EP1573259A1 - Echangeur thermique - Google Patents

Echangeur thermique

Info

Publication number
EP1573259A1
EP1573259A1 EP03779838A EP03779838A EP1573259A1 EP 1573259 A1 EP1573259 A1 EP 1573259A1 EP 03779838 A EP03779838 A EP 03779838A EP 03779838 A EP03779838 A EP 03779838A EP 1573259 A1 EP1573259 A1 EP 1573259A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
flow
planes
segment
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.)
Withdrawn
Application number
EP03779838A
Other languages
German (de)
English (en)
Inventor
Martin Kaspar
Gerrit WÖLK
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 EP1573259A1 publication Critical patent/EP1573259A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28D2021/0084—Condensers

Definitions

  • the invention relates to a heat exchanger, in particular a condenser or gas cooler for air conditioning systems, in particular for motor vehicles, preferably according to the preamble of patent claim 1.
  • Capacitors have become known from EP-B 0 414 433, in which two capacitors are arranged one behind the other on the air side and are mechanically connected to one another by additional fastening elements.
  • the two condensers On the refrigerant side, the two condensers are flowed through either in series or in parallel. When connected in series, the heat exchange takes place in cross-counterflow, ie the leeward condenser is first flowed through, the refrigerant then passes through a connecting line into the windward condenser and flows through it to the refrigerant outlet located on the windward side. Both condensers are flowed through with multiple flows with a decreasing flow cross-section (degressive circuit).
  • Duplex condenser is that two condensers must be connected to each other both mechanically and on the refrigerant side, which requires additional components and assembly time. This means increased manufacturing costs.
  • the known capacitor also has thermodynamic potential, since it is not optimally flowed through. It is an object of the present invention to improve a heat exchanger, in particular gas cooler or condenser, of the type mentioned at the outset in such a way that the power is increased with the same end face and / or the weight and / or the production costs are reduced.
  • the heat exchanger according to the invention such as, in particular, a condenser or gas cooler, is preferably produced as an integral block which is preferably soldered “in one shot”. This eliminates mechanical connecting parts and reduces the manufacturing costs.
  • the condenser is in the plane or in the levels of the flow channels, i.e. in the width, in blocks and / or perpendicular to the levels, i.e. in the depth, divided into segments which are flowed through in succession, both a deflection in the depth or in the width and both in the This division of the two-row condenser network results in optimal flow-through possibilities on the refrigerant side, which results in an increase in the performance of the condenser.
  • each block consists of two segments with the same number of flow channels.
  • the number of segments can also be odd, namely when one segment (or more than one) is divided into sub-segments through which refrigerant flows in succession. This increases the flow through the condenser, which enables additional performance increases.
  • the refrigerant inlet is arranged on a leeward or windward side segment and the refrigerant outlet on a windward or leeward side segment.
  • the individual segments are flowed through one after the other in such a way that the refrigerant is alternately deflected in depth and in width. This results in a cross-countercurrent flow for the heat exchange between air and refrigerant.
  • a deflection in depth results in a simultaneous deflection in depth and in width. This results in a cross-countercurrent for the heat exchange between air and refrigerant, which brings further thermodynamic advantages.
  • the flow channels are designed as flat tubes, either in two, three or more rows or in a row, with the “continuous” flat tube being flowed through in two-flow, three-flow or multiple flow.
  • the flat tubes may have inner ones arranged in parallel Channels through which flow flows in parallel. These channels can also have connecting openings to one another. These flat tubes can also have turbulence inserts which are introduced into the flat tube.
  • the flat tube ends are fastened in a manifold common to more than one flat tube, in which the deflection takes place at depth.
  • An advantageous solution is also when the flat tube ends on the other side open into two header tubes, in which the deflection takes place in the width.
  • the two header pipes are either formed in one piece and thus hold the block together or are designed as separate header pipes which are held together by the "continuous" flat tubes.
  • continuous corrugated fins are arranged between the flat tubes, which due to their soldering to the Flat tubes ensure a compact, stable condenser block.
  • FIG. 9 shows a performance diagram for a heat exchanger according to the invention, such as a condenser, in comparison with the prior art.
  • FIG. 1 shows a two-row heat exchanger 1, such as a condenser or gas cooler, with a first row 2 and a second row 3 of flat tube ren 4, 4 known corrugated fins, not shown, are arranged between the flat tubes.
  • a two-row heat exchanger such as a condenser or gas cooler
  • the fin height of the corrugated fins is advantageously 4 mm to 12 mm.
  • the rib density that is to say the number of ribs per decimeter, is advantageously in the range from 45 to 95 ribs / dm, which corresponds to a rib spacing or a rib pitch of 1.05 to 2.33 mm.
  • the fin or corrugated fin can advantageously be used from a band in which the band is inserted in waves or zigzag form between the flat tubes.
  • the fin designed in this way will expediently have a thermal separation between different regions, so that the regions which are arranged between different flat tubes or flat tube regions are at least partially insulated thermally.
  • the rib can also consist of several individual strips which are inserted between the respective adjacent flat tubes. It is advantageous that the individual ribs of different rows have no thermal connection.
  • the flat tubes are advantageously designed in such a way that the tube width, that is to say the extension of the tubes in the direction of an adjacent tube of the same planes, is in the range from 1 mm to 5 mm, in particular advantageously from 1.2 mm to 3 mm.
  • the expansion of the tubes in the direction perpendicular to the planes, the tube depth is expediently in the range from 3 mm to 20 mm, advantageously in the range from 5 mm to 10 mm.
  • the pipe depth can be substantially the same for the blocks of the heat exchanger. In another exemplary embodiment of the invention, however, the tube depth can also be selected differently from block to block. It is particularly expedient if the pipe depth in the windward plane is less than the pipe depth in the leeward plane.
  • the tubes of different levels viewed in the direction of air flow, are arranged one behind the other, that is to say they are arranged one behind the other at the same height.
  • the tubes of one level can be arranged offset with respect to the tubes of a further level. This staggered arrangement can preferably take place up to half the height of the ribs plus half the width of the tube. Intermediate values can also be assumed. In such an embodiment, different or identical fins can be used between the tubes of different levels, which are advantageously designed as independent bands.
  • the flat tubes 4 of both rows 2, 3 have flat tube ends 4a which open into a common header tube 5.
  • the flat tubes 4 of both rows 2, 3 have flat tube ends 4b, which open into two separate header tubes 6, 7.
  • the header pipe 7 has a refrigerant inlet 8.
  • Both manifolds 6, 7 are divided into manifold sections by partitions, of which a partition 9 is shown only in manifold 6, which is shown open.
  • the air flows through the condenser in the direction of arrow L, the air flow direction.
  • the flow of the refrigerant in the condenser 1 is shown by a multi-angled line, starting with the refrigerant inlet KME and ending with the refrigerant outlet KMA.
  • the two rows 2, 3 of the flat tubes 4 are divided into three blocks 1, II, III, each block being divided into two segments 1 a, 1 a, 1 b; lla, llb and purple, lllb is divided.
  • the refrigerant therefore first flows through the leeward segment la of the rear tube row 3, then reaches the header tube 5, where it is deflected in depth, represented by the arrow UT1, then reaches the windward segment Ib and the windward header tube 6, where it is redirected in width, represented by the arrow UB1.
  • the refrigerant then flows through the next segment 11a back into the collecting tube 5, where it is again deflected in depth, but in the opposite direction as before, according to the arrow UT2.
  • FIG. 2 shows a further exemplary embodiment of a capacitor 10 which is constructed essentially the same as the capacitor 1 according to FIG. 1, the same reference numbers being used for the same parts.
  • the condenser 10 has an additional partition 11 in the windward-side manifold 6 and two tubular deflection members 12, 13, which each connect sections of the windward-side manifold 6 to sections of the leeward-side manifold 7.
  • the refrigerant flow path is again represented by a continuous, multi-angled line, starting at the refrigerant inlet KME and ending at the refrigerant outlet KMA.
  • the refrigerant thus first flows through the leeward-side segment la, is deflected in depth in the collecting tube 5 in accordance with the arrow UT1 in the direction of the wind-side segment Ib and flows through it until the wind-up side collecting tube 6 is reached. Due to the position of the partition 11, the segments la and lb of the block I six flat tubes 4. Via the deflecting element 12, the refrigerant is then deflected into a section of the leeward collecting tube 7, i. H. there is a simultaneous deflection both in width and in depth, which is shown by the arrow UBT1. After this deflection, the refrigerant flows. through the leeward segment llb in
  • Fig. 3 shows the formation of the two manifolds 6, 7, here 6 ', T, to form a glasses-shaped double tube 14.
  • the two manifolds 6', 7 ' are formed from a continuous sheet metal strip 15 with end edges 16, 17, which in a web 18 connecting both manifolds 6 ', 7' is inserted and soldered to it. This results in a firm connection between the two manifolds 6 ', 7', which receive the flat tubes 4 with their flat tube ends 4b. This enables the production of the two-row capacitor in a soldered block.
  • Fig. 4 shows a further embodiment for the formation of the manifolds 6, 7, here called 6 ", 7", which are designed as separate manifolds.
  • Flat tubes here are not arranged in two separate rows - as in the previous exemplary embodiments - but are formed by a "continuous" flat tube 19 which is flowed through in two passages, ie in a front (windward side) area 19a and a rear (leeward side) area 19b.
  • the two areas 19a, 19b are separated from each other in terms of flow by a central separating area 19c.
  • the continuous flat tube 19 has separate flat tube ends 19a 'and 19b' which are inserted into passages 20 of the two header tubes 6 ", 7" and soldered to them This also results in a coherent, compact, soldered capacitor block.
  • FIG. 5 shows a schematic representation of the flow pattern of the exemplary embodiment according to FIG. 1, ie a cross countercurrent.
  • the entire network of capacitor 1 according to FIG. 1 is divided into three blocks I, II, III, each block consisting of two segments Ia and Ib, Ila and IIb and llla and lllb exists.
  • the segments of a block each have the same number of tubes and are located one behind the other in the air flow direction L.
  • the segments 1a, 1b each have nine flat tubes 4, the segments 11a, 11b each have seven flat tubes and the segments purple, 11bb each have five flat tubes 4.
  • Embodiment of FIG. 1, d. H. the flow course has three deflections in depth UT1, UT2 and UT3 and two deflections in width UB1 and UB2.
  • Fig.2 is based, with the same alphanumeric names are adopted.
  • the network of the capacitor 10 (FIG. 2) is again divided into three blocks I, II and III in width, and each block is divided into two equal segments la, Ib; lla, ilb and lilac, lllb divided.
  • the number of tubes of block I is 2x nine, of block II 2x seven and of block III 2x five, so as in the previous embodiment.
  • the deflection in the depth takes place with the same segments in the same direction, i. H. against the air flow direction L in the direction of arrows UT1, UT2 and UT3.
  • FIG. 7 shows a further flow pattern in which the network of the capacitor is divided in width into two blocks I, II.
  • the block I is divided into two equal segments la and Ib in depth, each of which has nine flat tubes 4.
  • Block II is in a segment 11b with nine flat tubes 4 and two subsegments Ilaa with five flat tubes 4 and a subsegment Hab with four flat tubes.
  • the refrigerant flows through the leeward side segment la, then there is a deflection in depth, according to the arrow UT1, then the windward segment Ib is flowed through, then there is a deflection in the width, according to the arrow UB1, into the adjacent sub-segment llaa, then a redirection in depth UT2 to the leeward segment Ilb and from there another redirection in depth, according to arrow UT3, to the windward subsegment Hab.
  • the division of a segment into two subsegments results in five flow paths, that is, an odd number.
  • Such a variant with sub-segments can be particularly advantageous for subcooling the refrigerant in the last sub-segment Hab.
  • a partition in the manifold is advantageously used.
  • This partition can expediently be designed as a partition plate.
  • FIG. 8 shows a further variant of the division of the capacitor network into seven flow paths.
  • the width of the network is divided into three blocks I, II, III; block I- is divided into two identical segments 1 a, 1 b with nine flat tubes 4 each.
  • Block II is divided into two identical segments Ha, Ilb, each with seven flat tubes
  • block III is divided into a segment purple with seven flat tubes and two subsegments lllba with four flat tubes, and a further subsegment lllbb with three flat tubes.
  • the refrigerant is routed between the segments mentioned in the order of the following arrows: UT1, UB1, UT2, UB2, UT3 and UB3.
  • FIG. 9 shows a performance comparison of the capacitors according to the invention with the prior art with variable air inflow velocity in m / s on the abscissa. The power of the capacitor in kW is plotted on the ordinate.
  • the solid line S represents the performance of a conventional, multi-flow serpentine condenser with a degressive circuit.
  • the first variant of the invention according to FIG. 1 is shown as a narrowly dotted line and is marked with KGG, which stands for cross-countercurrent.
  • the second variant of the invention according to FIG. 2 is shown as a wide-dotted line and labeled KG, which stands for cross-countercurrent. It can be seen that the two inventive variants are significantly more powerful than the prior art, variant 2 being superior to variant 1 at higher air velocities. This results in a clear advantage in favor of the inventive division of the capacitor network into blocks and segments with deflection in depth.
  • the curves S, KGG, KG shown result from calculations for capacitors with the same end face and the same fin density.
  • the heat exchanger can be flowed through from top to bottom or from bottom to top. Bottom and top are defined by the installation position of the heat exchanger. For example, one level of the heat exchanger can also be flowed through from bottom to top and another level from top to bottom.
  • the flow channels are preferably arranged horizontally.
  • the flow channels are expediently aligned vertically and the header tubes are aligned horizontally.

Abstract

L'invention concerne un échangeur thermique, notamment un condenseur ou un système de réfrigération de gaz pour installations de climatisation, en particulier pour automobiles, qui comprend au moins deux rangées (2, 3) de canaux d'écoulement qui peuvent être parcourus par un agent de refroidissement et sont reçus en sortie, dans des tubes collecteurs (5, 6 7). Il est prévu des ailettes au-dessus desquelles l'air peut passer et qui sont disposées entre les canaux d'écoulement. Des canaux individuels d'écoulement (4) sont disposés sur une rangée, au moins deux rangées (2, 3) de canaux d'écoulement (4) sont répartis en au moins deux blocs (1, 11) dans le plan et chaque bloc est réparti, perpendiculairement aux plans, en au moins deux segments (1a, 1b ; 11a, 11b) de canaux d'écoulement (4). Il s'effectue entre lesdits segments, une déviation par rapport aux plans (UT1, UT2) ou une déviation dans le plan (UB1, UB2) ou une déviation, aussi bien dans le plan qu'également perpendiculairement au plan /UBT1, UBT2).
EP03779838A 2002-12-10 2003-11-03 Echangeur thermique Withdrawn EP1573259A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10257767A DE10257767A1 (de) 2002-12-10 2002-12-10 Wärmeübertrager
DE10257767 2002-12-10
PCT/EP2003/012224 WO2004053411A1 (fr) 2002-12-10 2003-11-03 Echangeur thermique

Publications (1)

Publication Number Publication Date
EP1573259A1 true EP1573259A1 (fr) 2005-09-14

Family

ID=32336192

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03779838A Withdrawn EP1573259A1 (fr) 2002-12-10 2003-11-03 Echangeur thermique

Country Status (10)

Country Link
US (1) US20050205244A1 (fr)
EP (1) EP1573259A1 (fr)
JP (1) JP2006509182A (fr)
KR (1) KR20050084778A (fr)
CN (1) CN1723378A (fr)
AU (1) AU2003287988A1 (fr)
BR (1) BR0309404A (fr)
DE (1) DE10257767A1 (fr)
MX (1) MXPA04010517A (fr)
WO (1) WO2004053411A1 (fr)

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DE10257767A1 (de) 2004-06-24
US20050205244A1 (en) 2005-09-22
WO2004053411A1 (fr) 2004-06-24
JP2006509182A (ja) 2006-03-16
AU2003287988A1 (en) 2004-06-30
KR20050084778A (ko) 2005-08-29
CN1723378A (zh) 2006-01-18
MXPA04010517A (es) 2004-12-13

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