemes Thermiques Échangeur de chaleur

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009053090A1 (de) 2009-11-13 2011-06-30 Schaeffler Technologies GmbH & Co. KG, 91074 Käfig für Kegelrollen und Verfahren zu dessen Herstellung
DE102009054020A1 (de) 2009-11-19 2011-05-26 Schaeffler Technologies Gmbh & Co. Kg Käfig für Kegelrollen und Verfahren zu dessen Herstellung
DE102011076225A1 (de) * 2011-05-20 2012-11-22 Behr Gmbh & Co. Kg Wärmetauscher
DE102011085479A1 (de) * 2011-10-28 2013-05-02 Behr Gmbh & Co. Kg Wärmeübertrager
DE202012101622U1 (de) 2012-05-02 2012-06-26 Behr Gmbh & Co. Kg Wärmeübertrager
JP6547576B2 (ja) * 2015-10-15 2019-07-24 株式会社デンソー 熱交換器

Citations (1)

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Publication number Priority date Publication date Assignee Title
US4917182A (en) * 1988-04-01 1990-04-17 General Motors Corporation Sealed tank and header assembly

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE2852409C2 (de) 1978-12-04 1982-10-28 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Elastomere Dichtung für eine Flansch-Klemmverbindung
DE2852408B2 (de) 1978-12-04 1981-10-01 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Klemmverbindung
DE3841470A1 (de) * 1988-12-09 1990-06-13 Sueddeutsche Kuehler Behr Wasserkastenklemmverbindung
DE19515530C2 (de) * 1995-04-27 2001-11-15 Valeo Klimatech Gmbh & Co Kg Wasserkasten eines Wärmetauschers für Kraftfahrzeuge
US6786275B2 (en) * 2002-05-23 2004-09-07 Valeo Engine Cooling Heat exchanger header assembly
DE102004033784A1 (de) * 2004-07-12 2006-02-02 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Ladeluftkühler
FR2875592B1 (fr) * 2004-09-17 2007-02-16 Valeo Thermique Moteur Sas Echangeur de chaleur a boite collectrice sertie et procede d'assemblage
FR2882428B1 (fr) * 2005-02-21 2007-05-18 Valeo Systemes Thermiques Echangeur de chaleur a collecteur ameliore

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4917182A (en) * 1988-04-01 1990-04-17 General Motors Corporation Sealed tank and header assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4332492A1 (fr) * 2022-09-01 2024-03-06 Valeo Systemes Thermiques Échangeur de chaleur

Also Published As

Publication number Publication date
EP1972879A2 (fr) 2008-09-24
EP1972879A3 (fr) 2014-01-08
DE102007013483A1 (de) 2008-09-25

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Inventor name: MOLDOVAN, FLORIN

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