EP1770250B1 - Echangeur de chaleur pour tuyaux d'échappement - Google Patents

Echangeur de chaleur pour tuyaux d'échappement Download PDF

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Publication number
EP1770250B1
EP1770250B1 EP06020114A EP06020114A EP1770250B1 EP 1770250 B1 EP1770250 B1 EP 1770250B1 EP 06020114 A EP06020114 A EP 06020114A EP 06020114 A EP06020114 A EP 06020114A EP 1770250 B1 EP1770250 B1 EP 1770250B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
hose
jacket
corrugated hose
exchanger according
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
EP06020114A
Other languages
German (de)
English (en)
Other versions
EP1770250A2 (fr
EP1770250A3 (fr
Inventor
Carlo Burkhardt
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.)
Witzenmann GmbH
Original Assignee
Witzenmann GmbH
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 Witzenmann GmbH filed Critical Witzenmann GmbH
Publication of EP1770250A2 publication Critical patent/EP1770250A2/fr
Publication of EP1770250A3 publication Critical patent/EP1770250A3/fr
Application granted granted Critical
Publication of EP1770250B1 publication Critical patent/EP1770250B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/14—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having thermal insulation
    • F01N13/141—Double-walled exhaust pipes or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/11—Manufacture or assembly of EGR systems; Materials or coatings specially adapted for EGR systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/02—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/12—Tubes being corrugated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the invention relates to a heat exchanger for exhaust pipes and a method for its production.
  • the heat exchanger has an inner flow space for a first medium and an outer flow space for a second medium, wherein the inner flow space of a corrugated hose and the outer flow space between the corrugated hose and a sheath line are formed.
  • the corrugated hose is ring corrugated and extends along the sheath line on the radial inside and in particular substantially concentric with the sheath line, wherein in the outer flow space between the sheath line and the corrugated hose over the axial length of the corrugated hose one or more of the sheath line and the corrugated hose line adjacent spacer elements are arranged.
  • the known from the cited document heat exchanger consists of an inner bundle of helically corrugated hose lines and an outer partially corrugated sheathed cable.
  • the corrugated hose lines are fixed to each other via a plurality of plates and the combination of said plates is inserted together with the hose line bundle in the multiple bending sections having sheathed cable and fixed there.
  • the US 4,203,312 A discloses a generic heat exchanger, are held in the parallel corrugated hose between terminal walls of a heat exchange chamber.
  • the EP 1 136 780 A2 discloses a method for manufacturing a heat exchanger for exhaust pipes with an inner corrugated hose and an outer at least partially corrugated hose.
  • the present invention seeks to provide a heat exchanger for exhaust pipes of the type mentioned above, which is characterized by a simpler structure, easier installation and better working.
  • the spacer elements are substantially annular, helical, circumferentially formed around the circumference and / or formed over the circumference.
  • the heat exchanger according to the invention achieves improved heat transfer between the first and second flow medium, for which purpose the arranged in the outer flow space between the sheathed cable and the corrugated hose line spacing elements according to the invention in the form of circumferential or segmented ring or helical elements, eg. B. are formed in the form of wire compression rings or wire crimps.
  • These spacers provide a turbulence of flowing through this outer flow space second medium, ie the cooling water to increase the efficiency of the heat exchanger and at the same time to dampen vibration of the inner corrugated hose.
  • the spacers may also consist of sheet metal parts, temperature-resistant plastic elements and the like with a corresponding structure and appropriate arrangement.
  • Another advantage of the heat exchanger according to the invention lies in the annular corrugation of the inner corrugated hose, the expansions in mounting the inner corrugated hose in the outer sheathed cable and strains due to temperature changes in the use of the heat exchanger joins torsion and thus allows only relative movements between inner corrugated hose and outer sheath line in the axial and possibly also in the radial direction, but not in the torsion direction.
  • the connection connections that is, the connections to adjacent lines for transporting the first and the second medium are kept free of torsional forces, whereby the service life and the quality of the connection connection is increased accordingly.
  • a particular advantage of the heat exchanger according to the invention can be achieved in that the heat exchanger has at least one axial curvature region in which it changes its axial extension direction, that the sheathed cable is provided with corrugations at least in this curvature region and that the at least one curvature region of the heat exchanger by thornless forming is formed by corrugated hose and sheathed cable. It is therefore first inserted the inner corrugated hose in the sheath line, both being in straight or almost straight axial extent and wherein spacer elements are arranged between the hose and sheathed cable.
  • curvature areas are then introduced into the corrugated sections of the sheathed conduit in order to adapt the heat exchanger to the installation conditions, this can be done in a simple manner by bending the sheathed cable in the region of the intended curvature and transferring the spacers to the inner hose line, without the need for a mandrel or a similar auxiliary tool would be required.
  • the corrugations can extend radially inward and / or radially outward starting from the adjacent smooth cylindrical course.
  • the cross section of the first flow space is reduced, wherein the outer diameter of the sheath line corresponds to that in the smooth cylindrical areas, which is particularly advantageous in a confined installation space.
  • the waves extend substantially radially outward, then the cross section of the first flow space substantially corresponds to that of the smooth cylindrical profile, however, the outer diameter of the sheath line and thus of the heat exchanger is correspondingly increased in this area.
  • the corrugated hose is formed semiil, so that they inform istsfan the heat exchanger in particular by bending remains at least almost in the reshaped extension, so not due to the elasticity tries to bend back the heat exchanger in the straight direction of extent.
  • a semiflexible hose line could be produced, for example, by subjecting a conventional corrugated hose to a stretching or stretching operation, as a result of which the flanks are correspondingly flatter and the wave crests are further corrugated. In this case, the area of the flexible areas is reduced, but the hose line still remains sufficiently flexible to be able to absorb the required thermal expansions on the one hand and on the other hand to impede the installation and in particular the insertion into the sheathed cable.
  • a similar result can alternatively be achieved by equipping the hose line with a corresponding semiflexible corrugation in a first forming process.
  • the prior art already discloses a semiflexible hose line which can be used for other purposes, the geometrical conditions of which could also be used in the present case.
  • the radially outer peaks of the hose corrugations of the hose line may be substantially smooth cylindrical or cambered, i.
  • the axial length of the individual peaks is greater than the axial length of the radially inner troughs such that the tube with respect to the sizes axial length of the individual peaks and axial length of the individual troughs within the mutual ratio of these sizes in Range of 2.3: 1 to 4.6: 1 is formed, and wherein the axial length of the individual peaks is greater than the radial profile height between troughs and wave crests such that the hose with respect to the sizes axial length of the individual peaks and profile height between Wave trough and wave peak within the mutual ratio of these sizes in the range of 1.7: 1 to 2.8: 1 is formed.
  • the mentioned wide corrugation of the corrugated hose has but one more significant advantage: While in the prior art, the inner hose lines are helical, to a helical flow, especially in the field of troughs allow the wide corrugation in the present case also for a complete flow around the inner hose, so that there are no hose line areas that lie in the flow shadow and thus hinder heat transfer between the first and second flow medium.
  • the determination of the spacer elements on outer sheathed cable and inner hose is - especially in the case of metal spacers - simplified in that they have copper, so for example, the Drahtpressmaschine partially copper wires included, so that the spacer elements by simple soldering or resistance welding to the adjacent components can be set, which can conveniently be done in a soldering / continuous furnace. Similar advantages arise when the spacer elements contain plastic, since then a bonding or a thermal cohesive bonding is possible.
  • the exhaust pipe is an EGR pipe, which serves for exhaust gas recirculation, and that the heat exchanger is installed in the EGR pipe, so that the outer flow space for a cooling medium, in particular cooling water, and the inner flow space for the Exhaust gas is provided.
  • the heat exchanger in the exhaust pipe between a with respect to the exhaust flow upstream catalyst and a downstream muffler is installed. This can even be exploited to such an extent that almost provides the complete course of the exhaust pipe with a heat exchanger according to the invention.
  • the reduced temperatures also provide advantages with regard to the position and nature of the surroundings of the silencer or of the end of the exhaust pipe. For example, lower safety distances to the environment of the exhaust system must be maintained, which leads to a gain in space.
  • holding elements can be used for the exhaust system, which does not have to be so temperature resistant and thus can usually be simpler and cheaper.
  • heat exchange media various substances are suitable, such as e.g. Water, cooling water, air, compressed air, solids, which can also be used in the heat exchanger according to the invention.
  • the hose may be constructed in two or more layers and - also for noise control - have a changing over its length wave height, ie either the outer diameter of the wave crests or the inner diameter of the troughs or both above the length of the hose in particular can change progressively.
  • heat exchanger is protected by the present invention, but also a process for its production.
  • This is characterized in inventive manner by the fact that spacers are arranged between corrugated hose and sheathed cable, and that curved thornless simultaneous forming of hose and sheathed heat exchanger areas are created in which the hose and the sheath line change its axial extension direction.
  • This thornless reshaping consists in particular of a bending of the sheathed cable, wherein this bending of the sheathed cable is transmitted to the hose line via the spacer elements and mitverformt the hose accordingly.
  • the manufacturing method can be further developed according to the invention by the aforementioned device characteristics of the heat exchanger.
  • FIGS. 1 and 2 a heat exchanger 1 according to the invention in a sectional side view, in FIG. 1 in the linear starting position and in FIG. 2 in twice bent position, and in FIG. 3 an alternative embodiment of a heat exchanger 21 according to the invention in a partially sectioned side view.
  • the heat exchanger 1 consists of an outer sheathed cable 2, which has a straight axial extension in the example shown and consists of a total of three tubular cylindrical sections 3, 4, 5 and two corrugated areas 6, 7, which can act as curvature areas.
  • the sheathed cable 2 has an inlet 8 and a drain 9, wherein these inlets and outlets are connected in the radial direction to the sheathed cable 2 in the region of smooth cylindrical pipe sections 3, 5.
  • the heat exchanger 1 also has an inner corrugated hose line 10 extending coaxially with the outer sheathed cable 2, which are connected at cylindrical connecting ends 11, 12 to adjacent exhaust pipe sections 13, 14.
  • an outer Sheathed cable 2 set so that between the outer sheathed cable 2 and inner corrugated hose 10 an outer flow or annulus 15 is left, can flow through the cooling water W from the inlet 8 in the direction of the drain 9.
  • the flow of the cooling water W is deflected or impeded by spacer elements 16, 17, 18, which are arranged between the inner hose line 10 and the outer sheath line 2 and ensure the concentric mutual position of the two lines.
  • These spacer elements 16 to 18, for example, consist of wire press rings, which can be arranged completely circumferential, segmented circumferential, helical or the like between the two lines to give the flow the desired direction while maintaining its support or distance assurance function.
  • the exhaust gas G to be cooled flows in countercurrent direction from the adjacent exhaust gas line 14 via the connection element 12 through the inner corrugated hose line 10 to the connection element 11 and from there into the exhaust line 13, whereby the exhaust gas temperature can be correspondingly reduced significantly over the axial length of the heat exchanger.
  • the flow space within the corrugated hose is indicated by reference numeral 19.
  • the heat exchanger according to the invention extend to adapt to the respective installation conditions deviating from its axial extent, it can be bent accordingly in the radial direction in the region of the corrugated areas 6, 7 together with the already mounted inner corrugated hose 10, without requiring a mandrel or a similar auxiliary tool would be required.
  • the inner corrugated hose 10 can hold the entire heat exchanger in the bent position after bending, as exemplified in FIG. 2 is shown, even if the outer sheath line and their corrugated portions 6, 7 would tend due to their inherent elasticity to return to the axial output extension. Again, the spacers provide 16 to 18 again for the necessary support.
  • a heat exchanger 21 is shown, which consists of two parts 21a and 21b, which are arranged in the flow direction of the exhaust gas G one behind the other between a catalyst 22 and an end muffler 23 in an exhaust pipe 24.
  • the exhaust gas flow G is conveyed from an exhaust gas inlet 25 to the catalytic converter 22 and from there through a corrugated hose line 26 to the rear silencer 23, which the exhaust gas flow G exits via an exhaust gas outlet 27.
  • the hose 26 is like the hose 10 from the FIGS. 1 and 2 constructed and supported by spacer elements 28, 29 on which the hose on its radially outer by far surrounding sheath conduit 30 so that between the hose 26 and sheath conduit 30, a flow or annular space 31 is formed through which the refrigerant or to be heated Water W is flowing.
  • the sheath line 30 has a smooth-walled curved portion 30 a, in which the axial extension direction of the sheath line changes, and a corrugated portion 30 b, similar to the corrugated portions 6, 7 of the Figu ren 1 and 2 forms a bending region in which the exhaust pipe to compensate for assembly inaccuracies, etc. is designed to yield. Because of the large total length of the two heat exchanger parts 21 a and 21 b, the total heat exchanger surface is very large, it is possible to cool down the exhaust stream G to a considerable extent, so that finally in the region of the muffler 23 and in the region of the exhaust pipe end materials can be used which are otherwise not possible in exhaust pipes. Instead of metal and in particular galvanized steel or stainless steel, for example, plastic can be used, which is superior in terms of shaping options and manufacturing costs metal.
  • the present invention provides the significant advantage that heat exchangers for EGR lines are easier to assemble and also have a better working behavior due to the use of an inner ring-corrugated hose line.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)

Claims (20)

  1. Echangeur de chaleur pour conduits d'échappement, comprenant un espace intérieur d'écoulement (19) dévolu à un premier fluide (G) et un espace extérieur d'écoulement (15) dédié à un second fluide (W), l'espace intérieur d'écoulement étant formé d'un conduit souple annelé (10, 26), et l'espace extérieur d'écoulement étant formé entre ledit conduit souple annelé et un conduit d'enveloppement (2, 30), sachant que ledit conduit souple annelé (10, 26) comporte des ondulations annulaires et s'étend le long dudit conduit d'enveloppement (2, 30), sur la face intérieure radiale de ce dernier, et sachant qu'un ou plusieurs élément(s) d'espacement (16, 17, 18, 28, 29), en applique contre le conduit d'enveloppement et contre le conduit souple annelé, est (sont) logé(s) dans l'espace extérieur d'écoulement (15) entre ledit conduit d'enveloppement et ledit conduit souple annelé, sur la longueur axiale dudit conduit souple annelé, lesquels éléments d'espacement (16 à 18, 28, 29) sont pour l'essentiel de réalisation annulaire, avec étendue continue sur le pourtour et/ou avec segmentation sur le pourtour,
    caractérisé par le fait
    que les éléments d'espacement (16 à 18, 28, 29) sont disposés à chaque fois, au moins en partie, dans un creux d'ondulation du conduit souple annelé (10, 26).
  2. Echangeur de chaleur selon au moins la revendication 1,
    caractérisé par le fait
    que ledit échangeur de chaleur (1, 21) présente au moins une zone (6, 7, 30b) de courbure axiale, dans laquelle la direction de son étendue axiale varie ; et par le fait que le conduit d'enveloppement (2, 30) est muni d'ondulations, au moins dans cette zone de courbure.
  3. Echangeur de chaleur selon au moins la revendication 2,
    caractérisé par le fait
    que la zone de courbure (6, 7, 30b) dudit échangeur de chaleur (1, 21), à présence minimale, est obtenue par formage sans mandrin du conduit souple annelé (10, 26) et du conduit d'enveloppement (2, 30).
  4. Echangeur de chaleur selon au moins l'une des revendications précédentes, caractérisé par le fait
    que le conduit souple annelé (10, 26) est de réalisation semi-flexible, de sorte qu'il conserve au moins approximativement le tracé mis en forme au cours de la mise en forme dudit échangeur de chaleur (1,21), notamment par cintrage.
  5. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple annelé (10,26) est réalisé avec ondulations larges.
  6. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple annelé (10, 26) comporte des crêtes d'ondulations à allure essentiellement cylindrique lisse, ou bombée.
  7. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple annelé s'étend, pour l'essentiel, concentriquement au conduit d'enveloppement (2, 30).
  8. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que les éléments d'espacement (16 à 18, 28, 29) offrent un tracé en pas de vis dans l'espace extérieur d'écoulement (15), le long du conduit souple annelé (10, 26).
  9. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que les éléments d'espacement (16 à 18, 28, 29) sont de réalisation segmentée, et sont agencés avec répartition sur le pourtour du conduit souple annelé (10,26).
  10. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que les éléments d'espacement (16 à 18, 28, 29) sont constitués par des pièces comprimées en fil métallique.
  11. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que les éléments d'espacement (16 à 18, 28, 29) renferment partiellement du cuivre en vue de la consignation à demeure desdits éléments d'espacement sur le conduit souple annelé (10, 26) et/ou sur le conduit d'enveloppement (2, 30), par brasage ou par soudage résistif.
  12. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que les éléments d'espacement renferment partiellement une matière plastique en vue de la consignation à demeure desdits éléments d'espacement sur le conduit souple annelé et/ou sur le conduit d'enveloppement, par collage ou par liaison matérielle thermique.
  13. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit d'échappement est un conduit de remise en circulation des gaz d'échappement ; et par le fait que ledit échangeur de chaleur est intégré dans ledit conduit de remise en circulation des gaz d'échappement, de sorte que l'espace extérieur d'écoulement (15) est prévu pour un fluide de refroidissement (W), en particulier de l'eau de refroidissement, et l'espace intérieur d'écoulement (19) est prévu pour des gaz d'échappement (G).
  14. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que ledit échangeur de chaleur est intégré, dans le conduit d'échappement, entre un catalyseur (22) implanté en amont vis-à-vis du flux des gaz d'échappement, et un silenceur (23) implanté en aval.
  15. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple (10, 26) est structurellement organisé en deux ou plusieurs couches.
  16. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple (10, 26), et/ou le conduit d'enveloppement (2, 30), consiste(nt) notamment en de l'acier fin.
  17. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que le conduit souple (10, 26) et/ou le conduit d'enveloppement (2, 30) consiste(nt) en une matière plastique ou en du caoutchouc, au moins dans la région extrême du conduit d'échappement (24).
  18. Echangeur de chaleur selon au moins l'une des revendications précédentes,
    caractérisé par le fait
    que l'ondulation du conduit souple (10, 26) présente une hauteur variant sur sa longueur.
  19. Procédé de fabrication d'un échangeur de chaleur (1, 21) pour conduits d'échappement, comprenant un conduit souple intérieur annelé (10, 26) et un conduit extérieur d'enveloppement (2, 30) au moins partiellement annelé,
    caractérisé par le fait
    que des éléments d'espacement (16, 17, 18, 28, 29) interposés entre le conduit souple annelé et le conduit d'enveloppement sont placés à chaque fois, au moins en partie, dans un creux d'ondulation dudit conduit souple annelé ; et par le fait qu'un formage simultané dudit conduit souple et dudit conduit d'enveloppement, exécuté sans mandrin, donne naissance à des zones courbes d'échange thermique (6, 7, 30b) dans lesquelles se produit une variation de la direction de l'étendue axiale dudit conduit souple et dudit conduit d'enveloppement.
  20. Procédé selon la revendication 19,
    caractérisé par le fait
    que le formage sans mandrin consiste en un cintrage du conduit d'enveloppement (2, 30) qui, par l'intermédiaire des éléments d'espacement (16 à 18, 28, 29), est répercuté sur le conduit souple (10, 26) et déforme conjointement ce dernier.
EP06020114A 2005-09-28 2006-09-26 Echangeur de chaleur pour tuyaux d'échappement Not-in-force EP1770250B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005046536A DE102005046536A1 (de) 2005-09-28 2005-09-28 Wärmetauscher für EGR-Leitungen

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EP1770250A2 EP1770250A2 (fr) 2007-04-04
EP1770250A3 EP1770250A3 (fr) 2007-11-07
EP1770250B1 true EP1770250B1 (fr) 2012-06-06

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JP4618539B2 (ja) * 2003-12-19 2011-01-26 日立金属株式会社 ダイカスト用スリーブ
DE102007003684B4 (de) * 2007-01-25 2009-12-31 Häßler, Andreas, Dipl.-Ing. (FH) Durchlaufofen mit Rekuperator-Vorrichtung
GB2451862A (en) * 2007-08-15 2009-02-18 Senior Uk Ltd High gas inlet temperature EGR system
ITBS20070170A1 (it) * 2007-11-05 2009-05-06 Gianfranco Bonomi Scambiatore termico tubolare pieghevole
FR2926845A1 (fr) * 2008-01-24 2009-07-31 Renault Sas Element de conduite d'echappement flexible, et ensemble de motorisation comportant un tel element, notamment pour un vehicule avec circuit de recirculation des gaz d'echappement
DE102010005803A1 (de) * 2010-01-27 2011-07-28 Audi Ag, 85057 Kraftwagen mit einer Abgasanlage
DE102011007748A1 (de) * 2011-04-20 2012-10-25 Behr Gmbh & Co. Kg Abgaskühler zum Kühlen von Verbrennungsabgas einer Verbrennungskraftmaschine, Wassersammeladapter, Abgaskühlsystem und Verfahren zum Herstellen eines Abgaskühlsystems
DE102013111033B4 (de) 2012-10-08 2019-10-17 Witzenmann Gmbh Verfahren und Vorrichtung für Thermomanagement einer Kfz-Abgasanlage
SE540114C2 (sv) * 2014-03-27 2018-04-03 Skorstensbolaget I Stockholm Ab Rörformig motströmsluftvärmeväxlare innefattande distansorgan mellan rören
CN104929733B (zh) * 2015-06-22 2017-10-24 陈伟强 冷却排气管
CN108223093A (zh) * 2017-12-08 2018-06-29 中国北方发动机研究所(天津) 一种舷外机螺旋槽导流式水道夹层排烟管隔热结构

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JP3105882B2 (ja) * 1999-03-11 2000-11-06 東京ラヂエーター製造株式会社 熱交換機
EP1096131B1 (fr) 1999-10-26 2001-09-19 Senior Flexonics Automotive Limited Refroidisseur de recirculation de gaz d'échappement
EP1136780A3 (fr) 2000-03-23 2002-11-06 Senior Investments AG Echangeur de chaleur à tubes doubles
JP2002130060A (ja) * 2000-10-24 2002-05-09 Katayama Kogyo Co Ltd Ｅｇｒガス冷却装置
JP4207196B2 (ja) * 2003-05-23 2009-01-14 株式会社ティラド 熱交換器

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EP1770250A3 (fr) 2007-11-07
DE102005046536A1 (de) 2007-03-29

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