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EP1248063B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1248063B1
EP1248063B1 EP02006050A EP02006050A EP1248063B1 EP 1248063 B1 EP1248063 B1 EP 1248063B1 EP 02006050 A EP02006050 A EP 02006050A EP 02006050 A EP02006050 A EP 02006050A EP 1248063 B1 EP1248063 B1 EP 1248063B1
Authority
EP
European Patent Office
Prior art keywords
evaporator
flat tubes
accordance
block
heat medium
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.)
Expired - Lifetime
Application number
EP02006050A
Other languages
German (de)
English (en)
Other versions
EP1248063A1 (fr
Inventor
Josef Kern
Christoph Walter
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 EP1248063A1 publication Critical patent/EP1248063A1/fr
Application granted granted Critical
Publication of EP1248063B1 publication Critical patent/EP1248063B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/26—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 and extending transversely the means being integral with the element
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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

Definitions

  • the invention relates to an evaporator of a motor vehicle air conditioner with the features according to the preamble of claim 1.
  • evaporators are e.g. from EP-A-0947792.
  • Heat exchangers of the type mentioned have a substantially formed of parallel flat tubes block, wherein the flat tubes of a slightly evaporating heat medium, namely a refrigerant, flows through.
  • This block is traversed transversely to its end face by a second medium, usually air, wherein on the surface of the flat tubes, a heat exchange between the first and the second heat medium takes place.
  • a second medium usually air
  • the cold produced by the evaporation process of the first heat medium is conducted through the metallic wall of the flat tubes to the outer surface and to the air flowing past transferred, whereby this cooled air is used for air conditioning of the vehicle interior.
  • the volume of the heat exchanger is composed essentially of the end face and the block depth, wherein the block depth substantially corresponds to the depth of the flat tubes of one or more rows of tubes.
  • One way to reduce the volume of construction is to reduce the block depth, which shortens the path of the air flowing through the block in the direction of the block depth.
  • a variety of solutions are known, which are based essentially on an increase in the heat-transmitting surface. These are on the surface of the flat tubes, which faces the heat medium with the lower heat capacity, so here on the air side, surface enlarging facilities such as fins, corrugated fins or the like. Provided. However, such measures are not sufficient with correspondingly compact designs of the heat exchanger and high power requirement.
  • the invention has for its object to provide an evaporator, in which the required volume of construction is reduced.
  • the flat tubes in the direction of the block depth at least over a section at an angle to the end face of the block.
  • the angle is expediently approximately in a range between 25 ° and 65 ° and is in particular about 45 °.
  • the channels formed between the flat tubes for the air flowing through are rotated approximately at the same angle, so that the flow direction of the air between the flat tubes has a component inclined to the end face.
  • the flat tubes have a cross-section approximately in the form of a wave, with the convex side of a shaft of a flat tube engaging in the concave side of the corresponding shaft of the adjacent flat tube at a distance.
  • the waveform is approximately angled, that is formed, for example, in staircase form. This allows a cost-effective production with simple means.
  • the waveform is rounded, whereby the flow resistance is kept low for the air flowing through the block.
  • the Waveform formed such that the side surfaces of the flat tubes in the region of at least one longitudinal edge and in particular in the region of both longitudinal edges are approximately perpendicular to the end face.
  • the inflowing and possibly also the outflowing air is thereby led straight into the heat exchanger block or let out of it, wherein a deflection takes place only within the heat block under aerodynamically well-defined conditions with low flow losses.
  • the side surfaces of the flat tubes have means for enlarging the heat-transmitting surface and / or the flow path.
  • longitudinal ribs lying on the side surfaces of the flat tubes in the direction of their longitudinal axis are provided and arranged offset relative to one another such that the longitudinal ribs of a flat tube engage in the intermediate spaces of the longitudinal ribs of the adjacent flat tube on its adjacent side surface.
  • the resulting mutual engagement of the longitudinal ribs generates a further approximately wave-shaped deflection of the air flow along its path in the depth direction of the heat exchanger block in conjunction with an enlargement of the heat-transferring surface.
  • discrete projections are arranged on the side surfaces of the flat tubes, which also mutually engage in the intermediate spaces between the projections of the adjacent tube.
  • the projections must be surrounded on the outside by the air.
  • the projections also increase due to their Geome-trie conditionally the heat-transferring surface. Furthermore, there is a flow deflection and thus a flow path extension with a component which is parallel to the longitudinal axis of the flat tubes.
  • the said projections expediently have an aerodynamic cross-section, for example in the form of an oval or an ellipse, whereby the flow resistance for the air flowing through is reduced.
  • the projections extend from one outer side of a flat tube to the adjacent outer side of the adjacent flat tube, whereby they also serve as spacers.
  • struts may be provided which extend transversely through a plurality of flat tubes.
  • a block of flat tubes is threaded onto these struts, the struts serve as an assembly aid and align the flat tubes against each other.
  • the struts fulfill the function of the projections described above.
  • the mentioned variants of the surface and Strömungswegver sparnden means are expediently made in one piece with a wall of the flat tube.
  • the transverse ribs contribute to the increase in surface area, wherein the transverse ribs in the material composite are formed by the process of peeling out stay with the flat tube with a corresponding, correspondingly good heat transfer.
  • the transverse ribs may have an edge in waveform, wherein the waveform may be comparable to the serrated edge of a knife in the transverse rib plane.
  • the waveform of the edge is approximately perpendicular to the surface of the transverse rib, whereby this also has a strömungswegver multlusrnde effect.
  • the flat tubes are designed as multi-chamber tubes with individual channels for the first heat medium.
  • the flat tubes are made of a light metal sheet, whereby a cost-effective production is made possible even under high-volume conditions.
  • the flat tubes are produced by extrusion or extrusion, including light metal and aluminum in particular not only because of the relatively low weight, but equally suitable both from manufacturing aspects and because of its good heat transfer properties.
  • the evaporator 1 shows a schematic overview of a heat exchanger of an air conditioning system of a motor vehicle, using the example of an evaporator 1.
  • a condenser belonging to the air conditioning system can also be designed according to the invention, described below.
  • the evaporator 1 comprises a plurality of flat tubes 4, 4 ', which are substantially parallel to each other in the form of a block 5 summarized.
  • the flat tubes 4, 4 ' are connected at their two ends in each case with a collecting box 29, 30 flow-conducting.
  • the upper collection box 29 is divided by a total of four partitions 31 into a total of four subspaces 38, while the lower collection box 30 is divided by a partition wall 32 into two subspaces 39.
  • a slightly vaporizable first heat medium 2 flows through the flat tubes 4, 4 'along the arrows 27, wherein the arrangement of the partitions 31, 32 results in a flow through the flat tubes 4, 4' in the form of a countercurrent flow.
  • an embodiment of the evaporator 1 with another flow pairing, for example, a pure cross flow may be appropriate.
  • the block 5 is flowed through by a second flow medium 3 in the direction indicated by the arrow 7 flow direction, wherein the flow direction. 7 is substantially transverse to the end surface 6.
  • the second heat medium 3 is the air to be cooled by the evaporator 5.
  • the second heat medium 3 When flowing through the block 5, the second heat medium 3 first enters into the block 5 in the region of the front longitudinal edges 16 and is then guided past the flat tubes 4, 4 'on their surfaces 17, 18 for heat exchange. Subsequently, the second heat medium leaves the evaporator 1 in the region of the rear longitudinal edges 17 of the flat tubes 4, 4 '.
  • Fig. 2 shows a detail of a cross-sectional view through a block 5 (Fig. 1), in which a plurality of mutually parallel flat tubes 4, 4 'is provided, in the direction of the block depth t in each case from a front longitudinal edge 16 to a rear longitudinal edge 17th extend.
  • Due to the inclination receives the second heat medium 3 between the flat tubes 4, 4' a deflected flow direction eighth having a component inclined to the end face 6 and transverse to the longitudinal axis 10.
  • the arrangement of a filling body 28 on the side of the outermost flat tube 4 "also ensures an adjacent flow on the outermost flat tube 12.
  • the flat tubes 4, 4 ', 4" have in their cross-section an approximately angular waveform with one respective shaft 13 in the region of the front and the rear longitudinal edge 16, 17 on.
  • the two shafts 13 are formed such that the two side surfaces 15, 18 of the flat tubes 4, 4 ', 4 "in the region of Longitudinal edges 16, 17 are approximately perpendicular to the end face 6.
  • the flat tubes 4, 4 ', 4 "furthermore have longitudinal ribs 20, 20', 21, 21 'running approximately parallel to the longitudinal axis 10 on their two lateral surfaces 15, 17, which intermesh with one another at a distance described in more detail below in connection with FIG.
  • the convex side 12 of a shaft 13 of a flat tube 4 engages in the concave side 14 of the corresponding shaft 13 of the adjacent flat tube 4 'at a distance.
  • the air flowing in transversely to the plane E along the flow direction 7 is deflected between the flat tubes 4, 4 'in a flow direction 8 such that the flow direction 8 has a component inclined to the plane E.
  • the variant of flat tubes 4, 4 'shown in FIG. 4 has at its side surfaces 15, 15', 18, 18 'means 19 for enlarging the heat-transferring surface of the flat tubes 4, 4' and the flow path of the second heat medium 3.
  • the means 19 consist of a number of longitudinal ribs 20, 20 ', 21, 21' arranged parallel to the longitudinal axis 10 (FIGS. 1, 2).
  • the longitudinal ribs 20, 21 and the longitudinal ribs 20 ', 21' of the corresponding flat tube 4, 4 ' arranged in pairs opposite one another. This results in the region of the longitudinal ribs 20, 21, or 20 ', 21', a thick area 36, while the flat tubes 4, 4 'in the area have a thin area 34 between them.
  • the flat tubes 4, 4 ' have an angled waveform, each having a central shaft tip 13.
  • the waveform is symmetrical so that the front and rear longitudinal edges 16, 17 of the flat tubes lie on a line in the block depth direction indicated by an arrow 42.
  • the front and rear sections of the flat tubes 4, 4 'on both sides of the shaft tip 13 are arranged obliquely with respect to the plane E, that mutually each one longitudinal rib 20', 21 engages in the opposite gap 35.
  • the flat tubes 4, 4 ' have an identical design, wherein by the inclined position with respect to the plane E despite the cost-saving identical design and the pairwise opposed longitudinal ribs 20, 21 and 20', 21 'their mutual engagement in the opposite spaces 35 is possible , In addition to the flow deflection in the region of the longitudinal ribs 20, 20 ', 21, 21' and the associated intermediate spaces 35 also leads the inclination of the flat tubes 4, 4 'to a combined increase in the flow path of the second heat medium 3 and to increase the heat-transmitting surface of the Flat tubes 4, 4 '.
  • FIG. 5 shows in a perspective view schematically a variant of the arrangement according to FIG. 4 for an approximately rectangular arrangement with respect to the end face 6 in the region of the longitudinal edges 16, 17 (FIG. 2), with comparatively the embodiment of FIG Longitudinal ribs 20, 21 and 20 ', 21' are arranged in pairs.
  • the flat tubes 4, 4 'in the region of their front longitudinal edges 16 alternately each have a thick and a thin region 36, 34.
  • the longitudinal ribs 20, 20 ', 21, 21' distributed in the direction of the longitudinal axis 10 from the material of the flat tubes 4, 4 'peeled-out transverse ribs 23 are provided.
  • the mounting position of the flat tubes 4, 4 ' is selected with respect to the direction of the weight force 40 so that the transverse ribs 23 extend obliquely downwards in the direction of the force of gravity 40 and thus facilitate a drainage, for example, of condensed water.
  • FIG. 6 shows a cross-sectional view of a further variant of flat tubes 4, 4 ', in which the associated longitudinal ribs 20, 21 or 20', 21 'are offset relative to one another.
  • the width difference between the respective thin and thick regions 34, 36 is kept low.
  • a meander-shaped air duct 37 is formed in which the flow direction of the second heating medium indicated by the arrows 8 alternately with a component lying in the plane E of the end surface 6 (FIG is charged. This will be an extension the flow path and an enlargement of the heat transferring surface achieved.
  • Fig. 7 shows a further embodiment of a flat tube 4, from the flat side surfaces 15, 18 transversely to the longitudinal axis 10 extending transverse ribs 23 are peeled out as a means 19 for enlarging the heat-transmitting surface.
  • the transverse ribs 23 have a corrugated edge 24, wherein the corrugated edge 24 may be in the plane of the transverse ribs 23 or perpendicular thereto.
  • means 19 for enlarging the heat-transferring surface in the form of projections 22 are provided on its side surfaces 15, 18. 9 shows, in a sectional illustration through the projections 22, that in the spaces between them further projections 22 'of a not shown, adjacent flat tube 4' engage.
  • the projections 22, 22 ' have to reduce the flow resistance on an aerodynamic cross-section, which is elliptical in the embodiment shown, but may also be oval, diamond-shaped or the like.
  • the projections 22, 22 ' create a mutual division and merging of the air flow along the arrows 8 for improved mixing and for improved heat transfer.
  • the deflected flow direction 8 has a component which increases the flow path and which lies parallel to the longitudinal axis 10.
  • the flow direction 8 may comprise components which lie in any direction with respect to the plane E, and whereby an adapted Extension of the flow path for the heat medium 3 is made possible.
  • the exemplary embodiments of flat tubes 4, 4 'shown in FIGS. 2 to 8 are manufactured in one piece from aluminum by means of extrusion and are designed as multi-chamber tubes with individual channels 26 for the first heat medium 2.
  • flat tubes 4, 4 'shown in FIGS. 2 to 8 are manufactured in one piece from aluminum by means of extrusion and are designed as multi-chamber tubes with individual channels 26 for the first heat medium 2.
  • sheet metal expedient either as a tube with welded longitudinal seam or as disk elements formed from sheet metal shells.
  • FIG. 10 An embodiment of the latter form is shown in Fig. 10 schematically in cross section.
  • the flat tubes 4, 4 ' are formed by two joined half-shells 43, 44 of sheet metal.
  • the two half-shells 43, 44 are shaped such that in each case two chambers 45 are formed as channels 26 for the flow through the first heat medium 2.
  • the direction of the block depth t corresponding to FIG. 1 is indicated by the arrow 42.
  • a plurality of struts 41 are provided, which pass through the flat tubes 4, 4'.
  • the struts 41 also form projections 22, 22 'in the sense of FIGS. 8 and 9, which extend from one side surface 15, 18 to the adjacent side surface 18', 15 '.
  • the struts 41 both from the second heat medium 3 in the direction of arrows 8 as shown in FIG. 9 as Also flows through the first heat medium 2 within the channels 26 in the direction of the arrows 27 of FIG.
  • the illustrated variants of surface and Strömungswegver Strukturrnden means 19 in the form of longitudinal ribs 20, 20 ', 21, 21' and in the form of projections 22 and transverse ribs 23 are integrally formed with the respective walls 25 of the flat tubes 4, 4 '.
  • the projections 22, in particular in connection with the sheet-metal shell construction shown in Fig. 10 can be integrally formed by embossing the half-shells 43, 44. However, it may also be a separate production and subsequent attachment, for example by cohesive connection appropriate.

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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)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Claims (16)

  1. Evaporateur d'une installation de climatisation dans un véhicule automobile, pour la transmission de chaleur entre un premier et un second fluides de chaleur (2, 3) avec un certain nombre de tubes plats (4, 4') formant un bloc (5), à travers lesquels le premier fluide de chaleur (2) circule et qui sont disposés essentiellement parallèlement entre eux, de sorte que des canaux pour le second fluide de chaleur (3) entrant sur une face frontale (6) du bloc (5) sont formés entre les tubes plats (4, 4') respectivement voisins, la surface frontale (6) étant perpendiculaire à une direction d'écoulement du deuxième fluide de chaleur (3) caractérisé en ce que les tubes plats (4, 4') sont agencés en direction de la profondeur du bloc (t) au moins sur un tronçon partiel en formant un angle (α) par rapport à la face frontale (6) du bloc (5) l'angle (α) étant dans une plage comprise entre 25° et 65°.
  2. Evaporateur selon la revendication 1,
    caractérisé en ce que l'angle (α) est d'environ 45°.
  3. Evaporateur selon la revendication 1 ou 2,
    caractérisé en ce que les tubes plats (4, 4') présentent en section (11) à peu près une forme d'onde.
  4. Evaporateur selon la revendication 3,
    caractérisé en ce que la forme d'onde est réalisée à peu près de façon anguleuse.
  5. Evaporateur selon la revendication 3,
  6. Evaporateur selon l'une quelconque des revendications 3 à 5,
    caractérisé en ce que la forme d'onde est réalisée de telle sorte que les faces latérales (15, 18) du tube plat (4) sont agencées à peu près perpendiculairement à la face frontale (6) à proximité d'une arête longitudinale (16, 17) et en particulier dans le raccordement direct des deux arêtes longitudinales (16, 17).
  7. Evaporateur selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que, sur les faces latérales (15, 15', 18, 18') des tubes plats (4', 4), il présente des moyens (19) pour l'agrandissement de la surface de transmission de chaleur et/ou du chemin d'écoulement du second fluide de chaleur (3).
  8. Evaporateur selon la revendication 7,
    caractérisé en ce que les moyens (19) sont réalisés d'une seule pièce avec une paroi (25) du tube plat (4).
  9. Evaporateur selon la revendication 7 ou 8,
    caractérisé en ce que les tubes plats (4, 4') présentent des nervures longitudinales (20, 20', 21, 21') décalées les unes par rapport aux autres sur deux faces latérales (15', 18) contiguës entre elles.
  10. Evaporateur selon l'une quelconque des revendications 7 à 9,
    caractérisé en ce que des saillies (22, 22'), en particulier avec une section aérodynamique, sont prévues sur la face latérale (15, 15', 18, 18').
  11. Evaporateur selon la revendication 10,
    caractérisé en ce que les saillies (22, 22') sont réalisées depuis une face latérale (18, 15) jusqu'à la face latérale (15', 18') voisine du tube plat (4, 4') suivant respectif et sont réalisées en particulier sous la forme de montant (41) traversant plusieurs tubes plats (4, 4').
  12. Evaporateur selon la revendication 8 ou 9,
    caractérisé en ce que des nervures transversales (23) formées à partir du matériau du tube plat (4) sont prévues sur la face latérale (15, 18).
  13. Evaporateur selon la revendication 12,
    caractérisé en ce que les nervures transversales (23) présentent une arête (24) ondulée.
  14. Evaporateur selon l'une quelconque des revendications 1 à 13,
    caractérisé en ce que les tubes plats (4, 4') sont réalisés sous la forme de tubes à plusieurs chambres avec des canaux (26) individuels pour le premier fluide de chaleur (2).
  15. Evaporateur selon l'une quelconque des revendications 1 à 14,
    caractérisé en ce que les tubes plats (4, 4') sont fabriqués à partir d'une tôle en métal léger.
  16. Evaporateur selon l'une quelconque des revendications 1 à 14,
    caractérisé en ce que les tubes plats (4, 4') sont fabriqués par extrusion et/ou fluage d'un métal léger, en particulier de l'aluminium, ou d'un alliage d'aluminium.
EP02006050A 2001-03-28 2002-03-16 Echangeur de chaleur Expired - Lifetime EP1248063B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10115513A DE10115513A1 (de) 2001-03-28 2001-03-28 Wärmeübertrager
DE10115513 2001-03-28

Publications (2)

Publication Number Publication Date
EP1248063A1 EP1248063A1 (fr) 2002-10-09
EP1248063B1 true EP1248063B1 (fr) 2006-06-28

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Application Number Title Priority Date Filing Date
EP02006050A Expired - Lifetime EP1248063B1 (fr) 2001-03-28 2002-03-16 Echangeur de chaleur

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EP (1) EP1248063B1 (fr)
AT (1) ATE331928T1 (fr)
DE (2) DE10115513A1 (fr)

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WO2013085771A1 (fr) * 2011-12-08 2013-06-13 Carrier Corporation Procédé et appareil de formation de tubes d'échangeur de chaleur
WO2019026239A1 (fr) * 2017-08-03 2019-02-07 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle frigorifique
DE102018131026A1 (de) 2018-12-05 2020-06-10 Volkswagen Aktiengesellschaft Wärmeübertrager für ein Fahrzeug, insbesondere ein Elektrofahrzeug
FR3104690B1 (fr) * 2019-12-13 2022-08-26 Valeo Systemes Thermiques Echangeur de chaleur et procédé de fabrication d’un tel échangeur

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DE19740114A1 (de) * 1997-09-12 1999-03-18 Behr Gmbh & Co Wärmetauscher
DE19845336A1 (de) * 1998-10-01 2000-04-06 Behr Gmbh & Co Mehrkanal-Flachrohr
WO2002016834A2 (fr) * 2000-08-21 2002-02-28 Engineered Dynamics Corporation Ensemble echangeur thermique et procede permettant de transferer efficacement la chaleur

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DE10115513A1 (de) 2002-10-10
DE50207351D1 (de) 2006-08-10
EP1248063A1 (fr) 2002-10-09
ATE331928T1 (de) 2006-07-15

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