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EP0582835A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0582835A1
EP0582835A1 EP93110974A EP93110974A EP0582835A1 EP 0582835 A1 EP0582835 A1 EP 0582835A1 EP 93110974 A EP93110974 A EP 93110974A EP 93110974 A EP93110974 A EP 93110974A EP 0582835 A1 EP0582835 A1 EP 0582835A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
profile
cooling
exchanger according
tubes
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.)
Granted
Application number
EP93110974A
Other languages
German (de)
English (en)
Other versions
EP0582835B1 (fr
Inventor
Erwin Dipl.-Ing. Haas
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.)
MAN Truck and Bus Osterreich AG
Original Assignee
Steyr Nutzfahrzeuge AG
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 Steyr Nutzfahrzeuge AG filed Critical Steyr Nutzfahrzeuge AG
Publication of EP0582835A1 publication Critical patent/EP0582835A1/fr
Application granted granted Critical
Publication of EP0582835B1 publication Critical patent/EP0582835B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/062—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/14—Fastening; Joining by using form fitting connection, e.g. with tongue and groove

Definitions

  • the invention relates to a heat exchanger for cooling at least one medium flowing through by a cooling medium, in particular for water and / or charge air and / or oil cooling of an internal combustion engine of a motor vehicle.
  • a water cooler was used regularly, which consists of an upper and a lower water box, each connected to the cooling water circuit of the internal combustion engine, between which pipes with a continuous circular cross-section flow through which cooling water flows.
  • the said pipes are arranged in several pipe levels.
  • Between the tubes there are meandering strips of corrugated sheet metal that are used for heat dissipation to the cooling air flowing through the gaps. Since these outer corrugated sheets are not in direct contact with the medium to be cooled, there is a comparatively poor heat transfer, which in some cases can be compensated for by a relatively high cooling air output.
  • Charge air coolers have generally been built on a principle similar to that of water coolers. On the other hand, a different construction principle was used for oil coolers.
  • the heat exchanger according to the invention allows a very compact production due to its construction principle, and it can also be used universally for cooling a wide variety of media. Another particular advantage is the high efficiency of the heat exchanger, since the partition walls given internally to the profile tubes are in direct contact with the medium to be cooled and the cooling medium, thus ensuring excellent heat transfer. Since the heat exchanger according to the invention is composed only of a large number of extruded profiles which can easily be produced on an industrial scale in corresponding systems, it can also be implemented at a reasonable cost. A special design of the partition walls also ensures that both the cooling medium and the medium to be cooled remain exactly separated when flowing through within a profile tube.
  • the heat exchanger is composed of a large number of polygonal, mutually toothed profile tubes 1 (see FIGS. 1 and 2) or 2, 3 (see FIGS. 3 and 4), the interiors of which are each provided by a large number of axially parallel, heat-dissipating partition walls 4 are divided into a plurality of flow channels 5, 6, 7 for such a separate passage of cooling media and media to be cooled.
  • profile tubes 1 of a single type with the same cross-section are used, with interiors of the same shape through the partitions 4.
  • two cross-section different profile tube types 2, 3, each with the same interior space designed specifically by the partition walls 4, but always the same, are used.
  • each of the profile tubes 1, 2, 3 is divided in the illustrated embodiments by the partitions 4 into three different flow areas, namely a central one with a single flow channel 5, an annular around this given with the flow channels 6 and an annular around this given outer with the flow channels 7.
  • the interior of each profile tube 1, 2, 3 is divided by the partitions 4 so that the different media can flow through the respective flow areas 5, 6, 7 separated from each other.
  • each of the profile tubes 1, 2, 3 including all of its partitions 4 can each be made in one piece by extrusion.
  • the outer wall 8, 9, 10 of each profiled tube 1, 2, 3 and the entirety of the associated internal partition walls 4 can each be realized separately by means of a separate extruded profile.
  • the outer wall 8, 9, 10 of each profile tube 1, 2, 3 can be realized together with some of the associated internal partitions 4 by an extruded profile, while the rest of the internal partitions 4 is realized by at least one further extruded profile.
  • each profile tube 1, 2, 3 and the associated partition walls 4 can, however, also be realized by a plurality of extruded profiles which are inserted coaxially one into the other, which case is shown in the drawing.
  • the outer wall 8 (Fig. 1, 2) or 9, 10 (Fig. 3, 4) of each profile tube 1, 2, 3 is realized by its own extruded profile, while the associated partition walls 4 are realized by two different extruded profiles. This embodiment is discussed in more detail below.
  • the identical profile tubes 1 of the heat exchanger according to FIGS. 1 and 2 have an outer wall 8 which is approximated to a hexagon and made of six different outer wall parts 8/1, 8/2, 8/3, 8/4, 8/5, 8/6 is that the profile tubes 1 are all in the same relative position, that is, not rotated relative to one another about their longitudinal axis, and can be assembled and when they are joined together, their profiled outer wall parts - as can be seen in FIG. 1 - interlockingly interlocked with one another to the system come.
  • the one profile tube type 3 has an outer wall 10 which is approximated to an octagon. Specifically, it consists of four identical, flat, crosswise opposite outer wall parts 10/1, 10/2, 10/3, 10/4 and four, each arranged between two of the aforementioned outer wall parts, and thus also crosswise diametrically opposite same longitudinal grooves 10 / 5, 10/6, 10/7, 10/8 with flat groove base.
  • the other profile tube type 2 however, has an outer wall 9 which is approximated to a square.
  • each other diametrically opposed outer wall parts 9/1, 9/2 which are essentially flat in parallel, but in the middle of their longitudinal extent a projecting, form-fitting into a longitudinal groove 10/5, 10/6, 10/7, 10 / 8 of the other profile tube type 10 have a matching longitudinal web 9/11, 9/21.
  • the other two, mirror images of each other diametrically opposed outer wall parts 9/3, 9/4 are formed by a projecting longitudinal web 9/31, 9/41 having longitudinal constrictions having such a shape that in each of them when joining the profile tubes 9, 10 a profile tube 10 with any two of it flat side surfaces and the groove in between fits exactly.
  • a projecting longitudinal web 9/31, 9/41 having longitudinal constrictions having such a shape that in each of them when joining the profile tubes 9, 10 a profile tube 10 with any two of it flat side surfaces and the groove in between fits exactly.
  • the profile tubes 1, 2, 3 are not each made in one piece with their internal partition walls by appropriate extruded profiles, it is advisable to ensure an exact separation between the media flows to be passed through within a profile tube 1, 2, 3 or to realize several of the partitions 4 by an unprofiled or profiled tube.
  • the flow channel 5 is delimited by a partition 4/1, which are provided by a profiled tube, on which it integrally integrates with it, several other partition walls 4 directed radially towards the outer wall 8 of the profile tube 1. In this way, a defined separation between the central throughflow channel 5 and the central throughflow region containing the flow channels 6 is ensured.
  • a further partition 4/2 is formed by a profiled tube which is integrally united with several other partitions 4 directed radially towards the outer wall 8 of the profile tube 1.
  • the partitions 4 given radially on the inner tubular partition 4/1 extend to the inside of the outer part annular partition 4/2, two adjacent ones of said partition walls 4 together with the two tubular partition walls 4/1, 4/2 delimiting a flow channel 6.
  • the outgoing on the outer tubular partition 4/2 partitions 4 extend to the inside of the outer wall 8 of the profile tube 1, two of said partition walls together with the outer tubular partition 4/2 and the outer wall 8 of the profile tube 1 each having a flow channel 7 limit.
  • both tubular partitions 4/1, 4/2 can (as shown) radially outwards in the direction of the center of the profile tube 1, axially parallel and in the middle in a flow channel 6 or in the flow channel 5 projecting longitudinal webs 11 are formed, which for Serve to increase the heat transfer.
  • the arranged on the outer tubular partition 4/2 partitions 4 have a different length, so that this extruded profile can only be inserted into the profile tube 1 in a single possible position and thus precisely in terms of position.
  • the outer tubular partition 4/2 preferably has a rosette shape with eight wave crests and wave troughs which extend approximately sinusoidally along a pitch circle.
  • the partition walls 4 arranged on the preferably also rosette-shaped inner partition 4/1 all have the same length, so that this extruded profile can be inserted into the outer tubular partition 4/2 in eight different angular positions (each rotated by 45 °), the respective one Partition 4 extends into the interior of a wave crest.
  • the one profile tube 3 according to FIGS. 3 and 4 and its internal partitions 4,4 / 1, 4/2 are constructed.
  • real dividing walls 4 are arranged on the inside of the outer tubular dividing wall 4/2 radially to the center of the profiled tube 3, which extend to the outer surface of the inner tubular dividing wall 4/1.
  • a flow channel is formed in each case by a partition 4 projecting on the inside of the outer tubular partition 4/2 and a partition 4 projecting on the outside by the inner tubular partition 4/1 together with the inner and outer tubular partition 4/1, 4/2 6 limited.
  • the inner tubular partition 4/1 is designed as an unprofiled flat tube with a smooth outer wall.
  • the flow channels 6 are delimited here in each case by dividing walls 4 protruding on the inside from the outer tubular dividing wall 4/2 and reaching to the outer surface of the inner tubular dividing wall 4/1 together with the two tubular dividing walls 4/1, 4/2.
  • the heat exchanger composed of such internally divided profile tubes 1 or 2, 3 can be used in a variety of ways.
  • the central flow area of the profile pipes 1 or 2, 3 with the flow channels 6 given there by the cooling water of the internal combustion engine and the central (5) and outer flow area of the profile pipes 1 or 2, 3 with the Flow channels 7 flows through the cooling air generated by a cooling fan or an alternative cooling medium.
  • the central flow area 6 of the profile pipes 1 or 2, 3 is from the charge air to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 or 2, 3 from that of one Cooling fan generated cooling air or an alternative cooling medium flows through
  • the central flow area 6 of the profile pipes 1 and 2, 3 is generated by the engine oil to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 and 2, 3 are generated by a cooling fan Cooling air or an alternative cooling medium flows through.
  • the heat exchanger according to the invention advantageously allows the same to be used as a combined water and charge air and / or oil cooler of a supercharged internal combustion engine.
  • the profile tubes 1 or 2, 3 are a coherent heat exchanger area 12 for water cooling and the profile tubes 1 and 2, 3 of another connected heat exchanger area 13 for charge air cooling.
  • 6 schematically shows the use of the heat exchanger according to the invention as a combined water, charge air and oil cooler, the profile tubes 1 and 2, 3 of a first coherent heat exchanger area 14 for water cooling, the profile tubes 1 and 2, 3 of a second coherent Heat exchanger area 15 for charge air cooling and the profile tubes 1 and 2, 3 of a third coherent heat exchanger area 16 are used for oil cooling.
  • FIG. 7 it can be seen that for the supply of the medium to be cooled - water and / or charge air and / or oil - an inflow tank 17 is arranged on the front of the heat exchanger according to the invention and an outflow tank 18 is arranged on the rear of the heat exchanger according to the invention for collecting the cooled medium.
  • FIG. 8 shows an example for the supply of the medium to be cooled from the inflow container 17 and for the supply of the cooling medium into the heat exchanger according to the invention.
  • connecting pieces 19 which are connected at the end to the flow channels 6 and are sealed by sealing means.
  • a feed pipe 20 leads in from the side, which is connected and sealed at the end to the central flow channel 5 of the profile pipe 1 or 2 or 3 in question and serves to supply the cooling medium.
  • the cooling medium can enter from the environment around a connecting piece 19 on the end face.
  • This solution shown for the inlet area can equally be used for the outlet area of the heat exchanger according to the invention for connection to the outflow tank 18 given there.
  • the profile tubes 1, 2, 3 and the internal partitions 4, 4, 1, 4, 2 and heat dissipation webs 11 can be made of a highly thermally conductive metallic material, for example aluminum or an aluminum alloy. However, it is also possible to make the outer walls 8, 9, 10 of the profiled tubes 1, 2, 3 from plastic, the partitions 4,4 / 1,4 / 2 and heat dissipation webs 11 from metal, eg aluminum or an aluminum alloy. It is also conceivable, in order to facilitate assembly, to paint the different extrusions in different colors or to produce them from differently colored materials.
  • the inflow container 17 and outflow container 18 are preferably formed together with the connecting piece 19 and feed pipes 20 by essentially one-piece plastic parts.

Landscapes

  • 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)
EP19930110974 1992-08-11 1993-07-09 Echangeur de chaleur Expired - Lifetime EP0582835B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1614/92 1992-08-11
AT161492A AT401431B (de) 1992-08-11 1992-08-11 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP0582835A1 true EP0582835A1 (fr) 1994-02-16
EP0582835B1 EP0582835B1 (fr) 1997-04-16

Family

ID=3517233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930110974 Expired - Lifetime EP0582835B1 (fr) 1992-08-11 1993-07-09 Echangeur de chaleur

Country Status (3)

Country Link
EP (1) EP0582835B1 (fr)
AT (1) AT401431B (fr)
DE (1) DE59306161D1 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6019168A (en) * 1994-09-02 2000-02-01 Sustainable Engine Systems Limited Heat exchangers
ES2161581A1 (es) * 1998-06-17 2001-12-01 Santaolalla Milla Carlos Dispositivo para la refrigeracion de liquidos.
WO2002001133A1 (fr) * 2000-06-28 2002-01-03 Ultrafilter International Ag Echangeur de chaleur pour installation de sechage a froid
EP1178278A2 (fr) 2000-08-03 2002-02-06 F.W. Brökelmann Aluminiumwerk GmbH & Co.KG Tube d'échange de chaleur avec ailettes intérieures tordues
EP1300636A2 (fr) * 2001-10-06 2003-04-09 Robert Bosch Gmbh Echangeur de chaleur pour chaudière à gaz, spécialement chaudière à condensation
EP1434023A3 (fr) * 2002-12-24 2005-08-03 Kaeser Kompressoren GmbH Sécheur à froid
WO2007125118A1 (fr) * 2006-04-28 2007-11-08 Dayco Ensa, S.L. Echangeur de chaleur en aluminium destine a un systeme 'egr'
EP2146173A1 (fr) * 2008-07-17 2010-01-20 MAHLE International GmbH Échangeur thermique plastique
US20140182828A1 (en) * 2012-02-17 2014-07-03 Obschestvo S Ogranichennoi Otvetstvennostju "Proryvnye Innovatsionnye Tekhnologii" Heat-Exchange Apparatus
JP2015102277A (ja) * 2013-11-25 2015-06-04 協同アルミ株式会社 複穴管
EP3356167A4 (fr) * 2015-06-03 2019-06-19 Sfercoci, Petru Système de climatisation et refroidissement de moteur pour véhicules au moyen de gaz d'échappement
EP3455384A4 (fr) * 2016-05-10 2019-11-13 Momentive Performance Materials Inc. Dispositif à tube en graphite pyrolytique thermique pour la gestion thermique directionnelle
US20220196332A1 (en) * 2020-12-18 2022-06-23 Hamilton Sundstrand Corporation Multi-scale unitary radial heat exchanger core
WO2025020238A1 (fr) * 2023-07-24 2025-01-30 擎波探索(苏州)能源科技有限公司 Dispositif de dissipation de chaleur à ailette en plaques en aluminium de moteur hors-bord électrique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1008331B (de) * 1955-04-06 1957-05-16 Waagner Biro Ag Waermetauscherrohr
DE2222610A1 (de) * 1972-05-09 1973-10-31 Hagedorn Und Bailly Waermeuebertragungsanlage
EP0061779A2 (fr) * 1981-03-31 1982-10-06 Feraton Anstalt Echangeur de chaleur
GB2254687A (en) * 1991-04-10 1992-10-14 Int Radiator Services Ltd Heat exchanger

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2615168A1 (de) * 1976-04-07 1977-10-27 Gartner & Co J Waermeuebertragungseinrichtung mit zumindest einem laengsrippen aufweisenden rohr
US4345644A (en) * 1980-11-03 1982-08-24 Dankowski Detlef B Oil cooler
NL8200058A (nl) * 1982-01-08 1983-08-01 Droogtech Warmtewisselaar, werkwijze voor het vervaardigen daarvan, en van een dergelijke warmtewisselaar voorziene gasdroger.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1008331B (de) * 1955-04-06 1957-05-16 Waagner Biro Ag Waermetauscherrohr
DE2222610A1 (de) * 1972-05-09 1973-10-31 Hagedorn Und Bailly Waermeuebertragungsanlage
EP0061779A2 (fr) * 1981-03-31 1982-10-06 Feraton Anstalt Echangeur de chaleur
GB2254687A (en) * 1991-04-10 1992-10-14 Int Radiator Services Ltd Heat exchanger

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6019168A (en) * 1994-09-02 2000-02-01 Sustainable Engine Systems Limited Heat exchangers
ES2161581A1 (es) * 1998-06-17 2001-12-01 Santaolalla Milla Carlos Dispositivo para la refrigeracion de liquidos.
WO2002001133A1 (fr) * 2000-06-28 2002-01-03 Ultrafilter International Ag Echangeur de chaleur pour installation de sechage a froid
EP1178278A2 (fr) 2000-08-03 2002-02-06 F.W. Brökelmann Aluminiumwerk GmbH & Co.KG Tube d'échange de chaleur avec ailettes intérieures tordues
DE10038624A1 (de) * 2000-08-03 2002-02-21 Broekelmann Aluminium F W Wärmeübertragungsrohr mit gedrallten Innenrippen
DE10038624C2 (de) * 2000-08-03 2002-11-21 Broekelmann Aluminium F W Wärmeübertragungsrohr mit gedrallten Innenrippen
US6533030B2 (en) 2000-08-03 2003-03-18 F.W. Brokelmann Aluminiumwerk Gmbh & Co. Kg Heat transfer pipe with spiral internal ribs
EP1300636A2 (fr) * 2001-10-06 2003-04-09 Robert Bosch Gmbh Echangeur de chaleur pour chaudière à gaz, spécialement chaudière à condensation
EP1300636A3 (fr) * 2001-10-06 2004-04-07 Robert Bosch Gmbh Echangeur de chaleur pour chaudière à gaz, spécialement chaudière à condensation
EP1434023A3 (fr) * 2002-12-24 2005-08-03 Kaeser Kompressoren GmbH Sécheur à froid
US7040100B2 (en) 2002-12-24 2006-05-09 Kaeser Kompressoren Gmbh Low-temperature dryer
WO2007125118A1 (fr) * 2006-04-28 2007-11-08 Dayco Ensa, S.L. Echangeur de chaleur en aluminium destine a un systeme 'egr'
EP2146173A1 (fr) * 2008-07-17 2010-01-20 MAHLE International GmbH Échangeur thermique plastique
US20140182828A1 (en) * 2012-02-17 2014-07-03 Obschestvo S Ogranichennoi Otvetstvennostju "Proryvnye Innovatsionnye Tekhnologii" Heat-Exchange Apparatus
JP2015102277A (ja) * 2013-11-25 2015-06-04 協同アルミ株式会社 複穴管
EP3356167A4 (fr) * 2015-06-03 2019-06-19 Sfercoci, Petru Système de climatisation et refroidissement de moteur pour véhicules au moyen de gaz d'échappement
EP3455384A4 (fr) * 2016-05-10 2019-11-13 Momentive Performance Materials Inc. Dispositif à tube en graphite pyrolytique thermique pour la gestion thermique directionnelle
US11255613B2 (en) 2016-05-10 2022-02-22 Momentive Performance Materials Quartz, Inc. Thermal pyrolytic graphite tube device for directional thermal management
US20220196332A1 (en) * 2020-12-18 2022-06-23 Hamilton Sundstrand Corporation Multi-scale unitary radial heat exchanger core
US11781813B2 (en) * 2020-12-18 2023-10-10 Hamilton Sundstrand Corporation Multi-scale unitary radial heat exchanger core
WO2025020238A1 (fr) * 2023-07-24 2025-01-30 擎波探索(苏州)能源科技有限公司 Dispositif de dissipation de chaleur à ailette en plaques en aluminium de moteur hors-bord électrique

Also Published As

Publication number Publication date
EP0582835B1 (fr) 1997-04-16
DE59306161D1 (de) 1997-05-22
ATA161492A (de) 1996-01-15
AT401431B (de) 1996-09-25

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