EP2825832B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2825832B1
EP2825832B1 EP13710830.4A EP13710830A EP2825832B1 EP 2825832 B1 EP2825832 B1 EP 2825832B1 EP 13710830 A EP13710830 A EP 13710830A EP 2825832 B1 EP2825832 B1 EP 2825832B1
Authority
EP
European Patent Office
Prior art keywords
tubes
fluid
segment
heat exchanger
tube
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
EP13710830.4A
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German (de)
English (en)
Other versions
EP2825832A2 (fr
Inventor
Klaus Irmler
Peter Geskes
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
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 Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2825832A2 publication Critical patent/EP2825832A2/fr
Application granted granted Critical
Publication of EP2825832B1 publication Critical patent/EP2825832B1/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
    • 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
    • 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
    • F28D7/163—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • 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
    • 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
    • F28D7/1615—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 being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
    • F28D7/1623—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 being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium 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
    • 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
    • F28D2021/0085—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • thermocouples Various methods are currently being tested for this energy recovery. So there are approaches to recover the energy content electrically by means of thermocouples. However, this is currently still low Limited services, so that only about 1 kW in passenger cars is achieved.
  • This recovery can be thermal, i. the energy of the exhaust gas is used to heat the passenger compartment or to heat the engine and / or transmission.
  • thermal energy is also extracted from the exhaust gas, the energy is returned to the engine in mechanical form.
  • the method is based on a steam power process in which a particular suitable medium in an evaporator is vaporized and superheated and expanded in an expander or turbine to generate mechanical energy.
  • the evaporation of the medium takes place by means of a heating via the hot exhaust gas.
  • the medium can be brought to a higher pressure. In the case of water as the medium, about 40-50 bar can be achieved. When using organic refrigerants pressures up to about 30 bar are advantageous.
  • the medium to be evaporated is heated in a so-called evaporator in a first step to boiling temperature, then evaporated and then superheated. This can happen in a vehicle in two different locations.
  • a so-called evaporator used in place of or in addition to the exhaust gas cooler, heat may be extracted from the exhaust gas to vaporize the fluid to be evaporated.
  • the main exhaust gas flow can also be used as a heat source in order to evaporate a fluid in a so-called main exhaust gas evaporator.
  • disk evaporator From the air conditioning technology for vehicles are so-called disk evaporator according to the WO 2011/051163 A2 have become known in which ribs are soldered between disc pairs and in which a number of such pairs of discs are connected in parallel. In this case, a fluid flows through the pairs of discs and another fluid flows around them usually. In the discs then the fluid flowing through evaporates when the exhaust gas flows around the discs.
  • Disc and ribbed evaporators have a high power density, which makes it possible to provide even very compact high performance evaporators for vehicles.
  • the disadvantage, however, is that such evaporators are relatively expensive to manufacture.
  • the US 1 799 471 A discloses a heat exchanger according to the preamble of claim 1.
  • a preferred embodiment discloses a heat exchanger, such as in particular exhaust gas evaporator, with a housing having a fluid inlet and a fluid outlet for a first medium, such as in particular exhaust gas, arranged in the housing transversely to the flow direction of the first fluid tubes, which are flowed through by a second medium and inlet side and arranged on the outlet side in a tubesheet with their ends and are fluid-tightly connected to the respective tubesheet, respectively a structure by means of which groups of tubes are interconnected such that an outlet of at least one tube is fluidly connected to an inlet of at least one other tube , It is particularly advantageous if the respective outlet from a group of tubes is connected to a respective inlet of a group of tubes.
  • the structure consists of a baffle and a cover plate, wherein the baffle plate has openings which connects the outlets of a tube with the inlets of the other tubes, and wherein the cover plate covers the baffle fluid-tight.
  • the baffle plate is connected to the tubesheet and has openings within which inlets and outlets of a predeterminable number of tubes are in fluid communication.
  • baffle plate is integrally formed with the respective tubesheet, wherein the cover plate is placed on the respective baffle plate and connected thereto.
  • baffle plate is integrally formed with the respective cover plate, wherein the baffle plate and the cover plate are placed on the respective tube sheet and connected thereto.
  • the tubes are arranged in rows, wherein the deflecting plate deflects fluid between tubes of different rows.
  • the baffle deflects fluid from a first tube or from a group of first tubes into a second tube or into a group of second tubes, wherein the first tubes and the second tubes are preferably arranged in a different row of tubes.
  • the baffle deflects fluid between tubes of a series is particularly advantageous. This means that the baffle deflects fluid from a first tube or from a group of first tubes into a second tube or into a group of second tubes, wherein the first tubes and the second tubes are preferably arranged in a same row of tubes.
  • the rows of tubes are arranged in segments, wherein the deflecting plate deflects fluid from one segment to another segment.
  • FIGS. 1 and 2 show a heat exchanger 1, which in the embodiment of FIG. 1 designed as an exhaust gas evaporator.
  • the exhaust gas evaporator is flowed through by a first fluid, here preferably exhaust gas, and by a second fluid, here a fluid to be vaporized.
  • the exhaust gas transfers heat to the fluid to be evaporated and evaporates it.
  • the heat exchanger 1 in this case has a housing 2 with a fluid inlet 3 and a fluid outlet 4 for a first fluid.
  • the exhaust gas flows through the housing from the inlet 3 to the outlet 4, wherein between inlet 3 and outlet 4, a series of tubes 5 are preferably arranged transversely to the flow direction 7 of the first fluid, which can be traversed by a second fluid.
  • ribs 6 conveying the heat transfer are provided on the outside around the tubes 5 and / or between the tubes 5. These can be provided as corrugated ribs or as plane ribs or turbulence generators.
  • the tubes 5 for the flow through the second fluid are preferably round tubes or flat tubes. These are preferably fluid-tightly received on both sides with their ends in tube sheets.
  • the tubes 5 are preferably arranged on the inlet side and outlet side in a tube plate 8 with their ends 9 and connected fluid-tight.
  • the heat exchanger is connected to an inlet port 10 for the inlet of the second fluid and to an outlet port 11 to the outlet. From the inlet, the fluid distributes to a first number of tubes. These are preferably flowed through in parallel by the second fluid. Subsequently, the fluid is deflected at the opposite ends of these tubes in a further number of other tubes. These are again flowed through by the second fluid.
  • a respective structure 12 is connected to the respective tube sheet 8, by means of which groups of tubes 5 are connected to each other such that an outlet 15 of at least one tube 5 is fluidly connected to an inlet 16 of at least one other tube 5.
  • the structure 12 consists of at least one baffle plate 13 and a cover plate 14 which are formed and arranged one above the other.
  • the cover plate 14 covers the baffle 13 fluid-tight.
  • the cover plate 14 is welded to the baffle 13 or soldered or glued or even formed in one piece.
  • the baffle plate 13 has openings which connect the outlets 15 of one tube 5 to the inlets 16 of the other tubes 5.
  • the tubes 5 are inserted on at least one side in the tube sheet 8 in openings 17, where the tubes are soldered or welded to the ground.
  • the material for the tubes and tube sheets aluminum but most preferably stainless steel can be used. Also, the entire heat exchanger made of aluminum or stainless steel.
  • the baffle 13 has openings or channel structures adapted to connect outlets of pipes to inlets of other pipes.
  • baffle plate 13 and cover plate 14 it may also be advantageous if the baffle plate is formed with the tube sheet to a part or the baffle plate is formed with the cover plate as a part.
  • FIG. 4 It is shown that the baffle plate is formed with the tube sheet to a part 18.
  • FIG. 5 It is shown that the baffle plate is formed with the cover plate to a part 19.
  • the tubesheet can also be designed such as milled, for example, that the so multifunctional modified tube sheet also takes on the task of fluid distribution and acts as a combination of bottom plate and baffle. Then only a cover plate is placed and connected to the ground. Accordingly, the part 19 can also act as a milled component, which integrated deflection plate and cover plate.
  • tubesheet and / or the baffle plate and / or the cover plate may also be formed as a casting, which has a corresponding structure with recessed integrated openings for distribution of the medium.
  • connection of the two or three elements tube plate, baffle and cover plate is advantageously carried out by welding, soldering or screwing, whereby a combination of the connection options can be used.
  • the top plate can also have holes to distribute at certain points over the surface to connect by welding the plates together.
  • the 3 plates can be fixed to each other by means of rivets or tack welds and pressed together, alternatively on welds, embossing or screwing.
  • the baffle contains openings as structures to collect the medium from at least one tube and redistribute it to at least one other tube.
  • the fluid to be vaporized is collected in the ports and then re-divided into up to four or more other tubes.
  • FIG. 6 schematically shows a core 20 of the heat exchanger 1, in which a plurality of tubes 5 is arranged. These tubes 5 are arranged between the distributor plates 21, 22 formed as deflection regions and received there in tube plates and deflecting and cover plates.
  • the distributor plates 21, 22 are divided into individual segments 24, 25, 26, 27, 28 and 29 when viewed in the exhaust gas flow direction 23.
  • a number of tube rows 30, 31 are again provided.
  • two rows of tubes are provided.
  • a segment consists of only a few Tube rows, for example, two rows of tubes in the exhaust gas flow direction, so that the temperature gradient over a segment is as small as possible and thus all tubes are subjected to almost the same exhaust gas temperature.
  • a segment Depending on the working medium but can also form up to 6 rows of tubes a segment, or several segments are interconnected in parallel.
  • FIG. 6 In the embodiment of FIG. 6 continue to be connected in parallel to each tube row 30, 31 up to 4 tubes perpendicular to the exhaust gas flow direction.
  • the second fluid flows in the region of the tube ends 32 and is distributed over four tubes 5.
  • the fluid flows through these tubes to the ends of these tubes on the opposite side and flows out there into the region 33.
  • the deflection region 35 directs the fluid into the inlets of the region 34, from where the fluid flows back through the respective tubes back to the region 36. Subsequently, the fluid is deflected by the deflection region 37 to the region 38 of the tube ends and distributed, so that the fluid now flows back through tubes that lie below the first passage.
  • the first segment flows through in alternating flows and the fluid finally exits the region 39 from the segment and is diverted at the transition 40 from the first segment 29 into the second segment 28.
  • the corresponding flow through the second segment 28 takes place until the fluid flows over the passage 41 into the third segment 27.
  • the corresponding flow through the third segment 27 takes place until the fluid flows over the passage 42 into the fourth segment 26.
  • the corresponding flow through the fourth segment 26 takes place until the fluid flows over the transition 43 into the fifth segment 25.
  • the corresponding flow through the fifth segment 25 until the fluid flows over the passage 44 into the sixth segment 24.
  • the corresponding flow through the sixth segment 24 takes place until the fluid at the outlet 4 flows out of the sixth segment 24.
  • FIGS. 7 and 8th show once again the connection configuration of the tubes at the front and at the rear deflection area. It can be seen that in each case four tubes are connected in parallel and a diversion of fluid from four tubes into four other tubes takes place. The fluid enters the front according to FIG. 7 in tubes 5, from which it emerges at the rear side. Therefore, the tubes 5 are in the front deflection according to FIG. 7 also with the complementary entries or withdrawals as in FIG. 8 characterized.
  • FIG. 9 shows a corresponding view of six segments 50 to 55, each having two rows of tubes.
  • three tubes are combined to form a passage 56 and connected in parallel.
  • the fluid flows in and flows through the tubes to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes.
  • the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. This takes place until the fluid in the region 57 flows out of the tubes and is transferred through the passage 58 into the next segment.
  • the passage may preferably be integrated in the baffle or carried out by an external transfer via pipe.
  • the flow through the heat exchanger of FIG. 9 shows a difference from the previous embodiment.
  • the deflection of the fluid in the front baffle of tubes takes place in tubes of the same row according to opening 60, while in the rear baffle a diversion of tubes of one row into tubes of another row according to opening or openings 59 takes place.
  • FIG. 10 shows a further embodiment in a further view, wherein six segments 70 to 75 each have two rows 76,77 of tubes. As can be seen, the segments 71 and 72 are combined to form a common parallel-connected segment. The same applies to segments 73 and 74.
  • each case three tubes are combined to form a passage 78 and connected in parallel.
  • the fluid flows in and flows through the tubes to the rear deflection region.
  • the fluid is deflected from one row of tubes to the adjacent row of tubes through openings 79 in the baffle plate.
  • the fluid flows through the next three tubes and is deflected in the front deflection region in the same row of tubes in three more tubes through the opening 80 of the front baffle plate.
  • the fluid flows through the tubes to the rear deflection region.
  • the fluid is redirected from one row of tubes to the adjacent row of tubes.
  • the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. This takes place until the fluid in the region 81 flows out of the tubes and is transferred through the passage 82 into the next segment 71, 72.
  • the passage 82 may preferably be integrated in the baffle or carried out by an external transfer via pipe.
  • the flow through takes place as in the segment 70, although these are connected in parallel and the fluid enters the regions 83 and 84 in parallel. Subsequently, the tubes of the segments 71 and 72 are flowed through like the tubes of the segment 70, before the fluid is again discharged from the segment at the regions 85 and 86 and transferred into the parallel segments 73 and 74 by means of the transition 87. In the segments 73 and 74, the flow through as in the segments 71 and 72. Subsequently, the fluid from the segments 73 and 74 is collected and introduced into the final segment 75, where it flows through the segment 75 as in the input-side segment 70 before it is discharged from the heat exchanger.
  • FIG. 11 shows a further embodiment in a further view, wherein six segments 90 to 95 each have two rows 96,97 of tubes. As can be seen, the segments 90 and 91 are combined into a common parallel-connected segment. The same applies to the segments 92, 93 and 94, which are combined into a common segment.
  • the fluid flows in and flows through a tube to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes through an opening 105 in the baffle plate. Subsequently, the fluid flows through the next tube and is deflected in the front deflection region in the same row of tubes in another tube through the opening 106 of the front baffle plate. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube. This takes place until the fluid flows out in the mixing zone 100.
  • the passage 107 may preferably be integrated in the baffle plate or by an external passage via pipe.
  • the flow takes place as in the segment 90, 91, although these are all connected in parallel. Subsequently, the tubes of the segments 92 to 94 are flowed through, before the fluid is again discharged from the segment and transferred to the segment 95 by means of the transfer 108. In the segment 95, the flow takes place as in the segment 70 of FIG. 10 in which three tubes are connected in parallel. Subsequently, the fluid is discharged from the heat exchanger.
  • FIG. 12 shows a further embodiment in a further view, wherein six segments 110 to 115 each have two rows 116, 117 of tubes. As can be seen, the segments 110 to 112 and 113 to 115 are combined to form a common parallel-connected segment.
  • each tube 116 is parallel to a tube 117, 118 of the other Segments flows through.
  • the tubes 116, 117 or 118 are only flowed through serially. This is done up to the middle of the segment.
  • the fluid flows out of the tubes 119, 120, 121 of the three segments.
  • the fluid flows in and flows through a tube to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes through an opening in the baffle plate. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube through the opening of the front baffle plate. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube. This takes place until the fluid flows out in the mixing zone 122.
  • the passage 126 may preferably be integrated in the deflection plate or be made by an external passage via pipe.
  • baffle The design of the baffle is provided rectangular in the figures. It can also be round, so that it can be installed in a round, cylindrical recess in a housing or in a silencer.
  • the gas-side ribs form the so-called secondary surface of the heat transfer and the tubes represent the primary surface of the heat transfer.
  • the ribs 6 can be soldered to the tubes 3 or a thermally conductive connection is achieved without the addition of solder during the soldering process of the entire evaporator. This can be achieved by a very tightly tolerated pipe run, which leads to a very small gap between the rib and pipe.
  • a thermally conductive connection between the ribs and the tubes is made, even if no solder should be present.
  • a better connection of the ribs with the pipes, whether with or without solder, can be achieved by a combination of austenitic pipes and ferritic ribs.
  • Ferrites have a lower expansion at high temperatures than austenite, so that the tubes are pressed against the ribs at soldering temperature.
  • the rib may have small slits around the tubes.
  • the ribs have pipe passages with so-called collar, through which the distance between the ribs is ensured.
  • the rib spacing can also be ensured by exhibiting spacers in the rib.
  • the rib density can be between 30 Ri / dm and 80 Ri / dm.
  • the ribs can be punched and have cut and erect gills or even embossed structures, such as winglets, dimples or bulges, to increase performance. In particular It is expedient to impress such structures in the ribs, which directs the flow targeted to the pipes and thus a higher heat transfer can be achieved on the primary surface.
  • the rib thickness is 0.1 mm to 0.5 mm or preferably between 0.25 and 0.4 mm, which is advantageous for stainless steel as a ribbed material.
  • slots can be introduced in the composite of the plates above and / or below, so that a different thermal expansion due to different temperatures from the gas inlet to the gas outlet is made possible and does not lead to damage.
  • the pipe diameter of the pipes is preferably in the range of 3 to 20 mm, ideally in the range of 5 to 15 mm and preferably in the range of 6 to 10 mm.
  • Turbulence generating structures can be incorporated into the tubes, e.g. Swirl generator to promote heat transfer especially in the area where the fluid overheats.
  • the tube can also be designed as a spiral tube, but then preferably without outer ribs.
  • pipes with very deep grooves are used, which are similar to a bellows with larger pipe diameters formed in order to increase the heat transfer on the gas side and at the same time can absorb the thermal expansion difference between the tubes.
  • different performance classes can be achieved when an evaporator in the exhaust gas flow direction consists of individual modules.

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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)

Claims (9)

  1. Echangeur de chaleur (1), comme en particulier un évaporateur de gaz d'échappement, comprenant un carter (2) comportant une entrée de fluide (3) et une sortie de fluide (4) pour un premier milieu, comme en particulier des gaz d'échappement, ledit échangeur de chaleur comprenant des tubes (5) disposés dans le carter (2) de manière transversale par rapport à la direction d'écoulement du premier fluide, tubes qui peuvent être traversés par un deuxième milieu et sont disposés, côté entrée et côté sortie, en ayant leurs extrémités placées dans un plateau à tubes (8) et en étant reliés de façon étanche aux fluides, où une structure (12) est assemblée à chaque fois avec le plateau à tubes respectif (8), structure au moyen de laquelle des groupes de tubes (5) sont reliés entre eux de manière telle, qu'une sortie d'au moins un tube (5) soit en communication fluidique avec une entrée d'au moins un autre tube (5), caractérisé en ce que la structure (12) se compose d'une plaque de retour de flux (13) et d'une plaque de recouvrement (14), où la plaque de retour de flux (13) présente des ouvertures qui relient les sorties de l'un des tubes (5), aux entrées des autres tubes (5), et où la plaque de recouvrement (14) recouvre la plaque de retour de flux (13), de façon étanche aux fluides.
  2. Echangeur de chaleur (1) selon la revendication 1, caractérisé en ce que la plaque de retour de flux (13) est placée sur le plateau à tubes respectif (8) et est assemblée avec celui-ci, où la plaque de recouvrement (14) est placée sur la plaque de retour de flux respective (13) et assemblée avec celle-ci.
  3. Echangeur de chaleur (1) selon la revendication 1, caractérisé en ce que la plaque de retour de flux (13) est configurée de façon monobloc avec le plateau à tubes respectif (8), où la plaque de recouvrement (14) est placée sur la plaque de retour de flux respective (13) et assemblée avec celle-ci.
  4. Echangeur de chaleur (1) selon la revendication 1, caractérisé en ce que la plaque de retour de flux (13) est configurée de façon monobloc avec la plaque de recouvrement respective (14), où la plaque de retour de flux (13) et la plaque de recouvrement (14) sont placées sur le plateau à tubes respectif (8) et assemblées avec celui-ci.
  5. Echangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes (5) sont disposés en rangées, où la plaque de retour de flux (13) change la direction du fluide circulant entre des tubes (5) de différentes rangées.
  6. Echangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes (5) sont disposés en rangées, où la plaque de retour de flux (13) change la direction du fluide circulant entre des tubes (5) d'une même rangée.
  7. Echangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les rangées de tubes (5) sont disposées en segments, où la plaque de retour de flux (13) change la direction du fluide en circulation, passant d'un segment dans un autre segment.
  8. Echangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que des tubes formant une pluralité de tubes (5) sont montés en parallèle au moins dans un segment.
  9. Echangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que des tubes formant une pluralité de tubes (5) montés en parallèle sont reliés les uns aux autres, en série, au moins dans un segment.
EP13710830.4A 2012-03-16 2013-03-14 Échangeur de chaleur Not-in-force EP2825832B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012204151A DE102012204151A1 (de) 2012-03-16 2012-03-16 Wärmeübertrager
PCT/EP2013/055226 WO2013135808A2 (fr) 2012-03-16 2013-03-14 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP2825832A2 EP2825832A2 (fr) 2015-01-21
EP2825832B1 true EP2825832B1 (fr) 2019-01-09

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EP13710830.4A Not-in-force EP2825832B1 (fr) 2012-03-16 2013-03-14 Échangeur de chaleur

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US (1) US20150060028A1 (fr)
EP (1) EP2825832B1 (fr)
DE (1) DE102012204151A1 (fr)
WO (1) WO2013135808A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220212A1 (de) * 2013-10-07 2015-04-09 Behr Gmbh & Co. Kg Wärmeübertrager
EP3163244B1 (fr) * 2015-10-28 2019-08-14 Borgwarner Emissions Systems Spain, S.L.U. Évaporateur
EP3163243B1 (fr) * 2015-10-28 2019-08-14 Borgwarner Emissions Systems Spain, S.L.U. Évaporateur
DE102016215265A1 (de) * 2016-08-16 2018-02-22 Mahle International Gmbh Herstellungsverfahren eines Wärmeübertragerrohres
JP6696537B2 (ja) * 2018-08-09 2020-05-20 ダイキン工業株式会社 圧縮機、および、圧縮機の製造方法
DE102019108213A1 (de) * 2019-03-29 2020-10-01 Mahle International Gmbh Wärmeübertrager
DE102019204640A1 (de) * 2019-04-02 2020-10-08 Mahle International Gmbh Wärmeübertrager

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1542613A (en) * 1921-10-31 1925-06-16 Edwin R Cox Heat exchanger
US1799471A (en) * 1926-10-26 1931-04-07 Leach Charles Harold Heat-exchange apparatus
US1979975A (en) * 1933-04-19 1934-11-06 Maniscalco Pietro Heat exchanging device
US2064036A (en) * 1935-08-12 1936-12-15 Oakes Prod Corp Method of making a condenser
US2950092A (en) * 1957-11-01 1960-08-23 Carrier Corp Heat exchange construction
DE1905048U (de) * 1964-09-17 1964-11-26 Bertrams Ag Hch Heisswasserbeheizter waermeaustauscher.
US3430692A (en) * 1967-06-16 1969-03-04 John Karmazin Return bend construction for heat exchangers
DE2013958A1 (en) * 1970-03-24 1971-10-14 Alfa Laval Bergedorfer Eisen Tube heat exchanger end plate
DE3921531A1 (de) * 1988-07-05 1990-01-11 Vaillant Joh Gmbh & Co Waermetauscher mit gegenlaeufig durchstroemten rohren oder dergleichen
IT1245799B (it) * 1991-03-19 1994-10-18 Piero Pasqualini Scambiatore di calore per fluidi
NL9101227A (nl) * 1991-07-11 1993-02-01 Vomatec B V Inrichting voor het in doorstroom verwarmen van een stof.
FR2803378B1 (fr) * 1999-12-29 2004-03-19 Valeo Climatisation Echangeur de chaleur a tubes a plusieurs canaux, en particulier pour vehicule automobile
JP4180935B2 (ja) * 2003-02-04 2008-11-12 リンナイ株式会社 熱交換器及び温水加熱器
JP2005326135A (ja) * 2004-04-12 2005-11-24 Showa Denko Kk 熱交換器
ES2322728B1 (es) * 2005-11-22 2010-04-23 Dayco Ensa, S.L. Intercambiador de calor de tres pasos para un sistema "egr".
EP2131131A1 (fr) * 2008-06-06 2009-12-09 Scambia Industrial Developments AG Échangeur de chaleur
DE102009050889A1 (de) 2009-10-27 2011-04-28 Behr Gmbh & Co. Kg Abgasverdampfer

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2013135808A3 (fr) 2013-11-07
US20150060028A1 (en) 2015-03-05
WO2013135808A2 (fr) 2013-09-19
EP2825832A2 (fr) 2015-01-21
DE102012204151A1 (de) 2013-09-19

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