EP1711772B1 - Echangeur de chaleur, en particulier evaporateur a tuyaux plats pour un systeme de climatisation de vehicule a moteur - Google Patents

Echangeur de chaleur, en particulier evaporateur a tuyaux plats pour un systeme de climatisation de vehicule a moteur Download PDF

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Publication number
EP1711772B1
EP1711772B1 EP05707067.4A EP05707067A EP1711772B1 EP 1711772 B1 EP1711772 B1 EP 1711772B1 EP 05707067 A EP05707067 A EP 05707067A EP 1711772 B1 EP1711772 B1 EP 1711772B1
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EP
European Patent Office
Prior art keywords
heat exchanger
collecting tank
rib
flat
opening
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.)
Not-in-force
Application number
EP05707067.4A
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German (de)
English (en)
Other versions
EP1711772A1 (fr
Inventor
Gottfried DÜRR
Klaus FÖRSTER
Michael Kohl
Emil Neumann
Franz Ott
Wolfgang Seewald
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
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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 EP1711772A1 publication Critical patent/EP1711772A1/fr
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Publication of EP1711772B1 publication Critical patent/EP1711772B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • 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
    • 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
    • F28D2021/0085—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2220/00—Closure means, e.g. end caps on header boxes or plugs on 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
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/32—Safety or protection arrangements; Arrangements for preventing malfunction for limiting movements, e.g. stops, locking means
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines

Definitions

  • the invention relates to a heat exchanger, in particular a flat-tube evaporator for a motor vehicle air conditioning system, according to the preamble of claim 1.
  • a heat exchanger is known with at least one collecting box made of sheet metal and in the bottom of the ends of tubes are inserted and the front side each lid, wherein at least one lid is at least in its outer region formed flat and positively positioned in the collecting box.
  • a heat exchanger in particular an evaporator, known, in which a collection box is provided of sheet metal, which is formed from a prepared board.
  • the board consists of an aluminum alloy, which also consists of the flat tubes, the corrugated fins and the side parts as well as the other elements of the heat exchanger. It is first punched out of a plate, which is then shaped so that a flat bottom (substantially planar collection box part) is formed, connected to the longitudinal edges bent parts (tunnel-shaped collection box parts).
  • the bent parts are bent in a radius to a cylindrical surface, of which the longitudinal edges are folded such that they rest parallel to each other and extend substantially perpendicular to the bottom.
  • the Longitudinal edges are provided with a plurality of tabs distributed over their length, which are inserted through recesses of the bottom and are caulked on the outside of the flat tubes facing. In this way, a collection boxes is formed with the two chambers, which has a relatively high strength, before a soldering occurs.
  • the board is solder plated or provided with a solder coating.
  • passages are provided in the bottom, in which the flat tubes are accommodated.
  • the passages are used up close to the adjoining longitudinal edges. This results in a depth for the heat exchanger, which is only slightly larger than the sum of the depths of the flat tubes.
  • the longitudinal edges of the parts are provided with mutually aligned recesses which are located in the side facing away from the feed and discharge side portion between the transverse wall and the end of the collection chamber.
  • the transverse walls are inserted from the outside into the chambers.
  • slits are provided in the parts or in the bottom.
  • a flat board is first manufactured, in particular by punching, in which the required tabs and the later receiving these tabs openings and recesses are punched. Thereafter, first the longitudinal edges of the parts are bent. Then the passages are incorporated. If the partitions are to be inserted from the bottom in the chambers, so in the manufacture of the passages in the same operation, the passage-like slots are provided for the partitions. If the partitions are to be inserted from the side into the chambers, so the required slots are already incorporated into the planar board. After making the passes, the collection box is finished bending. Then the tabs are caulked.
  • the lids are made as a sheet metal stamping having a corresponding to the contour of the front ends of the collection box encircling, embossed edge.
  • One of the covers in this case has openings for connecting the refrigerant supply and -Ab entry.
  • the edge is provided in the region of the longitudinal edges with a transverse embossing, which is adapted to the sum of the wall thicknesses of the longitudinal edges. Due to the embossed edge creates a step that applies to the inner walls of the collecting tanks when attaching the lid and forms a frictional joint connection. This frictional joint connection is supported by means of several tabs, which connect to the embossed edge and angled at 90 °. These tabs surround the collection boxes on the outside.
  • known standard vaporizers (even with small rib heights) have nearly parallel ribs or a small opening angle between the individual ribs, which due to capillary forces tend to have an unfavorable water storage behavior, i. Store a lot of water locally due to the given geometry.
  • the evaporators may be prone to splash - especially in the case of large quantities of air and small end faces - which in turn limits the permissible rib density (number of rib sections per unit length in the longitudinal direction of the tubes).
  • the risk of splashing is greater, the more condensate accumulates in the individual rib windings or the lower the surface is free to flow through the air.
  • One object is in particular an improved water separation and / or a reduction of the water storage capacity. This object is achieved by a heat exchanger having the features of claim 1.
  • Advantageous embodiments are the subject matter of the subclaims.
  • a heat exchanger is provided, with at least one collecting box made of sheet metal, which is divided in the longitudinal direction at least into two chambers and in the bottom of the ends of tubes, in particular of flat tubes, are introduced, and the collecting box a tunnel-shaped collection box part, a substantially level collection box part, which forms the bottom, and the front side each having lids, wherein at least one lid is at least in its outer edge region formed flat and positively positioned in the collection box. Due to the planar design of the lid, a simple production of the same by means of punching from a sheet, as well as a simple fitting. The lids take up less space compared to the conventional, deep-drawn lids, so that the heat exchanger is smaller builds Rather, for the closed end faces of the heat exchanger, a sheet can be used, which at least substantially corresponds to the partition plates.
  • the positive positioning in the collecting box ensures optimal soldering.
  • the lid is inserted from the front side, wherein it rests Sammelkasten metal on several stops, which are formed on the tunnel-shaped collection box part and / or on the flat collection box part and as a stop pin by means of embossing.
  • the lid is preferably secured by means of a plurality of bent tabs, wherein the tabs are spaced from the stops such that the lid is received as possible clearance between them.
  • the tabs may be bent about an axis parallel to the longitudinal axis of the header. Alternatively, they may be bent from outside to inside.
  • the cover has a thickness, at least in the area located in contact with the collection box, of about 1 to 2 mm, preferably 1.5 mm. Due to the positive positioning before soldering results in an improved lid-tightness. In addition, process reliability can be increased so that fewer faulty heat exchangers are produced.
  • the tabs are preferably part of the tunnel-shaped collection box part and / or the flat collection box part, wherein they are formed by punched-out slots in the corresponding collection box part forming board integral therewith.
  • the cover preferably has in the case of an end-side refrigerant supply and / or -Ab Entry an opening whose edge is bent outwards.
  • the opening is preferably formed circular, in particular as a passage, whereby a different type of training, in particular an oval design, the opening is possible so that the surface of the lid can be optimally utilized, with maximum Strömungsfilkiee.
  • the opening is preferably conical, in particular with an angle of the edge to the longitudinal axis of the passage of a maximum of 5 °, particularly preferably from 2 ° to 3 °, so that the self-locking is ensured.
  • a suction tube is provided, which is attached to the lid with an opening having an inner diameter which corresponds approximately to the outer diameter of the opening delimiting edge, wherein the suction tube is pushed over the passage.
  • An injection pipe which is attached to the cover with an opening, preferably has an outer diameter which corresponds approximately to the smallest inner diameter of the opening delimiting edge.
  • the edge of the collection box plate for the lid preferably has an insertion bevel, which may be formed as bevel but also rounded.
  • the two tunnel-shaped collection box parts preferably have a substantially semicircular shape, which has a positive effect on the strength properties of the collecting box, so that the material thickness - compared to conventional headers - can be preferably reduced, in particular to wall thicknesses of about 0.8 mm with an attachment of injection and suction pipe from one of the front sides (by two lids), or at the longitudinal attachment of the same via a connection gutter in the region of the collecting tank of about 1 mm.
  • the flat tubes used preferably have a width of 2 to 3 mm, making them narrower than conventional flat tubes.
  • the heat exchanger is dependent on the block width 4- or Mehrflutig, in particular 6-flow through.
  • a heat exchanger has flat tubes and corrugated ribs, wherein the corrugated ribs have a rib height which corresponds to the spacing of two flat tubes, and two rib sections connected by a rib bend are inclined to each other at an opening angle ⁇ .
  • a rib height of 3 to 6 mm, preferably of 4 to 5 mm, and a rib density of 50 to 90 ribs, preferably from 60 to 80 ribs, particularly preferably 70 ribs, per 100 mm results in an enlarged angle between the individual ribs (with the same rib density and the same radius of curvature).
  • the opening angle of at least two rib sections is preferably 22 ° +/- 7 ° or 30 ° +/- 10 °.
  • a further enlargement of the opening angle may be achievable if one or more ribbed arches at least in some areas have a radius of curvature of less than 0.4 mm, preferably less than or equal to 0.35 mm, particularly preferably less than or equal to 0.3 mm.
  • a width of the flat tubes of approximately 1.5 to 3 mm is advantageous.
  • Capillary action in the fin turns is reduced by a smaller fin height, or larger fin opening angle, so that less condensate is retained in the fin turns. Associated with it a lower storable amount of water and possibly a better water flow and possibly a lower risk of splashing.
  • a smaller rib height leads to a distribution of the condensate on more ribs and tubes (more heat exchange surface), so that less condensate per Rippenwindung accumulates. This in turn results in a lower risk of splashing and possibly a more favorable flow behavior along the tubes and / or the ribs.
  • Indirect benefits may include a higher allowable rib density and thus an increased performance potential, a lower risk of bacterial growth and thus a reduced odor and possibly a cost savings through simpler surface treatment, which may even be completely eliminated.
  • a reduction of a so-called flash fog danger (sudden misting of windshields due to moisture from the evaporator) by faster drying of the evaporator surface is possible.
  • Such a heat exchanger is used in particular as a flat tube evaporator for a motor vehicle air conditioning.
  • a flat-tube evaporator 1 (only partially shown) of a motor vehicle air conditioner, as previously with reference to the DE 198 26 881 A1 described, two header boxes 2, flat tubes (not shown) extending between the two header boxes 2, and corrugated fins 3, which are arranged between the flat tubes.
  • Each collection box 2 is formed according to the embodiment of a board which is punched out of a metal sheet and then shaped so that a flat collection box part 4 and at the longitudinal edges then two tunnel-shaped collection box parts 5 are formed (see in particular FIGS. 4 and 6 ).
  • the longitudinal edges are provided with a plurality of distributed over the length arranged tabs, which are inserted through recesses of the flat collection box part 4 and are caulked on the flat tubes facing the outside.
  • the front ends are closed by means of covers 6 described in more detail below.
  • a plurality of passages 7 are formed, in which the flat tubes are guided, wherein the opening of the passages 7 substantially corresponds to the outer shape of the flat tubes.
  • the two tunnel-shaped collection box parts 5 have due to a relatively small depth on a substantially semicircular shape, such as the representation of Fig. 7 can be removed. Due to the improved strength properties as a result of the semicircular Shape of the collection box parts 5 and / or the smaller installation depth wall thicknesses of 0.8 to 1 mm, in contrast to the usual wall thicknesses of 1.2 to 1.5 mm possible.
  • one or more partitions 8 are provided, through which the flow path for a fluid such as the refrigerant through the heat exchanger, in particular its flat tubes can be predetermined.
  • the partitions 8 are preferably inserted through slots 9 in a flat collection box part 4, wherein the partitions 8 each between two openings or passages 7 for the tubes, such as flat tubes, are arranged and the distance of the passages 7 by the partitions 8 preferably not changed is.
  • a guide element such as a guide, for example. With a depth of 0.2 to 0.3 mm, to a guide of the partition wall 8 provided (see Fig. 11 ).
  • each cover 6 in the flat collection box part 4 only one stop 10 and offset this two tabs 11 is provided, but according to a variant not shown in the drawing also a the tunnel-shaped collection box part 5 corresponding design possible.
  • the tabs 11 are viewed from the stops 10 in the longitudinal direction of the header 2 to the thickness of the lid 6 forming sheet spaced from each other, so that an exact positioning as a result of a positive connection before soldering is possible.
  • the tabs 11 are bent about an axis which is parallel to the collection box longitudinal axis. According to a variant not shown in the drawing, bending of the tabs towards the cover is also possible, so that only two tabs each extending in the longitudinal direction of the collecting box need to be provided in the blank. Further, according to another variant not shown in the drawing, the limitation of the insertion of the lid may be limited by the respective first passage for the flat tubes, so that only in the tunnel-shaped collection box part stops must be provided and the total length of the collecting tank are optimally utilized can.
  • the refrigerant supply and discharge takes place as Fig. 10 can be removed, via an attached to each one provided with an opening 12 cover 6 injection pipe 13 and a suction pipe 14.
  • Die ⁇ réelle 12 der Lid 6 are formed in the corresponding punched sheet metal part as passages, wherein the cover 6 are installed in the collecting box 2 such that the edges of the passage each protrude outward.
  • the output sheet thickness of the cover 6, ie, the thickness of the unprocessed sheet is about 1.5 mm, to ensure a secure solder joint on the narrow sides and a sufficient material thickness for the passages, so that a sufficient. large connection surface and thus a secure connection between the pipes for the refrigerant supply and - discharge and the passages can be ensured.
  • the cover 6 without draft at least in their outer, adjacent to the board of the header box 2 border areas flat.
  • the passage for the injection tube 13 is formed such that the injection tube 13 is inserted into the opening 12 up to the height of the stops 10.
  • the passage of the lid 6 has a slightly conical, over the length of the passage to the outside tapered inner diameter.
  • the passage for the suction tube 14 has an outwardly tapering outer diameter, wherein the slightly expanded at its end suction pipe 14 is pushed from the outside.
  • the slope is at both openings 12 preferably 2-3 °, but not more than 5 °.
  • five-chambered flat tubes are used, in particular with a width of about 2.5 mm, wherein the web spacing remains unchanged, so that the air-side pressure drop does not increase or only marginally, compared with known evaporators with normal depth.
  • the flow through the evaporator can take place, for example, 6-fold or, in particular in the case of small block widths, 4-pass.
  • Fig. 13 is the rib geometry (opening angle ⁇ between adjacent rib portions 101 which are connected to each other via a rib bow 102) at 8 mm ( Fig. 13a ) and 4 , 5 mm rib height ( Fig. 13b ), in each case at 60 ribs per 100 mm, shown in comparison.
  • Fig. 13b is a rib bow 102 having a smaller radius of curvature (as compared to FIG Fig. 13a ).
  • a radius of curvature in each point of the rib bow 102 may be different and thus other symmetrical or asymmetrical shapes of the rib bow 102 are possible in addition to a circular arc-shaped cross section.
  • Fig. 14 shows the stored amounts of water as a function of the heat exchange surface of proven heat exchangers, wherein the fin height 1 is greater than the fin height 2 and the fin height 2 is greater than the fin height 3.
  • the values were determined by means of a simple screening test, in which first the evaporators are immersed in a water bath and, after removal after a certain dripping time, the remaining amount of water remaining in the evaporator is determined by weighing.
  • Fig. 15 are the stored on the heat exchange surface stored amounts of water as a function of the rib height shown, the rib height decreases to the right. The values were determined during operation at a given operating point.
  • Fig. 16 the critical air volumes are plotted above the rib height, starting from which a spraying of the respective evaporator starts (values likewise determined during operation).
  • the rib height here increases to the right.
  • the opening angle ⁇ is about 14 ° (at 60 fins per 100 mm), or lower.
  • angles of approx. 28 ° can be achieved (again with 60 ribs per 100 mm) (cf. Fig. 13 ). If the radii of curvature of the ribbed curves 102 are not yet executed, the opening angle can be further increased.
  • rib densities are also allowed, which in turn have a positive effect on performance, although this somewhat reduces the opening angle.
  • the resulting angle at a 6 mm high rib is between 15 ° and 22 ° (evaporator with 6 mm high rib also already show a much better drainage and storage behavior as evaporator mti 8 mm high rib, here is also the number of drainage surfaces or flat tubes already higher).
  • the water separation is also favored by a larger available drainage surface along the flat tubes or by the larger number of drainage surfaces / flat tubes with a comparable amount of condensate.

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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)

Claims (15)

  1. Echangeur de chaleur, en particulier évaporateur à tubes plats (1) pour un système de climatisation d'un véhicule automobile, ledit échangeur de chaleur comprenant au moins un bac collecteur (2), en tôle, qui est subdivisé dans le sens de la longueur en au moins deux chambres, et dans le fond duquel sont introduites les extrémités de tubes, en particulier de tubes plats, et le bac collecteur (2) présente une partie (5) du bac collecteur, en forme de tunnel, une partie (4) du bac collecteur, pratiquement plane, qui forme le fond, et présente à chaque fois, côté frontal, un couvercle (6), caractérisé en ce qu'au moins un couvercle (6) est configuré de façon plane au moins dans sa zone de bordure extérieure et positionné dans le bac collecteur par complémentarité de forme, en ce que le couvercle (6) est introduit par le côté frontal et est en appui, côté bac collecteur, sur plusieurs butées (10) qui sont configurées sur la partie (5) du bac collecteur, en forme de tunnel, et / ou sur la partie plane (4) du bac collecteur, où les butées (10) sont configurées par matriçage comme des pions de butée, et en ce que le couvercle (6) est verrouillé au moyen de pattes recourbées (11).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les pattes (11) sont parmi les composants de la partie (5) du bac collecteur, en forme de tunnel, et / ou parmi ceux de la partie plane (4) du bac collecteur.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que le couvercle (6) présente une ouverture (12) prévue pour l'amenée ou l'évacuation de fluide frigorigène, ouverture dont le bord est en particulier courbé vers l'extérieur.
  4. Echangeur de chaleur selon la revendication 3, caractérisé en ce que l'ouverture (12) est configurée comme un passage.
  5. Echangeur de chaleur selon la revendication 3 ou 4, caractérisé en ce que l'ouverture (12) est configurée de façon conique, en ayant un angle au maximum de 5°, compris en particulier entre 2° et 3°.
  6. Echangeur de chaleur selon l'une quelconque des revendications 3 à 5, caractérisé en ce qu'un tube d'aspiration (14), qui est fixé sur le couvercle (6) ayant une ouverture (12), présente un diamètre intérieur qui correspond à peu près au diamètre extérieur du bord délimitant l'ouverture (12).
  7. Echangeur de chaleur selon l'une quelconque des revendications 3 à 6, caractérisé en ce qu'un tube d'injection (13), qui est fixé sur le couvercle (6) ayant une ouverture (12), présente un diamètre extérieur qui correspond à peu près au plus petit diamètre intérieur du bord délimitant l'ouverture.
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le bord de la tôle du bac collecteur présente un chanfrein d'introduction prévu pour le couvercle (6).
  9. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les deux parties (5) du bac collecteur, en forme de tunnel, présentent une forme pratiquement demi-circulaire.
  10. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que des parois de séparation (8) sont disposées dans l'échangeur de chaleur, de manière telle que l'échangeur de chaleur soit traversé par 4 flux ou plus.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, comprenant des tubes plats et des ailettes ondulées, comprenant au moins un bac collecteur dans le fond duquel sont introduites les extrémités des tubes plats, où les ailettes ondulées présentent une hauteur d'ailettes qui correspond à la distance comprise à chaque fois entre deux tubes plats, et où deux sections d'ailettes reliées à chaque fois par un arc d'ailettes sont inclinées l'une par rapport à l'autre en formant un angle d'ouverture α, caractérisé en ce que l'ailette ondulée (3) présente une hauteur de 3 mm à 6 mm, de préférence de 4 mm à 5 mm, et présente, à chaque fois pour 100 mm, une densité d'ailettes de 50 à 90 ailettes, de préférence de 60 à 80 ailettes, en particulier de préférence de 70 ailettes.
  12. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'angle d'ouverture au moins de deux sections d'ailettes, de préférence de nombreuses ou de toutes les sections d'ailettes, est de 22° +/- 7° ou de 30° +/- 10°.
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un ou plusieurs arcs d'ailettes présentent au moins partiellement un rayon de courbure inférieur à 0,4 mm, de préférence inférieur ou égal à 0,35 mm, en particulier de préférence inférieur ou égal à 0,3 mm.
  14. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes plats présentent une largeur de 1,5 mm à 3 mm environ.
  15. Système de climatisation d'un véhicule automobile caractérisé par un évaporateur selon l'une quelconque des revendications précédentes.
EP05707067.4A 2004-01-28 2005-01-28 Echangeur de chaleur, en particulier evaporateur a tuyaux plats pour un systeme de climatisation de vehicule a moteur Not-in-force EP1711772B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004004494 2004-01-28
PCT/EP2005/000859 WO2005073662A1 (fr) 2004-01-28 2005-01-28 Echangeur de chaleur, en particulier evaporateur a tuyaux plats pour un systeme de climatisation de vehicule a moteur

Publications (2)

Publication Number Publication Date
EP1711772A1 EP1711772A1 (fr) 2006-10-18
EP1711772B1 true EP1711772B1 (fr) 2016-12-28

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EP05707067.4A Not-in-force EP1711772B1 (fr) 2004-01-28 2005-01-28 Echangeur de chaleur, en particulier evaporateur a tuyaux plats pour un systeme de climatisation de vehicule a moteur

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US (1) US20080029256A1 (fr)
EP (1) EP1711772B1 (fr)
CN (1) CN100565079C (fr)
BR (1) BRPI0507143B1 (fr)
DE (1) DE102005004284A1 (fr)
WO (1) WO2005073662A1 (fr)

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DE102008035358A1 (de) * 2008-07-29 2010-02-04 Modine Manufacturing Co., Racine Wärmetauscher mit Sammelrohr und Sammelrohr sowie Herstellungsverfahren dafür
DE202009006156U1 (de) 2009-04-28 2009-07-02 Behr Gmbh & Co. Kg Wärmeübertrager
DE102009018929A1 (de) 2009-04-28 2010-11-04 Behr Gmbh & Co. Kg Wärmeübertrager
DE202009006157U1 (de) 2009-04-28 2009-07-02 Behr Gmbh & Co. Kg Wärmeübertrager
DE202009006155U1 (de) 2009-04-28 2009-07-02 Behr Gmbh & Co. Kg Wärmeübertrager
FR2962206B1 (fr) * 2010-06-30 2014-12-19 Valeo Systemes Thermiques Collecteur pour echangeur de chaleur et echangeur de chaleur equipe d'un tel collecteur
CN102062549B (zh) * 2011-02-15 2012-08-29 金龙精密铜管集团股份有限公司 扁管热交换器
CZ2012317A3 (cs) * 2012-05-14 2013-11-27 Halla Visteon Climate Control Corporation Sberná hlavová nádrz
DE102012217340A1 (de) 2012-09-25 2014-03-27 Behr Gmbh & Co. Kg Wärmeübertrager
CN104937364B (zh) * 2013-01-28 2019-03-08 开利公司 具有歧管组件的多管束换热单元
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
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
CN106855164A (zh) * 2015-12-09 2017-06-16 王翔 一种空调连接管
US10648742B2 (en) * 2016-03-16 2020-05-12 Mitsubishi Electric Corporation Finless heat exchanger, outdoor unit of an air-conditioning apparatus including the finless heat exchanger, and indoor unit of an air-conditioning apparatus including the finless heat exchanger
FR3081984A1 (fr) * 2018-05-31 2019-12-06 Valeo Systemes Thermiques Boite collectrice et echangeur thermique correspondant
EP3587990B1 (fr) * 2018-06-22 2021-01-27 Valeo Vyminiky Tepla, s.r.o. Boîte collectrice pour échangeur de chaleur à découplage thermique
WO2020138850A1 (fr) * 2018-12-26 2020-07-02 한온시스템 주식회사 Échangeur de chaleur
DE102019207905A1 (de) 2019-05-29 2020-12-03 Hanon Systems Profil für einen Rohrboden eines Kühlers, Rohrboden mit einem derartigen Profil und Kühler mit einem Rohrboden
EP4317898A1 (fr) * 2022-08-04 2024-02-07 Valeo Systemes Thermiques Collecteur

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JP2002257493A (ja) * 2001-02-28 2002-09-11 Toyo Radiator Co Ltd アルミニューム製熱交換器の製造方法

Also Published As

Publication number Publication date
WO2005073662A1 (fr) 2005-08-11
DE102005004284A1 (de) 2005-08-11
BRPI0507143B1 (pt) 2018-08-07
CN100565079C (zh) 2009-12-02
BRPI0507143A (pt) 2007-06-19
US20080029256A1 (en) 2008-02-07
EP1711772A1 (fr) 2006-10-18
CN1914473A (zh) 2007-02-14

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