EP1794528B1 - Echangeur de chaleur, notamment pour automobile - Google Patents

Echangeur de chaleur, notamment pour automobile Download PDF

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Publication number
EP1794528B1
EP1794528B1 EP05794801A EP05794801A EP1794528B1 EP 1794528 B1 EP1794528 B1 EP 1794528B1 EP 05794801 A EP05794801 A EP 05794801A EP 05794801 A EP05794801 A EP 05794801A EP 1794528 B1 EP1794528 B1 EP 1794528B1
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EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
tubes
flow
designed
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
EP05794801A
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German (de)
English (en)
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EP1794528A1 (fr
Inventor
Walter Demuth
Wolfgang Geiger
Martin Kotsch
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
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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.)
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Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1794528A1 publication Critical patent/EP1794528A1/fr
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Publication of EP1794528B1 publication Critical patent/EP1794528B1/fr
Not-in-force 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • 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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Definitions

  • the invention relates to a heat exchanger, in particular for a motor vehicle according to the preamble of claim 1 .
  • the applicant has a heat exchanger, in particular for a motor vehicle is known, which is characterized by a pressure-stable construction, as it finds particular use in CO2-powered air conditioning.
  • the pipes through which the refrigerant can flow are designed as multi-chamber flat tubes which communicate with collecting and / or distributing devices as well as deflecting devices.
  • the collection and / or distribution facilities are characterized by a pressure-stable plate construction, which essentially consists of a bottom plate, a distribution plate and a cover plate.
  • the refrigerant, R744 is guided in the known heat exchanger in various ways through the tubes, with basically deflections in the width (parallel to the end face) and in the depth (in or against the flow direction of the air) are possible.
  • a disadvantage of this heat exchanger is that the inlet and outlet channels or the refrigerant inlet and outlet are not optimally insulated from each other thermally, but rather are in heat-conducting connection via the common plates.
  • the WO 03/040640 discloses a heat exchanger with a collecting device, wherein the collecting device is formed as at least one C-profile with two legs and a web and the C-profile is closed by a bar arranged between the legs.
  • the collecting and / or distribution device is designed as at least one C-profile, which is closed by an inserted rake.
  • the C-profile can be supplied as a semi-finished product or folded out of a flat sheet metal.
  • the openings for receiving pipe ends, called passages, can easily pass through Punching or stamping are produced.
  • the rake, ie a bar with recesses in the region of the passages can be formed as a flat stamped part with arbitrary shapes, for. B. with tongue-shaped dividers, which extend into the C-profile and cause a subdivision of the C-profile into individual chambers.
  • the dividers which act as partitions, can be arranged at any point between the passages.
  • the C-profile is soldered to the rake and the pipe ends and thus represents a low-priced pressure-resistant solution.
  • two C-profiles are arranged at a distance next to each other for two rows of tubes, d. H. in the air flow direction one behind the other. Due to the distance between the two C-profiles, the advantage of a thermal separation, d. H. Heat is prevented from flowing from the higher temperature C-profile to the lower temperature C-profile, thereby degrading the efficiency of the heat exchanger.
  • deflection devices are provided on the side facing away from the C-profiles side of the block, which are preferably formed as a U-profile with an inserted wave profile, wherein in each case a "wave" forms a deflection chamber and two pipe ends together.
  • a deflection in the depth, preferably against the air flow direction, d. H. be effected to generate a countercurrent.
  • the first flow medium preferably carbon dioxide, therefore, initially enters a leeward C-profile, flows through a leeward row of pipes or leeward arranged flow channels, is deflected by the deflection opposite to the air flow direction and flows through a windward pipe row or flow channels until reaching the windward C-profile, where the refrigerant meanwhile has a considerably lower temperature than when entering. Due to the distance between the two C-profiles according to the invention, heat from the leeward C-profile can not flow to the windward C-profile and heat the refrigerant there again. This thermal separation thus has a particularly advantageous effect on gas coolers with falling or sliding temperature of the supercritical refrigerant.
  • the lee- and windward flow channels can be used as separate rows of tubes, z. B. be formed two rows of flat tubes or as a continuous flat tube with opposite flow-through flow channels.
  • the C-profile can also be used as a deflection by a bar between two legs is inserted, which may have either the shape of a rake or a plate with slots.
  • the slots are formed as slots and include the tube ends - they form in a double-row tube assembly a transfer channel from one to the other row of tubes.
  • stops for limiting the insertion depth of the tubes are provided on the strips, rakes or plates, and preferably designed as paragraphs, which engage over the pipe ends, preferably on the narrow sides thereof.
  • the tubes can be mounted in a simple manner always with the same insertion depth.
  • a parallel connection of the tubes be it possible for a two-row or a single-row arrangement.
  • both C-profiles can be divided by arranged on the rake dividers in two chambers, so that four chambers result for the entire heat exchanger, of which two are approximately diagonally opposite chambers connected by a transfer device.
  • the transfer means each have a breakthrough in the web portion of the C-profile and a Matterbergsteil which forms a connection or transfer channel between the two C-profiles.
  • the refrigerant thus enters the first leeward located chamber, flows through after deflection in depth the second luv table arranged chamber, then enters the third lee chrome located chamber and leaves the heat exchanger on the fourth luv faculty located chamber of the windward C-profile - so are refrigerant inlet and - exit approximately diagonally opposite, ie they are largely thermally isolated from each other (a thermally conductive connection exists only in the middle crossing area).
  • the soldered heat exchanger according to the invention can be used advantageously in particular as a gas cooler of a CO2 air conditioning system because the collecting, distributing and deflecting devices according to the invention are on the one hand pressure-resistant and on the other hand variable in terms of flow guidance and thus permit deflections of the refrigerant both in the width and in the depth, whereby an effective cooling of the refrigerant from entry to exit is possible.
  • Fig. 1 shows a section of a gas cooler 1 with a gas cooler block 2, consisting of flat tubes 3 and arranged between them corrugated fins 4.
  • the flat tubes 3 are arranged in two rows and soldered to the corrugated fins 4.
  • a C-profile 5 is attached, which has elongated openings 6, so-called passages, for receiving the tube ends of the flat tubes 3.
  • a Rake 7 used in the open side of the C-profile, which has in the region of the passages 6 recesses 7a for the pipe ends and a divider 7b.
  • the C-profile 5 has two legs 5a, 5b formed as flat sides, which are connected by a web 5c.
  • the C-profile can be made by folding from a flat sheet, with the passages 6 can be produced by stamping before folding.
  • Fig. 1a shows the rake 7 (partially) as a single part with the divider 7b, as he also in Fig. 1 is shown.
  • the C-profile which is soldered to the tube ends of the flat tubes 3 and the rake 7, forms a collection or distribution channel, which is interrupted by the divider 7b.
  • the C-profile 5 is closed at the end by an end web 7 c at the end of the rake 7.
  • Fig. 2 shows a cross section in the upper region of the gas cooler 1 with a first row of tubes I and a second row of tubes II.
  • the air flow direction is shown by an arrow L;
  • the row of tubes I is the leeward (downstream) and the tube row II, the windward (upstream).
  • the C-profile 5 and on the leeward tube row I is another C-profile 8 is arranged, which is also completed by a rake 9 to the outside and mirror image of the C-profile 5 with 7 rake.
  • Both C-profiles form flow channels 10, 11, which are interconnected by a transfer channel 12.
  • a T-shaped formed transition part 13 is inserted and soldered to the two C-profiles 5, 8.
  • the crossing channel 12 is - as shown in the drawing - formed by openings in the web areas of the C-profiles 5, 8 and the T-shaped crossing part 13.
  • Such a transition region is preferably arranged in the middle of the heat exchanger or in the middle region of the two C-profiles 5, 8, so that a passage of the refrigerant from the windward chamber 10 into the leeward chamber 11 is made possible.
  • a plurality of such transition areas can also be provided on a heat exchanger.
  • Fig. 3 shows the crossing area according to Fig. 2 in a view from above of the two C-profiles 5, 8, which are cut in the region of their webs 5c, 8c.
  • the distance a between the two C-profiles 5, 8 causes a thermal decoupling.
  • the front C-profile 5 is divided by the divider 7b of the rake 7 in two flow chambers 10, 14 and the rear C-section 8 through a divider 9b of the rake 9 in two flow chambers 11, 15.
  • the two separating webs 7b, 9b are arranged offset to one another, so that an overlap is formed between the chambers 10, 11, within which the transfer channel 12 is arranged, which is formed in the region of the distance a through the T-shaped transition part 13.
  • the flow chamber 15 is the inlet chamber for the refrigerant and the flow chamber 14, the outlet chamber for the refrigerant from the gas cooler 1.
  • the refrigerant inlet, not shown, and also not shown refrigerant outlet are thus almost diagonally opposite and have a maximum distance, which proves favorable for the efficiency of the gas cooler, in particular in conjunction with the thermal decoupling by the distance a of both C-profiles 5, 8th
  • Fig. 4 shows the C-profiles 5, 8 opposite side of the gas cooler 1 with a deflection device 16, which consists essentially of a U-profile 17 with a wave profile 18.
  • the U-profile 17 has a flat web portion 17a, which acts as a tube sheet and has punched passages 19 for receiving the tube ends of the flat tubes 3.
  • U-legs 17b, 17c are bent at right angles, which receive the wave profile 18 between them and are soldered tightly thereto.
  • the wave profile 18 has a multiplicity of "waves" 18a, 18b..., Which respectively form deflection chambers and communicate with tubes of the first and second tube rows I, II.
  • the wave profile 18 is on the one hand end face with the two legs 17b, 17c soldered and on the other hand with its not shown wave crests with the tube sheet 17a.
  • Fig. 5 shows a further embodiment of a deflecting device 20, which is designed as a C-profile 21 with two parallel legs 21a, 21b and a web 21c. Between the two legs 21 a, 21 b, a plate 22 is inserted, which has slots 23 in the form of slots. Within the slots open pipe ends 24, 25, which are through the lower leg 21 a, which acts as a tube sheet, are pushed through.
  • the block of the heat exchanger, consisting of tubes and fins, is not shown here.
  • At the leg 21 a facing side of the plate 22 paragraphs 26, 27 are arranged, which partially overlap the tube ends 24, 25 on their narrow sides and thus act as a limitation for the insertion depth of the tubes.
  • the elongated holes 23 form a transfer channel for the tubes 24, 25 or the first and the second row of tubes.
  • the assembly of the deflecting device 20 takes place in such a way that first the plate 22 is pushed into the gap between the two legs 21 a, 21 b and fixed in this position, which can be done positively or non-positively. Thereafter, the deflection device 20 is attached to the tube ends 24, 25 of the finished block, not shown, wherein the tube ends 24, 25 come with their upper edges in attack with the paragraphs 26, 27. Thereafter, the heat exchanger can be soldered.
  • Fig. 6 shows a further embodiment of a deflecting device 28 in a sectional view.
  • the C-profile 29 is shown here by dashed lines.
  • a plate 30 which on its underside four paragraphs 31a, 31b, 31c, 31d, which each overlap the narrow side upper edges of the two flat tubes 32, 33 and thus form a Einstecktiefenbegrenzung.
  • This arrangement with collecting channel 36 allows a parallel flow of the tubes 32, 33, ie in the same direction, as shown by the arrows P.
  • the exiting refrigerant is then supplied via the collecting channel 36 to the outlet of the heat exchanger.
  • Fig. 7 shows a heat exchanger 37 as a single-row system, ie with only one row of flat tubes 38, which are received by the lower leg 39 a of the C-profile 39.
  • a rake 40 - as described above - inserted.
  • the plate-shaped rake 40 has on its underside a shoulder 41 which engages over the narrow side of the pipe end 38 and thus forms a stop for (one-sided) limitation of the insertion depth.
  • the heat exchanger 37 can be completed by side parts, not shown, which are inserted with their ends by slots, not shown in the C-profile 39.
  • Fig. 8 shows a further embodiment of a single-row heat exchanger 42 with C-profile 43 and inserted plate 44, which has 45 slots in the form of slots 46 in the pipe ends.
  • paragraphs 47, 48 provided as a double-sided Einstecktiefenbegrenzung.
  • the invention is not limited to the refrigerant R747 (CO2), but also extends to heat exchangers, which are operated with the refrigerant R134a or R152.

Claims (27)

  1. Echangeur de chaleur (1) comprenant un bloc (2) se composant de tubes (3) et, en particulier, d'ailettes (4), où les tubes (3) sont traversés dans au moins une direction, par un premier milieu, et baignés par un deuxième milieu, et comprenant au moins un dispositif collecteur et / ou distributeur pour le premier milieu, dispositif qui est raccordé en communiquant avec les tubes (3), où le dispositif collecteur et / ou distributeur est configuré comme au moins un profilé (5) en C comportant deux branches (5a, 5b) et une partie pleine (5c), et en ce que le profilé (5) en C est fermé par une traverse (7) disposée entre les branches (5a, 5b),
    caractérisé en ce que des ouvertures (6) servant à loger des extrémités tubulaires des tubes (3) sont disposées dans l'une des deux branches (5b).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la traverse est configurée comme un râteau (7) comportant des évidements (7a) dans la zone des ouvertures (6) prévues pour les extrémités tubulaires.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que les tubes (3) présentent deux rangées (I, II), ou plus, d'extrémités tubulaires, et en ce qu'une rangée (I, II) est reliée, à chaque fois, à un profilé (5, 8) en C.
  4. Echangeur de chaleur selon la revendication 3, caractérisé en ce que les deux profilés (5, 8) en C sont disposés parallèlement l'un à l'autre et à distance (a) l'un de l'autre.
  5. Echangeur de chaleur selon la revendication 3 ou 4, caractérisé en ce qu'un profilé (5) en C est configuré comme un conduit d'entrée, le profilé voisin (8) en C étant configuré comme un conduit de sortie, et les tubes (3) sont traversés parallèlement, dans deux directions, en comportant un changement de direction dans la profondeur.
  6. Echangeur de chaleur selon la revendication 3, 4 ou 5, caractérisé en ce que les extrémités tubulaires placées à l'opposé des profilés (5, 8) en C sont raccordées à un dispositif déflecteur (16, 20, 28).
  7. Echangeur de chaleur selon la revendication 6, caractérisé en ce que le dispositif déflecteur (16) est configuré comme un profilé (17) en U comportant une partie pleine (17a) configurée comme un plateau à tubes servant au logement des extrémités tubulaires, et comportant deux surfaces latérales (17b, 17c) entre lesquelles est disposée une tôle déflectrice (profilé ondulé 18) configurée en ayant une forme ondulée.
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que le profilé ondulé (18) présente des peignes ondulés qui sont reliés au plateau à tubes (17a) pour former des chambres de déviation.
  9. Echangeur de chaleur selon la revendication 6, caractérisé en ce que le dispositif déflecteur (20, 28) est configuré comme un profilé (21, 29) en C dans lequel peut être introduite une traverse (22, 30).
  10. Echangeur de chaleur selon la revendication 9, caractérisé en ce que la traverse est configurée comme un râteau.
  11. Echangeur de chaleur selon la revendication 9, caractérisé en ce que la traverse est configurée comme une plaque (22) comportant des fentes, en particulier des trous oblongs (23) dans lesquels débouchent les extrémités tubulaires (24, 25).
  12. Echangeur de chaleur selon la revendication 9, 10 ou 11, caractérisé en ce que la traverse (22, 30) présente des butées (26, 27, 31a - 31d) servant à limiter la profondeur d'introduction des tubes (24, 25, 32, 33).
  13. Echangeur de chaleur selon la revendication 12, caractérisé en ce que les butées sont configurées comme des épaulements (26, 27, 31a - 31d) formés dans la traverse (22, 30), épaulements qui recouvrent partiellement les extrémités tubulaires (24, 25, 32, 33).
  14. Echangeur de chaleur selon la revendication 13, caractérisé en ce que les épaulements (26, 27, 31a - 31d) sont disposés dans la zone d'au moins l'un des petits côtés des tubes (24, 25, 32, 33).
  15. Echangeur de chaleur selon l'une quelconque des revendications 9 à 14, caractérisé en ce que la traverse (30) présente un conduit collecteur (36) pour du fluide frigorigène sortant des tubes (32, 33).
  16. Echangeur de chaleur selon l'une quelconque des revendications précédentes, en particulier selon la revendication 15, caractérisé en ce que les tubes sont disposés sur une ou deux rangées (32, 33) et traversés de façon parallèle.
  17. Echangeur de chaleur selon l'une quelconque des revendications 2 à 16, caractérisé en ce qu'au moins un profilé (5) en C est divisé, dans le sens longitudinal, par une ou plusieurs parties pleines séparatives (7b) disposées sur le râteau (7).
  18. Echangeur de chaleur selon la revendication 17, caractérisé en ce que les deux profilés (5, 8) en C sont subdivisés, dans le sens longitudinal, pour former quatre chambres (10, 11, 14, 15) ou plus, et en ce que deux chambres (10, 11) sont reliées, entre les profilés (5, 8) en C, par un conduit de trop-plein (12).
  19. Echangeur de chaleur selon la revendication 18, caractérisé en ce que le conduit de trop-plein (12) est formé, à chaque fois, par une ouverture dans les parties pleines (5c, 8c) et par une partie de trop-plein (13) disposée entre les parties pleines (5c, 8c).
  20. Echangeur de chaleur selon la revendication 19, caractérisé en ce que la partie de trop-plein (13), configurée en forme de T, présente une partie pleine en T comportant une ouverture de passage, et en ce que la partie pleine en T comble la distance a comprise entre les profilés (5, 8) en C.
  21. Echangeur de chaleur selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le premier milieu est un fluide frigorigène, en particulier du R744 (CO2), et le deuxième milieu, un gaz, en particulier de l'air.
  22. Echangeur de chaleur selon la revendication 21, caractérisé en ce que l'échangeur de chaleur est configuré comme un refroidisseur de gaz (1) d'un système de climatisation fonctionnant avec du CO2.
  23. Echangeur de chaleur selon la revendication 21 ou 22, caractérisé en ce que le fluide frigorigène CO2 et l'air sont guidés l'un vers l'autre, dans le flux opposé croisé.
  24. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il peut être fabriqué par brasage.
  25. Echangeur de chaleur selon l'une quelconque des revendications 19 à 24, caractérisé en ce que la partie de trop-plein (13) est configurée en ayant une forme tubulaire.
  26. Echangeur de chaleur selon l'une quelconque des revendications 19 à 25, caractérisé en ce que la partie de trop-plein (13) s'engage dans au moins un profilé en C.
  27. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une chambre est formée dans au moins un profilé en C, chambre qui relie entre eux des tubes d'une première direction d'écoulement et des tubes ayant une seconde direction d'écoulement différente de la première, où la première et la seconde directions d'écoulement sont en particulier en sens inverse l'une par rapport à l'autre.
EP05794801A 2004-09-01 2005-09-01 Echangeur de chaleur, notamment pour automobile Not-in-force EP1794528B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004042677 2004-09-01
PCT/EP2005/009426 WO2006024528A1 (fr) 2004-09-01 2005-09-01 Echangeur de chaleur, notamment pour automobile

Publications (2)

Publication Number Publication Date
EP1794528A1 EP1794528A1 (fr) 2007-06-13
EP1794528B1 true EP1794528B1 (fr) 2010-03-31

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05794801A Not-in-force EP1794528B1 (fr) 2004-09-01 2005-09-01 Echangeur de chaleur, notamment pour automobile

Country Status (4)

Country Link
EP (1) EP1794528B1 (fr)
AT (1) ATE462948T1 (fr)
DE (1) DE502005009327D1 (fr)
WO (1) WO2006024528A1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137037A1 (de) * 1991-07-02 1993-01-14 Thermal Waerme Kaelte Klima Sammler fuer einen flachrohrverfluessiger
FR2793015B1 (fr) * 1999-04-28 2001-07-27 Valeo Thermique Moteur Sa Echangeur de chaleur brase pour haute pression, en particulier pour vehicule automobile
WO2003040640A1 (fr) * 2001-11-08 2003-05-15 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
US7418999B2 (en) * 2002-05-31 2008-09-02 Zexel Valeo Climate Control Corporation Heat exchanger
AU2003269545B2 (en) * 2002-12-31 2006-04-27 Modine Korea, Llc Evaporator
DE102004003789A1 (de) * 2004-01-23 2005-08-18 Behr Gmbh & Co. Kg Wärmetauscher

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Publication number Publication date
WO2006024528A1 (fr) 2006-03-09
EP1794528A1 (fr) 2007-06-13
DE502005009327D1 (de) 2010-05-12
ATE462948T1 (de) 2010-04-15

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