EP1711772A1 - 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

Info

Publication number
EP1711772A1
EP1711772A1 EP05707067A EP05707067A EP1711772A1 EP 1711772 A1 EP1711772 A1 EP 1711772A1 EP 05707067 A EP05707067 A EP 05707067A EP 05707067 A EP05707067 A EP 05707067A EP 1711772 A1 EP1711772 A1 EP 1711772A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
collecting box
exchanger according
flat
cover
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
EP05707067A
Other languages
German (de)
English (en)
Other versions
EP1711772B1 (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
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 EP1711772A1 publication Critical patent/EP1711772A1/fr
Application granted granted Critical
Publication of EP1711772B1 publication Critical patent/EP1711772B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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

  • Heat exchanger in particular flat tube evaporator for an automotive air conditioning system
  • 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 in particular an evaporator, is known from DE 198 26 881 A1, in which a collecting box made of sheet metal is provided, which is formed from a prepared circuit board.
  • the board consists of an aluminum alloy, from which the flat tubes, the corrugated fins and the side parts as well as the other elements of the heat exchanger are made. It is first punched out of a plate, which is then shaped in such a way that a flat bottom (essentially flat collecting box part) is formed, with bent parts (tunnel-shaped collecting box parts) adjoining its longitudinal edges.
  • the bent parts are bent in a radius to form a cylindrical surface, from which the longitudinal edges are bent in such a way that they abut one another parallel to one another and run essentially perpendicular to the floor.
  • the Longitudinal edges are provided with a plurality of tabs which are distributed over their length and which are inserted through recesses in the base and are caulked on the outside facing the flat tubes. In this way, a collecting box with the two chambers is formed, which has a relatively high strength before soldering takes place.
  • the board is solder plated or provided with a solder coating.
  • Passages are provided in the floor, in which the flat tubes are received.
  • the passages are pulled up to the longitudinal edges lying against one another. This results in a depth for the heat exchanger that is only slightly greater than the sum of the depths of the flat tubes.
  • the longitudinal edges of the parts are provided with recesses which are aligned with one another and which are located in the section facing away from the supply and discharge side between the transverse wall and the end of the collecting chamber.
  • the transverse walls are inserted into the chambers from the outside. For this purpose, slots are provided in the parts or in the floor.
  • a flat circuit board is first produced, in particular by punching out, in which the required tabs and the openings and cutouts later receiving these tabs are punched. Then the longitudinal edges of the parts are first bent. Then the passages are incorporated. If the dividing walls are to be inserted into the chambers from the bottom, the passage-like slots for the dividing walls are also provided when the passages are manufactured in the same operation. If the partitions are to be inserted into the chambers from the side, the slots required for this are already machined into the flat board. After the pull-throughs have been made, the collecting box is bent. The tabs are then caulked.
  • the covers are produced as a pressed sheet metal part, which has an embossed edge that runs all around the contour of the ends of the collecting box.
  • One of the covers has openings for connecting the refrigerant supply and discharge.
  • the edge is provided with a transverse embossing in the area of the longitudinal edges, which is adapted to the sum of the wall thicknesses of the longitudinal edges. Due to the embossed edge, a step is created, which attaches itself to the inner walls of the collecting boxes when the lids are attached and forms a frictional joint connection. This frictional joint connection is supported by several tabs that connect to the embossed edge and are angled by 90 °. These tabs grip the collection boxes on the outside.
  • known evaporators with the standard rib densities have almost parallel ribs or a small opening angle between the individual ribs, which tend to have an unfavorable water storage behavior due to capillary forces, i.e. store a lot of water locally due to the given geometry.
  • the evaporators may tend to spray - especially if there is a large amount of air and small end faces - which in turn limits the permissible fin density (number of fin sections per unit length in the longitudinal direction of the pipes).
  • the risk of splashing increases, the more condensate accumulates in the individual fin coils or the smaller the area through which the air can flow freely.
  • An unfavorable water storage and drainage behavior due to the given rib geometry have, for example, evaporators with almost parallel ribs or small opening angles between the individual rib sections. In particular, the flow rate or amount of air up to which spraying can still be avoided is limited.
  • One task is in particular an improved water separation and / or a reduction in the water storage capacity
  • a heat exchanger is provided with at least one collecting box made of sheet metal, which is arranged in the longitudinal direction in at least two. Chambers is divided and in the bottom of which the ends of tubes, in particular flat tubes, are inserted, and the collecting box has a tunnel-shaped collecting box part, an essentially flat collecting box part which forms the bottom, and each has a cover on the end face, at least one of which Lid is flat at least in its outer edge area and positively positioned in the collecting box.
  • the flat design of the cover enables it to be • easily manufactured by punching from a sheet metal, and to be easily fitted.
  • the lids take up less space compared to the conventional, deep-drawn lids, so that the heat exchanger is smaller.
  • a plate can be used for the closed end faces of the heat exchanger, which at least essentially corresponds to the partition plates.
  • the form-fit positioning in the collecting box ensures optimal soldering.
  • the cover is preferably inserted from the front side, with it abutting on the collecting box side at a plurality of stops which are formed on the tunnel-shaped collecting box part and / or on the flat collecting box part.
  • the cover is preferably secured on the outside by means of a plurality of bent-over tabs, the tabs being spaced apart from the stops in such a way that the lid is accommodated between them with as little play as possible.
  • the tabs can be bent about an axis running parallel to the longitudinal axis of the collecting tank. Alternatively, they can be bent from the outside in.
  • the cover has a thickness, at least in the area in contact with the collecting box, of approximately 1 to 2 mm, preferably 1.5 mm.
  • the positive positioning before soldering results in improved lid tightness.
  • process reliability can be increased so that fewer faulty heat exchangers are produced.
  • the tabs are preferably part of the tunnel-shaped collecting box part and / or the flat collecting box part, wherein they are formed in one piece with the same by punched slots in the circuit board forming the corresponding collecting box part.
  • the cover preferably has an opening, the edge of which is bent outwards.
  • the opening is preferably circular, in particular as a passage, a different design, in particular an oval design, of the opening is also possible, so that the surface of the cover can be optimally used, with maximum flow area.
  • the opening is preferably conical, in particular with an angle of the edge to the longitudinal axis of the passage of at most 5 °, in particular preferably from 2 ° to 3 °, so that self-locking is ensured.
  • a suction pipe is preferably provided, which is attached to the cover with an opening and which has an inner diameter which corresponds approximately to the outer diameter of the edge delimiting the opening, the suction pipe being pushed over the passage. This enables the flow cross-section to remain constant and widen slightly in the direction of flow, so that it is designed as large as possible and the pressure drop on the refrigerant side can be kept as low as possible. This allows the evaporator output to be increased.
  • 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 edge delimiting the opening.
  • the edge of the collecting box sheet for the covers preferably has an insertion bevel, which can also be rounded as a chamfer.
  • the two tunnel-shaped collecting box parts preferably have an essentially semicircular shape, which has a positive effect on the strength properties of the collecting box, so that the material thickness - compared to conventional collecting boxes - can preferably be reduced, in particular to wall thicknesses of approximately 0. 8 mm when attaching the injection and suction pipe from one of the front sides (through two lids), or when attaching the same lengthways via a connection core in the area of the header box of approx. 1 mm.
  • the flat tubes used preferably have a width of 2 to 3 mm, which makes them narrower than conventional flat tubes.
  • the heat exchanger can flow through 4 or more passages, in particular 6 passages.
  • a heat exchanger has flat tubes and corrugated fins, the corrugated fins having a fin height which corresponds to the distance between two flat tubes, and wherein two fin sections connected via a fin arch are inclined to one another 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 of 60 to 80 ribs, particularly preferably 70 ribs, each 100 mm
  • an enlarged angle results according to the present invention 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 increase in the opening angle can be achieved under certain circumstances if one or more rib arches 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, at least in some areas.
  • a width of the flat tubes of approximately 1.5 to 3 mm is advantageous.
  • a smaller fin height or a larger fin opening angle reduces a capillary action in the fin windings, so that less condensate remains in the fin windings. Are connected with it a smaller amount of water that can be stored and, under certain circumstances, a better water drainage and possibly a lower risk of splashing.
  • a smaller fin height leads to a distribution of the condensate over more fins and pipes (more heat exchange surface), so that overall less condensate is generated per fin turn. This in turn results in a lower risk of splashing and possibly a more favorable drainage behavior along the tubes and / or the fins.
  • Indirect advantages may be a higher permissible rib density and thus an increased performance potential, a lower risk of bacterial growth and thus a reduced odor formation, and possibly a cost saving through simpler surface treatment, which may even be completely eliminated under certain circumstances.
  • a so-called flash fog risk den fogging of windshields due to moisture from the evaporator
  • Such a heat exchanger is used in particular as a flat tube evaporator for a motor vehicle air conditioning system.
  • FIG. 1 shows a perspective illustration of a collecting box
  • FIG. 2 shows a detailed view of the collecting box from FIG. 1,
  • FIG. 3 shows the collecting box from FIG. 1 before the installation of the front-mounted cover
  • 4 is a detailed view of FIG. 3
  • FIG. 5 shows a detailed view of the collecting box from FIG. 1, the right one of the two lids not being shown,
  • FIG. 6 a detailed view corresponding to FIG. 5 from a different perspective
  • Fig. 8 is a section along line A-A in Fig. 7,
  • FIG. 9 is a sectional view corresponding to FIG. 8 without cover
  • FIG. 11 shows a section in the longitudinal direction of the collecting tank to illustrate a partition
  • Fig. 12a, 12b views of two Wellrippbleche, wherein 'in Fig. 12a is a known form, and in Fig. 12b is a form is shown for a larger flat tube density,
  • 13a, 13b each a section of a corrugated fin of an evaporator in different geometries
  • a flat tube evaporator 1 (only partially shown) of a motor vehicle air conditioning system has, as already described above with reference to DE 198 26 881 A1, two header boxes 2, flat tubes (not shown) which run between the two header boxes 2, and corrugated fins 3 on, which are arranged between the flat tubes.
  • each collecting box 2 is formed from a circuit board which is punched out of sheet metal and is then shaped such that a flat collecting box part 4 and then two tunnel-shaped collecting box parts 5 are formed on its longitudinal edges (see in particular FIGS. 4 and 6) ).
  • the longitudinal edges are provided with a plurality of tabs arranged distributed over their length, which are inserted through recesses in the flat collecting box part 4 and are caulked on the outside facing the flat tubes.
  • the front ends are closed by means of covers 6 described in more detail later.
  • the two tunnel-shaped collecting box parts 5 have an essentially semicircular shape due to a relatively small structural depth, as can be seen, for example, from the illustration in FIG. 7.
  • One or more partition walls 8 are provided in the interior of the header tank 2, 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 can preferably be inserted through slots 9 in a flat collecting box part 4, the partitions 8 each being arranged between two openings or passages 7 for the pipes, such as flat pipes, and the spacing of the passages 7 through the partitions 8 preferably not changing is.
  • a partition wall slot is punched out or otherwise introduced in the collecting box 2 in one area, so that under certain circumstances no passage is formed, and / or in another area a guide element, such as a guide groove, for example with a depth of 0.2 up to 0.3 mm, to guide the partition 8 (see FIG. 11).
  • the cover 6, which is made of sheet metal, is attached to the collecting box 2 from the end, whereby it is inserted as far as stops 10 formed by stop pins, which are formed on the board by means of stamping, and punched out during the manufacture of the board and after the positioning of the Cover 6 bent tabs 11 are locked.
  • insertion bevels are provided on the board (see chamfer in FIG. 9, which goes over about half the board thickness). Both the tabs 11 and the stops 10 in the tunnel-shaped collecting box part 5 are each at the same height, as seen in the longitudinal direction of the collecting box 2.
  • each cover 6 in the flat collecting box part 4 has only one stop 10 and offset two tabs 11, but according to a variant not shown in the drawing, there is also one the design corresponding to the tunnel-shaped collecting box part 5 is possible.
  • the tabs 11 are spaced apart from one another by the stops 10 in the longitudinal direction of the collecting tank 2 by the thickness of the sheet forming the cover 6, so that an exact positioning as a result of a positive connection is possible before the soldering.
  • the tabs 11 are bent around an axis which runs parallel to the longitudinal axis of the collecting box. According to a variant not shown in the drawing, it is also possible to bend the tabs towards the lid, so that only two slots in the plate running in the longitudinal direction of the collecting box have to be provided for each tab. Furthermore, according to a further variant, not shown in the drawing, the limitation of the insertion of the covers can be limited to the first passage for the flat tubes, so that stops only have to be provided in the tunnel-shaped collecting box part and the total length of the collecting box can be optimally used can.
  • the refrigerant supply and discharge takes place, as can be seen in FIG. 10, via an injection pipe 13 or a suction pipe 14 attached to a cover 6 provided with an opening 12.
  • the openings 9 of the cover 6 are in the corresponding stamped-out sheet metal part formed as passages, the covers 6 being installed in the collecting box 2 in such a way that the edges of the passages each project outwards.
  • the starting plate thickness of the cover 6, ie the thickness of the unprocessed plate is approximately 1.5 mm in order to ensure a secure solder connection on the narrow sides and a sufficient material thickness for the pull-throughs, so that there is also a sufficiently large connection area and thus a secure connection between the pipes for the refrigerant supply and discharge and the passages can be guaranteed.
  • the cover 6 is also flat without a passage, at least in its outer edge regions lying against the circuit board of the collecting box 2.
  • the passage for the injection pipe 13 is designed such that the injection pipe 13 is pushed into the opening 12 up to the height of the stops 10.
  • the passage of the cover 6 has a slightly conical inner diameter which tapers outwards over the length of the passage.
  • the passage for the suction pipe 14 has an outwardly tapering outer diameter, the suction pipe 14 being slightly widened at its end being pushed on from the outside.
  • the slope at both openings 12 is preferably 2-3 °, but maximum
  • Five-chamber flat tubes in particular with a width of approximately 2.5 mm, are preferably used, the web spacing remaining unchanged, so that the air-side pressure drop does not increase, or increases only insignificantly, compared to known evaporators with a normal overall depth.
  • the flow through the evaporator can be 6-flow, for example, or, especially in the case of small block widths, 4-flow.
  • FIG. 13 shows a costal arch 102 with a smaller radius of curvature (compared to FIG. 13a).
  • a radius of curvature can be different at each point of the costal arch 102 and that, in addition to an arcuate cross section, other symmetrical or asymmetrical shapes of the costal arch 102 are also possible.
  • the fin height 1 being greater than the fin height 2 and the fin height 2 being greater than the fin height 3.
  • a positive influence of the smaller rib height on the storage capacity is also noticeable here.
  • the values were determined by means of a simple screening test, in which the evaporators are first immersed in a water bath and, after removal after a certain draining time, the amount of residual water still in the evaporator is determined by weighing.
  • the opening angle ⁇ is approximately 14 ° (with 60 fins per 100 mm), or lower.
  • angles of approx. 28 ° can be achieved (again with 60 ribs per 100 mm) (see Fig. 13).
  • the resulting angle for a 6 mm high rib is between 15 ° and 22 ° (evaporators with a 6 mm high rib already show a significantly better drainage and storage behavior than evaporators with an 8 mm high rib, but here is also the number of drain surfaces or flat tubes already higher).
  • the water separation is further favored by a larger available drainage surface along the flat tube or by the larger number of drainage surfaces / flat tubes with a comparable amount of condensate.

Landscapes

  • 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)

Abstract

Echangeur de chaleur, en particulier évaporateur à tuyaux plats pour un système de climatisation de véhicule à moteur, qui comporte au moins un récipient collecteur en tôle divisé dans le sens de la longueur en au moins deux chambres et dans le fond duquel sont introduites les extrémités de tuyaux, en particulier de tuyaux plats. Ledit récipient de collecte comporte une partie en forme de tunnel, une partie essentiellement plane qui forme le fond et des couvercles au niveau de ses extrémités, au moins un couvercle étant plan au moins dans sa zone de bordure extérieure et positionné par liaison de forme dans le récipient collecteur.
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 true EP1711772A1 (fr) 2006-10-18
EP1711772B1 EP1711772B1 (fr) 2016-12-28

Family

ID=34745195

Family Applications (1)

Application Number Title Priority Date Filing Date
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

Country Status (6)

Country Link
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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FR3081984A1 (fr) 2018-05-31 2019-12-06 Valeo Systemes Thermiques Boite collectrice et echangeur thermique correspondant
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CN1914473A (zh) 2007-02-14
BRPI0507143A (pt) 2007-06-19
BRPI0507143B1 (pt) 2018-08-07
DE102005004284A1 (de) 2005-08-11
EP1711772B1 (fr) 2016-12-28
CN100565079C (zh) 2009-12-02
WO2005073662A1 (fr) 2005-08-11
US20080029256A1 (en) 2008-02-07

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