EP2863157B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2863157B1
EP2863157B1 EP14189402.2A EP14189402A EP2863157B1 EP 2863157 B1 EP2863157 B1 EP 2863157B1 EP 14189402 A EP14189402 A EP 14189402A EP 2863157 B1 EP2863157 B1 EP 2863157B1
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EP
European Patent Office
Prior art keywords
fluid
housing
heat exchanger
section
flow channel
Prior art date
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Active
Application number
EP14189402.2A
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German (de)
English (en)
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EP2863157A1 (fr
Inventor
Simon HUND
Albrecht Siegel
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Mahle Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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Publication of EP2863157A1 publication Critical patent/EP2863157A1/fr
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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
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1684—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 in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—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 in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • 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
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0292—Other particular headers or end plates with fins

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1 and a method for using a heat exchanger according to claim 9.
  • US Pat. No. 1,868,661 discloses such a heat exchanger.
  • U-flow heat exchangers are used. These heat exchangers are characterized in that the fluid flowing through the heat exchanger flows in at an end region of the heat exchanger and is deflected by approximately 180 degrees at an end region opposite this end region. The fluid finally flows out of the heat exchanger at the end region where it has flowed. Heat exchangers with such a configuration are preferably used when the installation space no longer permits conventionally flow-through heat exchangers or speak of other boundary conditions for use.
  • the exhaust gas recirculation system in this case has a heat transfer unit, which comprises a heat exchanger, which has a deflection of a fluid to be cooled by about 180 degrees.
  • the heat exchanger has for this purpose a flow channel, which is U-shaped.
  • a disadvantage of the solutions in the prior art is in particular that the deflection of the heat exchanger either not at all or only by the ambient air surrounding the heat exchanger is cooled. Furthermore, in heat exchangers, which provide a flow around the flow channel including the deflection, often the maximum heat transfer is too low.
  • a deflected along its flow direction heat exchanger is particularly advantageous because overall the overall length of the heat exchanger can be made shorter than a straight-flow heat exchanger.
  • a deflecting region surrounded by a second fluid is advantageous because it provides an additional heat transfer capability within the heat exchanger, whereby the efficiency or the performance of the heat exchanger can be increased.
  • the first section and / or the second section of the first flow channel is advantageously formed from tubes. Tubes are particularly advantageous because they are inexpensive to produce and are available in a variety of different shapes on the market. By a plurality of tubes, which are each surrounded by a fluid at their outer surfaces, the total heat transfer surface can be increased, whereby an improved heat transfer between the fluid within the tubes and the fluid outside the tubes can be achieved.
  • the housing may be better adapted to the shape of the heat exchanger.
  • undercuts can be realized by a multi-part housing, which can not be realized, for example, by one-piece deep-drawn housing.
  • the housing is advantageously made of an aluminum material and produced in a die-casting process. In this case, either all housing parts or only individual housing parts can be generated in this way.
  • the housing or individual housing parts may be made of a steel material, in particular stainless steel, or a plastic. Made of plastic housing or housing parts are preferably made in an injection molding process.
  • the housing at least partially forms the second flow channel.
  • the housing surrounds the first flow channel such that a cavity is formed between the outer walls of the first flow channel and the inner walls of the housing, which forms the second flow channel. By flowing through this second flow channel, the first flow channel is flowed around, whereby a heat transfer between the fluid in the first flow channel and the fluid in the second flow channel can be generated.
  • first housing part surrounds the first and second part section and the second housing part surrounds the deflection area.
  • the subsections can advantageously be encompassed by a simple cuboid structure, while the deflection region can be encompassed, for example, by a further housing part which, for example, in the form of a housing part deep-drawn lid can be formed and can be produced in a separate manufacturing process. It is also preferable if the tubesheet with a lid forms a collecting box, wherein the internal volume of the collecting box forms the deflection region. In this way, a fluid-tight deflection region can be produced by known production methods.
  • This flow path is particularly advantageous, since it can flow around the deflection region with the second fluid, which is preferably cooling. As a result, the overall heat transfer area between the first fluid and the second fluid is increased, whereby the performance of the heat exchanger is improved.
  • the fluid flow in the flow path can be advantageously influenced.
  • the effective cross-flow area can be influenced, which has a direct influence on the occurring pressure loss within the heat exchanger.
  • the course of flow within the flow path can also be influenced.
  • the housing has a first fluid connection and a second fluid connection, via which the second fluid can be supplied into the housing and can be discharged from the housing.
  • first section and the second section and / or the deflection of the first flow channel into the housing, which at least partially forms the second flow channel can be integrated such that the second flow channel fluid-tight with respect to the First flow channel and / or the deflection region and the environment is sealed.
  • a fluid-tight seal of the flow channels with respect to the respective other flow channel and the environment is particularly advantageous in order to ensure the functionality of the heat exchanger.
  • a mixing of the fluids could occur, which can lead to damage of the heat exchanger and / or the upstream and downstream components.
  • tubes are accommodated at least at a common end region in a tube plate.
  • the tubes are advantageously accommodated at a common end region in a tube plate. This increases the stability of the heat exchanger. Furthermore, by providing a tube plate at a common end region, a particularly simple connection to a fluid supply line and a fluid discharge can be achieved.
  • the fluid supply and the fluid discharge of the first flow channel are arranged at a common end region of the heat exchanger. This allows a particularly compact design of the heat exchanger.
  • the first fluid is a gas and the second fluid is a coolant.
  • the first fluid is a gas and the second fluid is a coolant.
  • a cooling of the in the first flow channel flowing fluid can be achieved advantageously.
  • the second fluid has a lower temperature level than the first fluid.
  • the second fluid serves to cool the first fluid.
  • the second fluid can advantageously be incorporated into a cooling circuit in order to always ensure the lowest possible temperature level for the second fluid.
  • the second fluid in an alternative embodiment, but also have a higher temperature level than the first fluid. This is especially true when the heat exchanger is used to heat the first fluid.
  • the first fluid in the deflection region can be deflected by 180 degrees along its direction of flow.
  • a deflection of about 180 degrees is particularly advantageous since in this way the fluid connections can be provided at a common end region of the heat exchanger.
  • the maximum amount of heat that can be transferred may be larger or smaller.
  • a second fluid which is preferably a cooling fluid, flows around.
  • the Fig. 1 shows a perspective view of a heat exchanger 1.
  • the heat exchanger 1 is surrounded by a housing 2.
  • the housing 2 has on its outer side a plurality of ribs 5, which increase the structural rigidity of the housing 2.
  • the ribs 5 are for this purpose distributed on the housing 2 load.
  • the housing 2 has a holding element 4, with which the heat exchanger 1 can be attached to a surrounding structure.
  • the housing 2 has a fluid connection 3, through which a fluid can be conveyed into the housing 2.
  • a tube plate 6 is indicated, which belongs to the heat exchanger 1 inserted in the housing 2.
  • the housing 2 is preferably formed from a plastic, which can be processed, for example, in a die-casting process. Alternatively, metallic materials can also be used.
  • the Fig. 2 shows a perspective view of the heat exchanger 1, as in the housing 2 of Fig. 1 is arranged.
  • the heat exchanger 1 has in its lower region a tube plate 6, in which a plurality of first tubes 8 and second tubes 9 is received.
  • the tubes 8 and 9 are arranged in each case in two adjacent tube stacks with several tubes in depth.
  • the tubes 8 are traversed along the flow direction 10 with a first fluid and the tubes 9 are flowed through along the flow direction 11 with the first fluid.
  • the directional deflection between the tubes 8 and tubes 9 takes place in the upper deflection region 7.
  • the deflection region 7 is essentially also through a tube plate 16 is formed, in which the tubes 8, 9 are received and a box-like lid 17, which is inserted into this tubesheet, whereby an internal volume within the deflection region 7 is generated, in which the fluid from the tubes 8 into the tubes 9 flow can.
  • the first tubes 8 form a first section 12 of a first flow channel 15 and the second tubes 9 form a second section 13 of a first flow channel 15. Overall, the tubes 8 and 9 and the deflection 7 form the first flow channel 15.
  • the first flow channel 15 can be flowed around by a second fluid within the housing 2.
  • a second flow channel 14 is formed for this purpose.
  • a heat exchange between the first fluid can be generated both along the tubes 8 of the deflection region 7 and the tubes 9.
  • the heat transfer between the first fluid and the second fluid can be significantly increased, since in particular the deflection region 7 is fully involved in the heat transfer between the first fluid and the second fluid.
  • adeschleitvorraum shown which surrounds both the tubes 8 and the tubes 9.
  • the task of theisserleitvoroplasty is to influence the flow of fluid flowing within the housing. This should primarily be prevented that a short-circuit flow within the housing is formed and thus the fluid flows directly from the fluid inlet to the fluid outlet. This can happen, in particular, if the fluid inlet and the fluid outlet are arranged on a common housing side.
  • the fluid can also be routed specifically between the tubes 8, 9 in such a way that the best possible flow around and thus an improved heat transfer occurs.
  • an increase in the stability of the heat exchanger 1 can be achieved by thehariffenleitvortechnisch.
  • tubes 8 a fluid can be supplied and separated from the tubes 9, a fluid can be removed.
  • the Fig. 3 shows an alternative embodiment of a heat exchanger 21.
  • the heat exchanger 21 is received within the housing 22.
  • the housing 22 is preferably formed of a metallic material. Ideally, the housing 22 is formed of an aluminum.
  • the housing 22 has a plurality of holding elements 24, with which the housing 22 or the heat exchanger 21 can be attached to surrounding structures.
  • a tube plate 26 is indicated, which belongs to the heat exchanger 21 inserted in the housing 22.
  • the Fig. 4 shows a perspective view of the heat exchanger 21, as in the interior of the housing 22 of the Fig. 3 is arranged.
  • the tube plate 26 has a plurality of tubes 28 received in the tubesheet 26 and tubes 29.
  • the tubes 28 and 29 are in the tube plate 26 analogous to the arrangement of the tubes 8 and 9 of the Fig. 2 arranged in the tube sheet 6.
  • the tubes 28 form a first section 36 of a first flow channel 39
  • the tubes 29 form a second section 37 of the first flow channel 39.
  • the tubes 28 and 29 are in the Fig. 4 further from adeschleitvoriques similar to Fig. 2 whereby the fluid flow within the heat exchanger 21 can be improved overall and, in particular, short-circuit flows of the fluid between the fluid inlet and the fluid outlet of the housing can be avoided.
  • the tubes 28 are flowed through along the flow direction 30 with a first fluid and the tubes 29 are flowed through along the flow direction 31 with the first fluid.
  • the deflection of the fluid takes place in the deflection region 27.
  • the tube plate 26 has, in addition to openings in which the tubes 28 and 29 are received and the openings 32 and 33.
  • the interior of the housing 22 or of the second flow channel 38 formed in the interior of the housing 22 can be subjected to a fluid or the fluid can be discharged from the interior of the housing 22.
  • the tube plate has a circumferential shoulder, which is guided both around the openings 32, 33 and the tubes 28 and 29. This paragraph comes when placing the housing 22 on an inner wall of the housing for lying and thus serves to seal the housing 22 relative to the tube sheet 26th
  • a sealing means may further be provided on this shoulder.
  • the tube plate 26 has a plurality of openings, which can serve for screwing the tube plate 26 to the housing 22 and the connection of fluid connections to the tube plate 26 for supplying the tubes 28 with a first fluid or for the discharge of the first Fluids from the pipes 29.
  • the turbulence inserts 34 are designed such that the gap which arises between the outer wall of the deflection region 27 and the inner wall of the housing 22 is influenced such that the fluid flow of the second fluid flowing within the housing 22 is optimized.
  • a flow path 35 is formed in the region between the deflection region 27 and the inner wall of the housing 22.
  • the housing 22 as well as the housing 2 of Fig. 1 designed such that at least between the deflection region 27 and the deflection region 7 and the interior of the housing 22 and 2, a sufficiently large gap remains, as Flow path 35 is formed and can be flowed through by the second fluid within the housing 22 and 2 respectively.
  • the tubes 28 and 29 are also flowed around by the second fluid, whereby along the entire heat exchanger 1, 21, a heat transfer between the first fluid within the tubes 8, 9, 28, 29 of the heat exchanger 1, 21 and the second fluid in the housing 2, 22 of the heat exchanger 1, 21 can take place.
  • the Fig. 5 shows a further perspective view of a heat exchanger 41, which is arranged within a housing 42.
  • the housing 42 is formed in two parts and has a substantially cuboidal region 42 and a housing part 45 connected thereto or placed on this area.
  • Fluid connections 43 and 44 for feeding or discharging a second fluid into the housing 42 are provided on the cuboid housing part 42 intended.
  • a tube plate 46 of the heat exchanger 41 is indicated.
  • the Fig. 6 shows a view of the heat exchanger 41, as in the housing 42 of the Fig. 5 is arranged.
  • the housing part 42 and the housing part 45 is not shown.
  • the fluid ports 43 and 44 of the housing 42 are further shown.
  • the heat exchanger 41 has a plurality of first tubes 48 and a plurality of second tubes 49, which analogous to the Fig. 4 and 2 are arranged.
  • the tubes 48 are flowed through along the flow direction 50 and form a first section 52 of the first flow channel 55.
  • the tubes 49 are traversed along the flow direction 51 and form a second section 53 of the first flow channel 55th
  • the deflection between the tubes 48 and the tubes 49 takes place along the deflection region 47, which is analogous to the preceding figures formed by a tube plate 56 and a cover 57 inserted therein. Both the tubes 48, 49 and the deflection region 47 can be flowed around by the second fluid, while they are flowed through by the first fluid.
  • the housing 42, 45 forms a second flow channel 54. In this way, a complete heat transfer also takes place both on the tubes 48, 49 and on the deflection region 47.
  • the Fig. 7 shows a sectional view through a conventional deflected heat exchanger 61, as is known in the art.
  • This has a plurality of tubes 68, which are flowed through along the flow direction 70 and a plurality of tubes 69, which are flowed through along the flow direction 71.
  • the tubes 68, 69 are received in the tube plate 63 in their left-hand region and in the tubesheet 64 at their right-hand end region.
  • the tube plates 63 and 64 are accommodated within the housing 62 in widened regions 65, 66.
  • the tube sheets 64, 64 are welded or soldered to the housing 62.
  • the fluid flow of the first fluid is deflected from the tubes 68 to the tubes 69. This is illustrated with the flow direction 73 within the deflection region 67.
  • the lid is advantageously inserted within the tube bottom 64 with a sealing element 72.
  • a positive connection can be generated, alternatively, a cohesive, for example by gluing, soldering, welding.
  • the in Fig. 7 shown heat exchanger 61 is only flowed through by a first fluid along the tubes 68, 69 and the deflection region 67.
  • the housing 62 can be traversed by a second fluid.
  • the deflection region 67 is shown in the illustration of Fig. 7 does not flow around a cooling second fluid, so that the heat transfer takes place in the heat exchanger 61 only along the tubes 68 and 69. As a result, the overall heat transfer path is reduced compared to the preceding figures, whereby the total amount of heat transferable is reduced.
  • the deflection region 67 can only be exposed to the surrounding medium, such as the air, whereby both an additional cooling of the first fluid and an unwanted heating of the first fluid can take place.
  • the Fig. 8 shows a sectional view through a heat exchanger 81.
  • a heat exchanger 81 is shown, as already in the Fig. 5 or 6 is shown.
  • the heat exchanger 81 has a plurality of first tubes 88 and a plurality of second tubes 89, which are flowed through according to the flow direction 90 and 91, respectively.
  • the first tubes 88 form a first section 97 and the second tubes 89 form a second section 98.
  • the two subsections 97, 98 together with a deflection region 87 form a first flow channel 100.
  • the tubes 88, 89 are received in tube ends 83 and 84 at the ends.
  • the tubes 88 and 89 are surrounded by the housing 82.
  • a second flow channel 99 is formed, which can be traversed by a second fluid.
  • the tube plate 83 is inserted in the housing 82 in a fluid-tight manner.
  • the housing 82 is connected in a fluid-tight manner to the housing part 85 such that the deflection area 87 and the tube bottom 93 are received within the housing part 85.
  • the flow path 94 as already in Fig. 4 indicated by means which reduce the cross-section, or are designed by turbulence inserts such that an optimal heat exchange between the first fluid in the deflection region 87 and the second fluid in the flow path 94 takes place.
  • the provision of means for reducing the cross section of the flow path 94 and / or turbulence inserts can influence the resulting pressure loss in the flow path 94.
  • the deflection region 87 is formed, as in the preceding figures, by a cover 101, which is inserted into the tubesheet 84 and sealed with a sealing agent 93, such that the fluid flow of the first fluid within the deflection region 87 of the fluid flow of the second fluid in the Flow path 94 and within the housing 82 is separated. The deflection within the deflection region 87 takes place along the flow direction 96.
  • the housings 2, 22, 42, 45, 82 and 85 can be formed both from a plastic and from a metallic material. The corresponding material has to be adapted to the application condition. If the respective housing 2, 33, 43, 45, 82 and 85 flows through a second fluid, the connection between the respective tube plates 6, 16, 23, 26, 46, 56, 83, 84 and the housing 2, 22nd , 42, 82 and the additional housing part 45, 85 be designed so fluid-tight that no leaks to the environment or in the circulation of the first fluid arise.
  • Fig. 1 to 6 and 8th All features of Fig. 1 to 6 and 8th can be combined individually.
  • the embodiments 1 to 6 and 8 have no limiting character.
  • the geometries and the arrangement of the individual components to each other and the choice of materials are the Fig. 1 to 6 and 8th by way of example and serve to clarify the inventive idea.

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

Claims (9)

  1. Echangeur de chaleur (1, 21, 41, 81) comprenant un premier conduit d'écoulement (15, 39, 55, 100) qui peut être traversé par un premier fluide, et comprenant un deuxième conduit d'écoulement (14, 38, 54, 99) qui peut être traversé par un deuxième fluide, où le premier conduit d'écoulement (15, 39, 55, 100) présente un premier tronçon partiel (12, 36, 52, 97), un deuxième tronçon partiel (13, 37, 53, 98) et une zone de retour de flux, où le premier tronçon partiel est en communication fluidique avec le deuxième tronçon partiel, via la zone de retour de flux (7, 27, 47, 87), et le premier tronçon partiel (12, 36, 52, 97), le deuxième tronçon partiel (13, 37, 53, 98) et la zone de retour de flux (7, 27, 47, 87) peuvent être entourés par le deuxième fluide, où le premier tronçon partiel (12, 36, 52, 97) et / ou le deuxième tronçon partiel (13, 37, 53, 98) du premier conduit d'écoulement (15, 39, 55, 100) est formé à chaque fois par une pluralité de tubes (8, 9, 28, 29, 48, 49, 88, 89), où l'échangeur de chaleur présente un carter (42, 45, 82, 85) qui est configuré en étant monobloc ou en se composant de plusieurs parties comprenant au moins une première partie de carter (42, 82) et une deuxième partie de carter (45, 85), où un trajet d'écoulement du deuxième conduit d'écoulement (35, 94) est configuré entre une paroi extérieure (25, 101) délimitant la zone de retour de flux (27, 87), et une paroi intérieure du carter (22, 82, 85) et / ou une paroi du premier conduit d'écoulement (39, 100), lequel trajet d'écoulement peut être parcouru par le deuxième fluide, caractérisé en ce que des pièces intercalaires (34) générant des turbulences sont disposées le long du trajet d'écoulement (35) et / ou des moyens (34) diminuant la section sont disposés sur la paroi extérieure de la zone de retour de flux (27) et / ou sur la paroi intérieure du carter (22).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le carter (42, 45, 82, 85) forme au moins partiellement le deuxième conduit d'écoulement (35, 94).
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que la première partie de carter (42, 82) entoure le premier et le deuxième tronçon partiel (12, 36, 52, 97, 13, 37, 53, 98), et la deuxième partie de carter (45, 85) entoure la zone de retour de flux (47, 87).
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce qu'une plaque tubulaire (16, 23, 56, 84) forme, avec un couvercle (17, 25, 57, 101), un bac collecteur, où le volume intérieur du bac collecteur forme la zone de retour de flux (7, 27, 47, 87).
  5. Echangeur de chaleur (21, 41, 81) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le carter (22, 42, 45, 82, 85) présente un premier raccord de fluide (32, 33, 43, 44) et un deuxième raccord de fluide (32, 33, 43, 44) par lequel le deuxième fluide peut être amené dans le carter (22, 42, 45, 82, 85) et évacué du carter (22, 42, 45, 82, 85).
  6. Echangeur de chaleur (1, 21, 41, 81) selon l'une quelconque des revendications précédentes 1 à 5, caractérisé en ce que le premier tronçon partiel (12, 36, 52, 97) et le deuxième tronçon partiel (13, 37, 53, 98) et / ou la zone de retour de flux (7, 27, 47, 87) du premier conduit d'écoulement (15, 39, 55, 100) placé dans le carter (2, 22, 42, 45, 82, 85), qui forme au moins partiellement le deuxième conduit d'écoulement (14, 38, 54, 99), peuvent être intégrés ou sont intégrés de manière telle, que le deuxième conduit d'écoulement (14, 38, 54, 99) soit étanche au fluide par rapport au premier conduit d'écoulement (15, 39, 55, 100) et / ou par rapport à la zone de retour de flux (7, 27, 47, 87) et soit rendu étanche par rapport au milieu environnant.
  7. Echangeur de chaleur (1, 21, 41, 81) selon l'une quelconque des revendications précédentes, caractérisé en ce que tous les tubes (8, 9, 28, 29, 48, 49, 88, 89) sont logés au moins au niveau d'une zone d'extrémité commune située dans une plaque tubulaire (6, 16, 23, 26, 46, 56, 83, 84).
  8. Echangeur de chaleur (1, 21, 41, 81) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'alimentation en fluide et l'évacuation du fluide se produisant dans et hors du premier conduit d'écoulement (15, 39, 55, 100) sont disposées au niveau d'une zone d'extrémité commune de l'échangeur de chaleur (1, 21, 41, 81).
  9. Procédé pour l'utilisation d'un échangeur de chaleur (1, 21, 41, 81) selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier fluide est un gaz et le deuxième fluide est un liquide de refroidissement.
EP14189402.2A 2013-10-17 2014-10-17 Échangeur de chaleur Active EP2863157B1 (fr)

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DE201310221151 DE102013221151A1 (de) 2013-10-17 2013-10-17 Wärmeübertrager

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EP2863157B1 true EP2863157B1 (fr) 2017-12-27

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EP (1) EP2863157B1 (fr)
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DE (1) DE102013221151A1 (fr)

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DE102017218254A1 (de) * 2017-10-12 2019-04-18 Mahle International Gmbh Abgaswärmeübertrager
DE102017130153B4 (de) * 2017-12-15 2022-12-29 Hanon Systems Vorrichtung zur Wärmeübertragung und Verfahren zum Herstellen der Vorrichtung
WO2019183312A1 (fr) 2018-03-23 2019-09-26 Modine Manufacturing Company Échangeur de chaleur liquide-réfrigérant apte à la haute pression

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Also Published As

Publication number Publication date
EP2863157A1 (fr) 2015-04-22
DE102013221151A1 (de) 2015-04-23
US20150107807A1 (en) 2015-04-23
CN104567474A (zh) 2015-04-29

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