EP3048407B9 - Fluide caloporteur - Google Patents

Fluide caloporteur Download PDF

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Publication number
EP3048407B9
EP3048407B9 EP15202230.7A EP15202230A EP3048407B9 EP 3048407 B9 EP3048407 B9 EP 3048407B9 EP 15202230 A EP15202230 A EP 15202230A EP 3048407 B9 EP3048407 B9 EP 3048407B9
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EP
European Patent Office
Prior art keywords
flow
heat exchanger
structural elements
variable
winglets
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.)
Active
Application number
EP15202230.7A
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German (de)
English (en)
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EP3048407B1 (fr
EP3048407A1 (fr
Inventor
Peter Geskes
Ulrich Maucher
Michael Schmidt
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
Mahle Behr GmbH and Co KG
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Publication of EP3048407A1 publication Critical patent/EP3048407A1/fr
Publication of EP3048407B1 publication Critical patent/EP3048407B1/fr
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Publication of EP3048407B9 publication Critical patent/EP3048407B9/fr
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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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/14—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by endowing the walls of conduits with zones of different degrees of conduction of heat
    • 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
    • F28F3/042—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 in the form of local deformations of 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
    • F28D2021/0082—Charged air coolers
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1 - known by the US 4,314,587 ,
  • V-shaped arranged structural elements are formed by non-cutting deformation of the wall of the exhaust pipes.
  • the V-shaped arranged structural elements also referred to as so-called winglets, can thus be economically, ie introduced at low cost in the exhaust pipes.
  • the density of the structural elements is variable, especially in the flow direction is increasing.
  • the heat transfer coefficient on the inside of the flow channel is variable, in particular, the heat transfer increases in the flow direction, while it is comparatively low or minimal in the inlet region of the flow.
  • the invention is based on the recognition that the heat dissipation in the inlet region of the flow channel-for example, to a cooling medium flowing around the flow channel-is greater than in the downstream region of the flow channel due to the high temperature difference prevailing there, and that a forming on the inner wall of the flow channel, in the flow direction growing temperature boundary layer in the inlet region is still relatively thin.
  • structural elements for increasing the heat transfer on the inside of the flow channel in favor of a reduced pressure drop in this area can be dispensed with in the inlet region.
  • the density of the structural elements is adapted to the conditions prevailing locally in the flow channel with respect to temperature difference and temperature boundary layer.
  • the structural elements are formed as swirl-generating indentations in the wall of the flow channel, as so-called winglets, as are known for exhaust gas heat exchangers according to the aforementioned prior art.
  • the arrangement and design of the winglets in the flow channel can be made variable according to the invention: thus, the distance of the winglets in the flow direction can increase continuously or gradually, as well as the height of the winglets, which extends into the flow. For manufacturing reasons, it is advantageous if the distances each amount to a multiple of the smallest distance. Further, the angle included by the V-shaped winglets can be increased continuously or stepwise in the flow direction, thereby also increasing the heat transfer, but also the pressure drop.
  • the inventive arrangement of structural elements with variable density, in particular for exhaust gas heat exchanger of internal combustion engines for motor vehicles is advantageously used.
  • Exhaust gas heat exchangers require on the one hand a high power density and on the other hand a low exhaust back pressure, so that the required EGR rates (proportion of the recirculated exhaust gas in the total exhaust gas flow) can be achieved to achieve the emission requirements.
  • the reduced pressure drop resulting from the invention thus has a particularly advantageous effect when used as an exhaust gas heat exchanger.
  • ribs in particular rib ribs are arranged as structural elements on the inside of the flow channel, which increase the heat transfer.
  • the rib elements have a density that is variable in the direction of flow, ie. H. preferably gradually increases in the flow direction, which in turn can be dispensed with in the inlet area entirely on a réelleberippung.
  • the change in density can advantageously be achieved in the case of a rib ridge by means of a variable longitudinal or transverse distribution or by a variable angle of attack for the flow. This also achieves the advantage of a reduced pressure drop.
  • further measures could be taken to increase the heat transfer, e.g.
  • the measures according to the invention are particularly advantageous in the inlet region of the respective flow channel, d. H. in the area of the flow, where there are still transient conditions with respect to the temperature difference and the thickness of the boundary layer.
  • the flow channels are designed as exhaust gas flows through and can be umströmbare exhaust gas from a coolant.
  • the structural elements, in particular the inner ribs have a rib density, which is variable in the flow direction, in particular in the flow direction (P) is increasing.
  • the rib ridge has a variable longitudinal division (t 1 , t 2 , t 3 , t 4 , t 5 t x ).
  • the smallest longitudinal pitch t x has a limit value t x > 0.3 H, where H is the channel height.
  • the rib ridge has a variable angle of attack ( ⁇ 1 , ⁇ 2 , ⁇ 3 ... ⁇ x ), wherein the angle of attack is preferably in the range of 0 ⁇ ⁇ 30 °.
  • the rib ridge has a variable transverse distribution (q 1 , q 2 , q 3 ... Q x ).
  • the transverse pitch q has a range of 8> q> 1 mm, preferably 5> q> 2 mm.
  • the inner rib has a longitudinal swivel with variable pitch (t 1 , t 2 , t 3 , t 4 ).
  • the pitch t of the inner rib has a range of 10 ⁇ t ⁇ 50 mm.
  • the flow channels are formed as tubes, in particular as tubes of a tube bundle.
  • the flow channels are formed as disks, in particular as disks of a disk package.
  • thermoelectric cooler for cooling combustion air for an internal combustion engine of a motor vehicle.
  • Fig. 1 shows a pipe 1 designed as a flow channel 2, which has an inlet cross-section 3 and is flowed through by a flow medium according to the arrow P.
  • the tube 1 is traversed by a hot exhaust gas of an internal combustion engine, not shown, and is part of a Abgastageübertragers not shown.
  • the tube 1 has a smooth inner side or inner wall 1a and an outer wall or outer wall 1b, which is cooled by a preferably liquid coolant.
  • the hot exhaust gas gives its heat over the Pipe 1 to the coolant.
  • a temperature boundary layer 4 forms on the inner wall 1a, which increases in its thickness d from the inlet cross-section 3 in the flow direction of the arrow P.
  • the temperature profile in this boundary layer 4 is represented by a temperature profile 5.
  • the temperature in the temperature boundary layer thus rises from a temperature Ta on the inner wall 1a to a temperature level Ti in the interior of the flow channel (core flow), which corresponds to the exhaust gas inlet temperature. Due to the growing temperature boundary layer 4, the heat transfer conditions in the inlet region of the tube 1 deteriorate.
  • Fig. 2 shows a diagram in which the heat transfer coefficient ⁇ is plotted as a relative size over the length l of a smooth-walled flow channel, ie from the inlet cross-section (reference numeral 3 in Fig. 1 ) in the flow direction of the flow medium.
  • the length l is plotted in millimeters.
  • Fig. 3a, 3b, 3c, 3d and 3e show a first embodiment of the invention with five different variants, namely the arrangement of structural elements with variable density.
  • Fig. 3a shows in a first variant, a schematically illustrated flow channel 6, preferably an exhaust pipe of a Abgastownschreibtragers not shown, wherein the exhaust pipe 6 is traversed according to the arrow P.
  • the outside of the exhaust pipe 6 is - what is not shown, but from the above-mentioned prior art is known - preferably lapped by a liquid coolant - but is also possible air cooling.
  • the exhaust pipe 6 is formed as a stainless steel tube, consisting of two halves welded together, with a rectangular cross-section.
  • the exhaust pipe 6 has an inlet region 6a, which is smooth-walled over a length L. Downstream of the smooth-walled region 6a, a region 6b adjoins, in which V-shaped arranged structural elements embossed from the tube wall 7, so-called winglets, are arranged.
  • the winglet pairs 7 are arranged in the section 6b at the same distance and in the same formation.
  • the transition from the smooth-walled region 6a to the winglets 7 occupied area 6b thus takes place in the form of a "step".
  • a sufficiently large heat transfer or heat transfer is achieved in the smooth-walled region 6a, since the temperature difference is still sufficiently large and the temperature boundary layer is relatively small.
  • the smooth-walled region 6a - this also applies to the following variants 3b, 3c, 3d, 3e - may have a length of up to 100 mm.
  • a rectangular tube 8 is shown in longitudinal section, which also has a smooth-walled inlet region 8a and a channel height H. Downstream of this smooth-walled region 8a winglet pairs 9 are arranged with equal distances a in the flow direction, but with different heights h: projecting into the flow cross-section of the exhaust pipe 8 heights h of the winglet pairs 9 grow continuously in the flow direction P. Thus, the heat transfer in This pipe section has been successively increased. At the same time, the pressure drop increases. The transition from smooth to not smooth is thus continuous. In a preferred embodiment, a range of 0.05 ⁇ h / H ⁇ 0.4 is selected for the ratio h / H.
  • a third variant according to Fig. 3c are in a tube 10 winglet pairs 11 with decreasing in the flow direction P distances a 1 , a 2 , a 3 arranged.
  • the heat transfer starting from the smooth inlet region 10a, successively increased, since the density of the structural elements or winglets 11 is greater.
  • the distances a 1 , a 2 , a 3 can each be a multiple of the minimum distance a x .
  • the latter is advantageously in a range of 5 ⁇ a x ⁇ 50 mm and preferably in a range of 8 ⁇ a x ⁇ 30 mm.
  • Fig. 3d shows a fourth variant for the arrangement of structural elements with different density in an exhaust pipe 12, which is permeable according to the arrow P of exhaust gas.
  • the smooth-walled entry region 12a is shorter in comparison to the previous embodiments.
  • This is followed by winglet pairs 13 with equal distances in the flow direction, but with different angles ⁇ (angle with respect to flow direction P).
  • the winglets of the upstream winglet pair 12 are aligned almost parallel ( ⁇ 0), while the angle ⁇ of the downstream winglet pair 13 formed by the winglets is about 45 degrees.
  • the intervening winglet pairs 13 have corresponding intermediate values, so that the heat transfer coefficient for the inner wall of the exhaust pipe 13 increases due to the increasing spreading of the winglets in the flow direction, continuously or in small steps.
  • the angle ⁇ is advantageously in a range of 20 ° ⁇ ⁇ 50 °.
  • Fig. 3e shows a fifth variant with an exhaust pipe 30, a smooth-walled portion 30a and adjoining rows of parallel winglets 31, which each form an angle ⁇ with the flow direction P.
  • the rows have in the flow direction P decreasing distances a 1 , a 2 , a 3 , wherein the angle ⁇ of the winglets 31 from row to row changes the sign.
  • a smooth area without structural elements is preferably left at the beginning of the tube and at the tube end, so that a clean separation point can be produced when the tubes are cut to length.
  • Fig. 4 shows a further embodiment of the invention for a flow channel 14, which is according to the arrow P flows of a flow medium - this may be, for example, a liquid coolant or charge air.
  • the outside of the flow channel 14 can be cooled by a gaseous or liquid cooling medium.
  • the flow channel 14 has a smooth-walled inlet region 14a, at which, in the flow direction P, a first region 14b provided with internal ribs 15 and, at the same time, another ribbed region 14c connects.
  • the regions 14b and 14c have a different fin density - in the illustrated embodiment, the rib density in the downstream region 14c is twice as large as in the upstream region 14b, since between the continuous ribs 15 further ribs 16 are arranged.
  • an increase of the heat transfer is also achieved, in stages from 14a to 14b to 14c.
  • Fig. 5 shows as a third embodiment of the invention, a gas flow channel in which a Stegrippe 17 with variable longitudinal pitch t 1 , t 2 , t 3 , t 4 , t 5 is arranged.
  • t 1 > t 2 > t 3 > t 4 > t 5 ie the heat transfer increases from t 1 to t 5 , ie in the flow direction P.
  • Web ribs are used in particular for intercoolers and are preferably soldered to the pipes.
  • the ratio of the smallest pitch t x to the channel height H has a limit of 0.3 ⁇ t x / H.
  • Fig. 6 shows a fourth embodiment of the invention, a gas flow channel in which a rib ridge 18 with variable angles of attack ⁇ 1 , a 2 , ⁇ 3 ... ⁇ x is arranged.
  • Advantageous angles of attack are in the range of 0 ⁇ ⁇ 30 °.
  • Fig. 7 shows a fifth embodiment of the invention, a gas flow channel in which a rib ridge 19 with variable transverse pitch q 1 , q 2 , q 3 ... q 6 is arranged, wherein the heat transfer with decreasing transverse division of q 1 in the direction q 6 , ie Flow direction P increases.
  • Advantageous areas for the transverse division q are 8>q> 1 mm and preferably 5>q> 2 mm.
  • Fig. 8 shows in a gas flow channel a corrugated in the flow direction P (deep waved) inner fin 20 with variable pitch t 1 , t 2 , t 3 , t 4 - the heat transfer increases here in the direction of decreasing pitch t.
  • Advantageous ranges for the pitch t are 10 ⁇ t ⁇ 50 mm.
  • a variation of the heat transfer in the flow channel also by further from the Prior art known means can be achieved, for example by placing gills or windows in the ribs.
  • other forms of structural elements for vortex generation or to increase the heat transfer can be selected.
  • the application of the invention is not limited to exhaust gas heat exchangers, but also extends to intercoolers whose tubes are flowed through by hot charge air, and generally to gas flow channels, which may be formed as tubes of a tube heat exchanger or as slices of Scheibennzoübertragers.

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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)
  • Exhaust-Gas Circulating Devices (AREA)

Claims (11)

  1. Echangeur de chaleur comprenant au moins un conduit d'écoulement pouvant être traversé par un milieu d'écoulement, depuis une section d'entrée jusqu'à une section de sortie, et présentant un côté intérieur et un côté extérieur, lequel conduit d'écoulement présente, sur le côté intérieur, des éléments de structure servant à l'augmentation du transfert de chaleur, où les éléments de structure (7, 9, 11, 13, 15, 16, 17, 18, 19, 20, 31) sont disposés et / ou configurés de façon variable, dans la direction d'écoulement (P), de manière telle que le conduit d'écoulement (6, 8, 10, 12, 14, 30) présente, sur le côté intérieur, un transfert de chaleur variable, augmentant en particulier dans la direction d'écoulement (P), où les éléments de structure (9, 11, 13, 15, 16, 17, 18, 19, 20, 31) présentent une résistance à l'écoulement par rapport au milieu d'écoulement et sont disposés et / ou configurés de manière telle, que la chute de pression soit variable dans le conduit d'écoulement (8, 10, 12, 14), en particulier minimale dans la zone d'entrée (6a, 8a, 10a, 12a, 14a, 30a), où les éléments de structure sont configurés comme des générateurs de tourbillons, ce que l'on appelle des winglets (7, 9, 11, 13, 31), caractérisé en ce que le conduit d'écoulement présente, à partir de la section d'entrée, une partie à paroi lisse sans structures, et en ce que les winglets (11, 31) sont disposées en rangées et forment, avec la direction d'écoulement (P), un angle β, où l'angle β présente pour des winglets adjacentes, un signe identique ou opposé.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la densité des éléments de structure (11; 15, 16; 19; 31) est variable, augmentant en particulier dans la direction d'écoulement (P).
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que la partie à paroi lisse (6a, 8a, 10a, 12a, 14a, 30a) présente, dans la direction d'écoulement (P), une longueur L, où L est ≤ 100 mm.
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les éléments de structure sont configurés comme un ailetage intérieur, comme des ailettes intérieures (15, 16, 20), des ailettes nervurées (17, 18, 19) et / ou comme des éléments rapportés créant des turbulences, et sont brasés en particulier dans les conduits d'écoulement.
  5. Echangeur de chaleur selon la revendication 1, 2, 3 ou 4, caractérisé en ce que les winglets (13, 31) forment, avec la direction d'écoulement (P), un angle β qui est variable, augmentant en particulier dans la direction d'écoulement (P).
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que l'angle β présente une plage de 20° < β < 50°.
  7. Echangeur de chaleur selon la revendication 1, 2, 3 ou 4, caractérisé en ce que les winglets (9) présentent une hauteur (h) en pénétrant dans l'écoulement, hauteur qui est variable, augmentant en particulier dans la direction d'écoulement (P).
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que le conduit d'écoulement (8) présente une hauteur H, et le rapport de h/H présente une plage de 0,05 ≤ h/H ≤ 0,4.
  9. Echangeur de chaleur selon la revendication 1, 2, 3 ou 4, caractérisé en ce que des winglets (11, 31) sont disposées en rangées agencées de manière transversale par rapport à la direction d'écoulement (P), et en ce que les rangées présentent un espacement (a1, a2, a3 ... ax) variable, diminuant en particulier dans la direction d'écoulement.
  10. Echangeur de chaleur selon la revendication 9, caractérisé en ce que le plus petit espacement ax présente une plage de 5 < ax < 50 mm, en particulier une plage de 8 < ax < 30 mm.
  11. Echangeur de chaleur selon la revendication 10, caractérisé en ce que l'espacement (a1, a2, a3 ...) des rangées est un multiple (entier) du plus petit espacement ax.
EP15202230.7A 2005-06-24 2006-06-23 Fluide caloporteur Active EP3048407B9 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005029321A DE102005029321A1 (de) 2005-06-24 2005-06-24 Wärmeübertrager
PCT/EP2006/006071 WO2006136437A1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur
EP06762163.1A EP1899670B1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP06762163.1A Division EP1899670B1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur
EP06762163.1A Division-Into EP1899670B1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur

Publications (3)

Publication Number Publication Date
EP3048407A1 EP3048407A1 (fr) 2016-07-27
EP3048407B1 EP3048407B1 (fr) 2019-08-07
EP3048407B9 true EP3048407B9 (fr) 2019-11-27

Family

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Application Number Title Priority Date Filing Date
EP06762163.1A Not-in-force EP1899670B1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur
EP15202230.7A Active EP3048407B9 (fr) 2005-06-24 2006-06-23 Fluide caloporteur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP06762163.1A Not-in-force EP1899670B1 (fr) 2005-06-24 2006-06-23 Echangeur de chaleur

Country Status (5)

Country Link
US (1) US7942137B2 (fr)
EP (2) EP1899670B1 (fr)
JP (1) JP5112304B2 (fr)
DE (1) DE102005029321A1 (fr)
WO (1) WO2006136437A1 (fr)

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EP3048407B1 (fr) 2019-08-07
WO2006136437A1 (fr) 2006-12-28
EP1899670B1 (fr) 2016-08-10
JP5112304B2 (ja) 2013-01-09
EP1899670A1 (fr) 2008-03-19
US20100139631A1 (en) 2010-06-10
DE102005029321A1 (de) 2006-12-28
JP2008544207A (ja) 2008-12-04
EP3048407A1 (fr) 2016-07-27
US7942137B2 (en) 2011-05-17

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