EP2567172B1 - Échangeur de chaleur à plaques empilées - Google Patents

Échangeur de chaleur à plaques empilées Download PDF

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Publication number
EP2567172B1
EP2567172B1 EP11718066.1A EP11718066A EP2567172B1 EP 2567172 B1 EP2567172 B1 EP 2567172B1 EP 11718066 A EP11718066 A EP 11718066A EP 2567172 B1 EP2567172 B1 EP 2567172B1
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EP
European Patent Office
Prior art keywords
dome
heat exchanger
elongated
plate
hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11718066.1A
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German (de)
English (en)
Other versions
EP2567172A2 (fr
Inventor
Volker Velte
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 International GmbH
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Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Priority to PL11718066T priority Critical patent/PL2567172T3/pl
Publication of EP2567172A2 publication Critical patent/EP2567172A2/fr
Application granted granted Critical
Publication of EP2567172B1 publication Critical patent/EP2567172B1/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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/086—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning having one or more openings therein forming tubular heat-exchange passages

Definitions

  • the invention relates to a stacked plate heat exchanger having a plurality of stacked and interconnected elongated discs having a cavity for passing a medium to be cooled in the longitudinal direction of the discs and defining a further cavity for carrying a coolant, wherein approximately in the two end regions of each elongated disc a through hole for supplying the medium to be cooled is arranged, which is surrounded at least partially by a dome at its boundary.
  • a heat exchanger according to the preamble of claim 1 is for example from the JP 11-193998 known.
  • FIG. 1 shows an elongated disc of a stacked plate heat exchanger, which is cooled with oil.
  • the elongated disk 1 has a disk circulation 2 as well as a plurality of circular segment-shaped punched through holes 3. At least two of the circular segment-shaped through holes 3 are surrounded by a dome 4 (FIG. FIG. 1b ).
  • each through hole 3 has a distance 5 to the edge of the disc. This has the consequence that the effectiveness of the heat exchanger is limited, since not all areas of the elongated disc are used for heat transfer.
  • FIG. 2 A similar arrangement results in a stacked plate heat exchanger, which is cooled with air and in FIG. 2 is shown.
  • the stacked plate heat exchanger consists in detail of several elongated discs 6, of which in the FIG. 2 only one is shown. This elongated disc 6 is completely surrounded by a disc circulation 7.
  • Each disc 6 has two through holes 8 for the medium to be cooled and further two through holes 9 for the coolant. How out FIG. 2b As can be seen, both the through-hole 8 and the through-hole 9 are surrounded by a dome 10, 11. Such a dome 10, 11 in the discs 6 is necessary to separate the coolant from the medium to be cooled in the heat exchanger.
  • the dome is disposed adjacent to a circuit defining a base plate of the elongated disk.
  • the available space is fully utilized, since the heat exchange takes place over the entire surface of the elongated disc.
  • the dome is arranged in a different plane than the circulation of the elongated disc, wherein the dome is preferably embossed into the base plate or protrudes raised from the base plate. This arrangement results in an improved stackability of the individual disks of the heat exchanger.
  • the dome completely fills a space between a circuit defining a base plate of the disk and the respective through hole.
  • the through hole is arranged in a different plane than the elongated disc. Also by this training, the stackability of the elongated discs improves.
  • the dome has a plurality of elongate holes supplying the coolant. This increases the compactness of the component, since the dome both used as a spacer to the overlying elongated disc is received as well as on the same surface, the slots for the passage of the coolant.
  • the through hole is formed approximately circular segment-shaped, wherein the holes surrounding the through holes are formed circular arc-shaped.
  • the dome of a first elongated disc with a further elongate disc arranged underneath or above forms an annular channel which is interrupted by the oblong holes.
  • the base plate may lie in a first plane which lies between a second plane in which the respective through hole lies and a third plane in which the elongated holes lie. This results in a narrow space a multi-tiered structure, which is characterized by a high rigidity.
  • the mold may be at least partially integrated into a circulation delimiting a base plate of the elongated disk.
  • the circulation and the dome so to speak, merge into one another and allow a double use of the respective wall section.
  • the structure is thereby particularly compact.
  • an outer wall of the dome running along the edge of the disk is integrated into the circulation.
  • said outer wall of the dome forms part of the circulation when the dome and circulation are located on the same side of the disk, or an integral extension of the circulation when the dome and circulation are located on opposite sides of the disk. This also results in a particularly compact design.
  • the dome is formed with a predetermined angle of inclination, which is guided in particular inwardly to the through hole.
  • the stackability of the elongated disks is further improved, since gaps which can occur in the soldering of the disks lying on top of one another are prevented.
  • a segment between a terminal region of the dome and the circulation is formed, whose further inclination angle is greater than the predetermined inclination angle of the dome, wherein the deviation of the predetermined inclination angle of the dome to the further inclination angle of the segment is approximately 5 °.
  • the segment is arranged at the level of the dome and terminates with the circulation of the elongated disc.
  • This design requires only a small change in the degree of deformation in the manufacture of the dome.
  • a cam is formed on the dome, which approximately has the predetermined angle of inclination of the circulation and preferably extends parallel to the dome.
  • the end region of the arc-shaped dome is designed semicircle-like.
  • the design of the end portion of the dome provides the cam with a kind of closure to limit any liquid entering the heat exchanger through that channel.
  • the cam can be kept very small in size.
  • the cam has an extension of less than 6 mm.
  • dome and at least one cam are integrally formed from the elongated disc. These parts can be easily manufactured as stamped parts. The production takes place in a single step, for which only simple tools are needed. As a result, the production costs are significantly reduced.
  • the elongated disc is formed of solderable aluminum.
  • This easily deformable material simplifies the manufacture of the stacked plate heat exchanger and reduces material costs.
  • FIG. 3 shows an elongated disc 6 of a stacked plate heat exchanger for air cooling, which is formed oval.
  • This elongated disc 6 consists of a base plate 12, which is adjoined by a boundary 7 at the edge thereof. This boundary 7 is in an angle of approximately 90 ° to the base plate 12 and serves for better stacking of the various discs 6 one above the other.
  • a through hole 8 is arranged in each case, which is machined out of the disc 6.
  • Each through hole 8 is brought so close to the edge of the boundary 7 of the disc 6 that between the through hole 8 and the boundary 7 only a dome 10, which is also referred to as a passage, is arranged.
  • This passage 10 thus completely fills the space between the boundary 7 and the through-hole 8.
  • the through hole 8 is semicircular, wherein the radius of the semicircle is completely surrounded by the passage 10.
  • FIG. 3b is a closer view of a through hole 8 a with the surrounding passage 10 shown.
  • the passage 10 has a plurality of elongated holes 13 which fill the entire surface of the passage 10 and which are the base plate 12 of the elongated disc 6 facing away.
  • the passage 10 is raised above the plane defined by the base plate 12, whereby the elongated holes 13 are positioned in a plane above the plane defined by the base plate 12 level.
  • the medium to be cooled is supplied to the heat exchanger, which through the further through hole 8b, the in FIG. 3a is shown again out of the heat exchanger.
  • the elongated holes 13 serve to supply the cooling medium, in this case air, to the heat exchanger.
  • turbulence inserts are arranged, which are used to generate turbulence, with the aim that the medium to be cooled over the entire surface of the base plate 12 and thus a large thermal contact with the cooling medium achieved.
  • FIG. 3b can be seen, the passage 10 is punched out in a punching operation of the material of the base plate 12 of the elongated disc 6 to the outside.
  • the dome 10 or the passage 10 is at least partially integrated into the circulation 7 of the disc 6, namely in the area of an outer wall of the dome 10 or of the passage 10 which extends along the edge of the disc 6.
  • the example of Fig. 3 stand circulation 7 and outer wall of the passage 10 on different sides of the disc 6, whereby the passage 10 in the region of its outer wall is an integral extension of the circulation 7.
  • FIG. 4 shows a similar arrangement of the elongated disc 6, which is used for a stacked plate heat exchanger with air cooling.
  • the elongated disc 6 also consists of a base plate 12, which has an oval shape and which is surrounded by a boundary 7.
  • the two through holes 8a, 8b extending at the ends of the elongated disc 6 are each surrounded by a passage 10a, 10b in their radius of the semicircle.
  • the passages 10a, 10b slots 13 for transporting the coolant.
  • the passage 10a, 10b formed inwardly, which means that the base plate 12 of the elongated disc 6 is formed in a higher plane than the slots 13 of the passage 10a, 10b. How out FIG. 4b can be seen, there is thus a step 15 between the base plate 12 and the outer edge of the surface of the passage 8a, 8b.
  • FIGS. 5a and 5c a comparable arrangement for a stacked plate heat exchanger is shown, which is cooled with oil.
  • the elongate disc 1 is formed like a rectangle and has rounded corners, wherein this base plate 14 is completely surrounded by a boundary 2.
  • Four through-holes 3a-3d are arranged in the corners of the base plate 14, of which two opposite through-holes 3b, 3c, which are arranged along one longitudinal side of the base plate 14, each have a passage 4a, 4b ( FIGS. 5a and 5c ).
  • a step jump 15 is present in that the base plate 14 leaves the normal plane and merges with the passage 4a in a plane above it.
  • each through-hole 3a to 3d extends completely into the edge region of the base plate 14, where it is enclosed directly by the boundary 2.
  • the passage 4a, 4b in this case comprises the through holes 3b, 3c completely, wherein a part of the passage 4a, 4b is incorporated into the boundary 2.
  • FIG. 6 a disc 1 is shown for the stacked plate heat exchanger with an oil cooling, in which the passage 4a, 4b is directed inwards.
  • the two passages 4a, 4b are arranged opposite each other to the inside of the base plate 14.
  • the plane spanned by the base plate 14 is higher than the plane in which the through hole 3b, 3c is located.
  • FIG. 7 are sections of the elongated disc 6 of the stacked plate heat exchanger, which is cooled with air, shown. It shows Figure 7a an inwardly impressed passage 10, while in FIG. 7b an outwardly drawn passage 10 is shown. It can be seen from the marked areas that a step jump 15 occurs between the boundary 7 of the base plate 12 and the passage 10 at the point where the base plate 12 merges into the passage 8. Such a step change 15 has, as in FIG. 8 is shown, the problem that in the soldering of several superimposed discs 6, a gap 16 occurs. This gap 16 is particularly in FIG. 8b clarified.
  • FIG. 10 The circumferentially adjacent contact of the disk 6 with the soldering surface is shown again in FIG. 10 for a stacked heat exchanger with several disks 6 lying one above the other. This creates between two superimposed discs 6 a circumferential channel 18.
  • a cam 19 placed to complete this circumferential channel 18 and to prevent leakage of coolant from this channel 18 is in the radius range of the semicircular passage 10, in particular near the two ends of a passage 10, a cam 19 placed.
  • the cam 19 is located at the outer edge of the last slot 13 of the passage 10, the cam 19 a Angle perpendicular to the base plate 12 which is greater than the angle that has the outside of the passage 10 to the base plate 12.
  • the cam 19 is approximately 5 mm wide and located approximately at the radial outlet of the wall of the passage 10 in the vicinity of the segment 17 (see FIGS. 11a and b ).
  • the Figures 11c and 11d show the arrangement of the cam 19 in a section through a plurality of stacked elongated discs 6 of the stacked plate heat exchanger.
  • the cam 19 is positioned in the region of the boundary 7 of the elongated disc 6 and has an obtuse angle to this. When superimposing the discs 6, these are positioned so that the passages 10 of each two adjacent discs 6 are superimposed.
  • FIG. 12 are also stacked discs 6 of the stacked plate heat exchanger shown in cross section.
  • the individual elongated discs 1, 6 of the stacked plate heat exchanger are made of solderable aluminum and form with the described embodiments a compact heat exchanger, which has a high space performance, whereby a maximum degree of heat transfer heat exchange between the medium to be cooled and the coolant is achieved.
  • the compact design of the heat exchanger leads to a reduction in the use of material in the production. In addition, a lower degree of deformation is necessary, resulting in a cost-effective solution.
  • a process-reliable soldering By a circumferential soldering surface is possible without grading, so that a dense heat exchanger is generated.

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

Claims (12)

  1. Echangeur de chaleur à plaques empilées,
    - comprenant une pluralité de plaques (6) allongées empilées les unes sur les autres et reliées entre elles qui présentent un creux pour faire passer un milieu à refroidir dans le sens longitudinal desdites plaques (6) et délimitent un autre creux pour faire passer un fluide de refroidissement,
    - approximativement dans les deux zones d'extrémité de chaque plaque (6) allongée étant disposé un trou de passage (8) destiné à amener le milieu à refroidir, qui est entouré sur sa limite au moins en partie par un dôme (10),
    - ledit trou de passage (8) étant agencé approximativement sur le bord de la plaque (6) allongée,
    - ledit dôme (10) et/ou ledit trou de passage (8) étant intégré(s) au bord de ladite plaque (6) allongée,
    caractérisé par le fait
    - que ledit dôme (10) comble complètement un espace situé entre un rebord périphérique (7) délimitant une plaque de base (12) de la plaque (6) et le trou de passage (8) respectif,
    - que ledit dôme (10) présente une pluralité de trous oblongs (13) amenant le fluide de refroidissement,
    - qu'une paroi extérieure dudit dôme (10), qui s'étend le long du bord de la plaque (6), est intégrée au rebord périphérique (7).
  2. Echangeur de chaleur à plaques empilées selon la revendication 1, caractérisé par le fait que ledit dôme (10) est disposé de manière contiguë à un rebord périphérique (7) délimitant une plaque de base (12) de la plaque (6) allongée.
  3. Echangeur de chaleur à plaques empilées selon la revendication 1 ou 2, caractérisé par le fait que ledit dôme (10) est disposé dans un autre plan qu'un rebord périphérique (7) de la plaque (6) allongée, qui délimite une plaque de base (12) de ladite plaque (6), le dôme (10) étant, de préférence, gravé en creux dans ladite plaque de base (12) ou faisant saillie en relief de ladite plaque de base (12).
  4. Echangeur de chaleur à plaques empilées selon l'une quelconque des revendications 1 à 3, caractérisé par le fait que ledit trou de passage (8) est disposé dans un autre plan que la plaque (6) allongée.
  5. Echangeur de chaleur à plaques empilées selon l'une quelconque des revendications précédentes, caractérisé par le fait
    - que ledit trou de passage (8) est réalisé de manière à présenter approximativement une forme de segment de cercle et/ou les trous oblongs (13) entourant le trou de passage (8) étant réalisés de manière à être courbés en arc de cercle,
    - que le dôme (10) d'une première plaque (6) allongée forme avec une autre plaque (6) allongée disposée là-dessous un canal annulaire qui est interrompu par lesdits trous oblongs (13).
  6. Echangeur de chaleur à plaques empilées selon l'une quelconque des revendications précédentes, caractérisé par le fait que ladite plaque de base (12) est située dans un plan qui est situé entre le plan où est situé le trou de passage (8) respectif et le plan où sont situés les trous oblongs (13).
  7. Echangeur de chaleur à plaques empilées selon l'une au moins des revendications précédentes, caractérisé par le fait que ledit dôme (10) est réalisé avec un angle d'inclinaison donné qui s'étend en particulier vers l'intérieur en direction du trou de passage (8).
  8. Echangeur de chaleur à plaques empilées selon la revendication 7, caractérisé par le fait qu'un segment (17) est réalisé entre une zone terminale du dôme (10) et le rebord périphérique (7), dont l'autre angle d'inclinaison est supérieur audit angle d'inclinaison donné du dôme (10), l'écart de l'angle d'inclinaison donné du dôme (10) par rapport audit autre angle d'inclinaison du segment (17) étant de 5° approximativement.
  9. Echangeur de chaleur à plaques empilées selon la revendication 8, caractérisé par le fait que ledit segment (17) est disposé au niveau du dôme (10) et se termine sur le rebord périphérique (7) de la plaque (6) allongée.
  10. Echangeur de chaleur à plaques empilées selon l'une quelconque des revendications 7 à 9, caractérisé par le fait qu'une came (19) est réalisée sur le dôme (10) à proximité d'au moins une zone terminale du dôme (10), laquelle came présente approximativement l'angle d'inclinaison donné du rebord périphérique (7) et s'étend de préférence parallèlement au dôme (10).
  11. Echangeur de chaleur à plaques empilées selon la revendication 10, caractérisé par le fait
    - que la zone terminale du dôme (10) réalisé en arc de cercle est formée de manière à ressembler à un demi-cercle, et/ou
    - que ladite came (19) présente une extension inférieure à 6 mm, et/ou
    - que le dôme (10) et au moins une came (19) sont réalisés d'un seul tenant à partir de la plaque (6) allongée.
  12. Echangeur de chaleur à plaques empilées selon l'une au moins des revendications précédentes, caractérisé par le fait que la plaque (6) allongée est réalisée en aluminium apte à être brasé.
EP11718066.1A 2010-05-06 2011-05-04 Échangeur de chaleur à plaques empilées Active EP2567172B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11718066T PL2567172T3 (pl) 2010-05-06 2011-05-04 Wymiennik ciepła z płytek ułożonych w stos

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010028660A DE102010028660A1 (de) 2010-05-06 2010-05-06 Stapelscheiben-Wärmetauscher
PCT/EP2011/057091 WO2011138349A2 (fr) 2010-05-06 2011-05-04 Échangeur de chaleur à plaques empilées

Publications (2)

Publication Number Publication Date
EP2567172A2 EP2567172A2 (fr) 2013-03-13
EP2567172B1 true EP2567172B1 (fr) 2015-01-07

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ID=44626182

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11718066.1A Active EP2567172B1 (fr) 2010-05-06 2011-05-04 Échangeur de chaleur à plaques empilées

Country Status (7)

Country Link
US (1) US9557116B2 (fr)
EP (1) EP2567172B1 (fr)
CN (1) CN203464814U (fr)
DE (1) DE102010028660A1 (fr)
HU (1) HUE024508T2 (fr)
PL (1) PL2567172T3 (fr)
WO (1) WO2011138349A2 (fr)

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DK2728293T3 (en) * 2012-10-30 2017-02-27 Alfa Laval Corp Ab HEAT EXCHANGER PLATE AND PLATE HEAT EXCHANGERS INCLUDING SUCH A HEAT EXCHANGE PLATE
CA2885552C (fr) * 2012-10-30 2017-01-03 Alfa Laval Corporate Ab Joint d'etancheite et ensemble
DE102013205242A1 (de) 2013-03-25 2014-09-25 Mahle International Gmbh Abgaskühler
DE102015220579A1 (de) 2015-10-21 2017-04-27 Mahle International Gmbh Stapelscheiben-Wärmeübertrager
ES2664103B1 (es) * 2016-10-17 2019-01-30 Valeo Termico Sa Placa de apilamiento para un intercambiador de calor de placas apiladas y un intercambiador de calor de placas apiladas
CN109751900B (zh) * 2017-11-03 2020-10-16 斗山重工业建设有限公司 包括一体型结构的印刷电路板式热交换器
DE102018206574A1 (de) 2018-04-27 2019-10-31 Mahle International Gmbh Stapelscheibenwärmetauscher
FR3086379B1 (fr) * 2018-09-25 2021-01-29 Valeo Systemes Thermiques Plaque d'echangeur de chaleur a ouverture optimisee
CN112648867A (zh) * 2020-11-30 2021-04-13 合肥通用机械研究院有限公司 一种强化传热的一体化扩散焊热交换器
DE102022124354A1 (de) 2022-09-22 2024-03-28 Mahle International Gmbh Wärmeübertrager bestehend aus zwei Arten von Platten

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Also Published As

Publication number Publication date
WO2011138349A2 (fr) 2011-11-10
CN203464814U (zh) 2014-03-05
PL2567172T3 (pl) 2015-07-31
DE102010028660A1 (de) 2011-11-10
WO2011138349A3 (fr) 2012-02-16
HUE024508T2 (en) 2016-01-28
EP2567172A2 (fr) 2013-03-13
US20130126137A1 (en) 2013-05-23
US9557116B2 (en) 2017-01-31

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