EP2655828A1 - Tube aspirant avec refroidisseur d'air de suralimentation intégré - Google Patents

Tube aspirant avec refroidisseur d'air de suralimentation intégré

Info

Publication number
EP2655828A1
EP2655828A1 EP11804557.4A EP11804557A EP2655828A1 EP 2655828 A1 EP2655828 A1 EP 2655828A1 EP 11804557 A EP11804557 A EP 11804557A EP 2655828 A1 EP2655828 A1 EP 2655828A1
Authority
EP
European Patent Office
Prior art keywords
housing
charge air
projection
intercooler
radiator block
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.)
Withdrawn
Application number
EP11804557.4A
Other languages
German (de)
English (en)
Inventor
Andreas Eilemann
Hubert Pomin
Christian Saumweber
Veit Bruggesser
Jürgen Stehlig
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
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG, Mahle International GmbH filed Critical Behr GmbH and Co KG
Publication of EP2655828A1 publication Critical patent/EP2655828A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0456—Air cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—Liquid cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—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
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0138—Auxiliary supports for elements for tubes or tube-assemblies formed by sleeves for finned tubes
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a suction pipe for an internal combustion engine, in particular of a motor vehicle, according to the preamble of claim 1.
  • intercoolers for internal combustion engines as indirect radiators, in which the heat of the charge air flow is removed by means of a cooling fluid flowing through the radiator. It is also known »that such intercoolers can be integrated into a suction pipe of the internal combustion engine. It is customary »to provide the intercooler with a flange plate so that it can be inserted into an opening of a Saugrohrgephinuses transversely to the charge air flow direction and bolted to an edge of the flange plate on the housing or welded.
  • Such intake manifolds with integrated charge air cooling are disclosed, for example, in DE 10 2007 030 464 A1, DE 10 2009 012 024 A1, DE 10 2009 025 282 A1 and DE 10 2009 050 258 B3.
  • the flange member and the bottom member are formed separately from the radiator block of the intercooler and sealed against the radiator block and the intake manifold.
  • the entire charge air cooler is surrounded by the intake manifold and the charge air cooler has side parts having a structuring to form a labyrinth seal against an inner wall of the intake manifold to reduce a leakage current of the charge air between intercooler and intake manifold. Additionally or alternatively, the use of elastomeric seals between the side parts of the intercooler and the inside of the intake manifold is known.
  • the intercooler of DE 10 2009 050 258 B3 has at least one cooling fluid boxes as an integral part, which also forms part of the intake manifold.
  • at least one of the cooling fluid boxes of the intercooler is formed as an integral part of the intake manifold.
  • the intake manifold in particular for an internal combustion engine, in particular of a motor vehicle, has a housing defining a charge air duct and a charge air cooler with a radiator block, which is arranged in the housing in such a way that it can be flowed through by the charge air.
  • the radiator block of the intercooler closes on a side facing the housing with an outer component, preferably a cooling element and is formed in this outer component of the radiator block at least one recess, which extends at least over a part of the length of Kuhierblocks substantially transverse to a charge air flow direction.
  • At least one projection is provided on an inner side of the housing facing the radiator block of the intercooler, which extends at least over a part of the inside of the housing substantially transversely to the charge air flow direction and sealingly engages at least partially in the at least one recess of the radiator block.
  • the object is achieved with a suction pipe for an internal combustion engine » in particular a motor vehicle, with a charge air duct defining housing (10) and a charge air cooler with a radiator block, which is arranged in the housing so that it can be flowed through by the charge air, wherein the radiator block of the charge air cooler terminates on an outer side facing the housing with an outer component; at least one projection is formed on this outer component of the Kuhierblocks which extends at least over a part of the length of the kuhierblocks substantially transverse to a charge air flow direction (L); and at least one recess is provided on an inner side of the housing facing the radiator block of the intercooler, which extends at least over part of the inside of the housing essentially transversely to the charge air flow direction (L) and wherein the projection engages at least partially sealingly in the at least one recess.
  • radiator block of the intercooler concludes with an outer component and the at least one recess is formed in this outer component, in contrast to conventional intake manifolds with integrated intercooler can be dispensed with a side part of the intercooler with attached sealing elements.
  • the weight, the cost of materials and the manufacturing cost of the intercooler and thus reduce the intake manifold formed from suction and intercooler can be reduced.
  • the radiator block of the intercooler terminates with an outer component, preferably in the form of a cooling element, the remaining leakage current of the charge air, which possibly flows despite the sealing construction according to the invention between the radiator block and the inside of the intake manifold on the radiator block, at least through the outer cooling element of the radiator block a little chilled.
  • the leakage current thus experiences a much higher cooling compared to conventional designs of the intake manifold with integrated intercooler.
  • this has the further advantage that, compared with conventional constructions, larger leakage currents of the charge air between the radiator block and the intake manifold housing may be permitted before there is a noticeable increase in the temperature of the charge air flow at the inlet of the internal combustion engine.
  • Charge air in the sense of the invention is understood as meaning the gas supplied to an internal combustion engine.
  • the “charge air” also includes any desired mixtures of air and exhaust gas, provided that Internal combustion engine is equipped with an exhaust gas recirculation system.
  • the intake manifold according to the invention can be combined with both gasoline engines and diesel engines.
  • the intake manifold according to the invention can be used in internal combustion engines with and without turbocharger.
  • the "charge air flow direction” designates the main flow direction of the charge air through the portion of the intake manifold housing in which the charge air cooler is arranged.
  • radiator block in this context refers to the part of the intercooler in which the heat exchange between the charge air and the cooling fluid takes place (eg water, refrigerant, etc.)
  • the essential components of the radiator block are several cooling fluid channels and preferably in addition several between the
  • the cooling fluid ducts are preferably formed and arranged in the manner of a tube or tube stacker or a stacked plate cooler
  • the cooling elements between the tubes are in thermal communication with these tubes and increase the effective heat exchange area of the tube
  • the radiator block is preferably formed substantially cuboid, wherein the main sides are substantially transverse to the charge air flow direction and are flowed through by the charge air, without the invention being limited to this geometry s
  • the radiator block is bounded at its two ends by a Sammeiplatte, which has openings for receiving the cooling fluid channels.
  • the cooling fluid channels then open through these collection plates each into a collector (often referred to as a cooling fluid box or water tank).
  • the collectors are provided with an inlet connecting piece and a drain connecting piece for supplying or discharging the cooling fluid to and from the intercooler.
  • inlet and outlet can be provided either both on the same collector or on different collectors. Accordingly, intercooler with inflow direction (I-shaped flow path), Zweiströmungscardi (U-shaped flow path) or Mehrströmungsraum are possible in the context of the invention.
  • one or both collectors may be integrally formed with the radiator block in the present invention, formed as separate components and connected to the radiator block (eg, welded, soldered or glued) or integrally formed with the intake manifold and sealed against the radiator block.
  • the "outer component" of the radiator block designates a component of the radiator block itself, for example, in contrast to a side part or housing part around the radiator block
  • this outer component is designed as a cooling element of the radiator block or another element with a large heat exchange surface.
  • substantially transverse to the charge air flow direction includes, in particular, a direction perpendicular to the charge air flow direction, but also directions having a main component perpendicular to the charge air flow direction, ie, directions in an angular range of, for example, about ⁇ 30 degrees to the normal to the main flow direction
  • protrusions which intermesh with one another are fundamentally of any desired shape, provided that they are substantially complementary to one another, so that they achieve a sufficient sealing effect by forming a labyrinth
  • the recess is preferably groove-like formed at least partially round or rounded cross-sectional shapes.
  • Recess and projection should each extend at least over part of the radiator block or the inside of the housing transversely to the charge air flow direction. In this context, this means that the recess and the projection each extend over the entire width of the charge air duct transversely to the charge air flow direction or over only a part of this width. Recess and projection preferably extend substantially parallel to the longitudinal direction of the radiator block, but can also extend within the scope of the invention at a predetermined angle to this longitudinal direction of the radiator block.
  • Recess and projection are preferably arranged in the charge air flow direction centrally to the radiator block or symmetrically to the center of the radiator block, without the invention being limited to these embodiments,
  • the "projection" on the inside of the housing is preferably formed integrally with the housing
  • the at least one projection is formed as a separate component and firmly connected to the housing (eg welded, glued and / or jammed)
  • the protrusion may be formed of a material that is sufficiently dimensionally stable for the seal construction, regardless of the material of the draft tube housing.
  • the projection at least partially engages in the recess, it should be understood in this connection that the projection over at least a part of the length of the projection or the Recess engages in the width direction of the charge air channel and / or at least in part of the depth of the recess in the recess.
  • the engagement of the projection is designed such that the overlap between the projection and the recess is also given sufficiently, even if the housing inflates due to pressure and bulges outward. This swelling can reduce the intervention by several millimeters. It is preferred if, even in the inflated state, at least an overlap of 2 to 5 mm would be present.
  • “at least one recess” and “at least one projection” is provided. This includes numbers one of exactly two "three or more recesses or projections. The numbers of the recesses and the projections preferably match. If several, ie at least two recesses and projections are provided, they preferably but not necessarily substantially parallel to each other. If a plurality of recesses and projections are provided, these may all extend over the entire width of the charge air channel or occupy only a part of this width. In the latter case, the recesses and projections are preferably arranged offset in the longitudinal direction of the radiator block of the charge air cooler to each other, so that overall preferably the entire width of the charge air duct is provided with the sealing measure according to the invention. In the case of a plurality of recesses and projections, these are preferably dimensioned essentially equal to one another, but they may also have different depths and / or thicknesses in the context of this invention.
  • a sealing construction is provided on both sides of the radiator block, which faces an inside of the housing.
  • the sealing construction according to the invention is provided only on one side of the radiator block and the other side of the radiator block is sealed in a different manner relative to the inside of the intake manifold.
  • sealing construction according to the invention between intake manifold housing and radiator block does not exclude that further sealing measures are provided.
  • sealing elements such as elastomeric gasket and the like may be additionally disposed between the radiator block and the intake manifold housing.
  • the present invention is preferably applicable to suction pipes, in which the charge air cooler is flowed through by the entire charge air flow at all times.
  • the construction according to the invention can also be used with suction tubes, in which a bypass channel is provided, which is guided past the charge air cooler. Adjusting elements for setting a mass flow ratio between intercooler and bypass channel can be arranged in this case optionally upstream and / or downstream of the Ladeiuftkühlers in the intake manifold.
  • the bypass channel can optionally be separated by means of a dividing wall arranged in the intake manifold, or at least partially formed as a pipe channel separate from the main duct.
  • the housing has an opening for inserting the intercooler in the direction transverse to the Ladeiuft- Flow direction in the housing.
  • the (lateral) insertion of the intercooler into the Saugrohrohrgepuruse is preferably transverse to the charge air flow direction and thus substantially in the longitudinal direction of the intercooler or its radiator block.
  • the opening of the intake manifold housing is formed closable to seal the charge air duct.
  • a flange or the like is preferably provided on the rear collecting plate in the direction of insertion of the intercooler or on the rear in the insertion direction of the charge air cooler, which is bolted or welded to the intake manifold, for example.
  • the flange is formed integrally with the collecting plate or the collector.
  • the housing of the suction tube may also be formed with two openings on opposite sides of the housing, through which the intercooler can be pushed. In this case, both openings are closable as described above.
  • This embodiment is particularly advantageous when the one collector of the intercooler is provided with the inlet connection piece and the other collector of the intercooler is provided with the outlet connection piece.
  • the at least one recess in the outer component of the radiator block during a mounting operation of the intercooler in the housing of the suction tube by the at least one projection on the inside of the housing educated.
  • the projection on the inside of the housing presses the outer component (plastic deformation) and thus forms the recess.
  • a seal construction is achieved with very small gaps between the radiator block and the intake manifold housing. Since the recess is formed automatically during the assembly process, eliminates a corresponding manufacturing step prior to assembly, whereby the manufacturing cost of the intercooler can be reduced.
  • This embodiment can be applied to both a laterally insertable and a usable intercooler.
  • the at least one recess in the outer member of the radiator block is preformed and brought during a mounting operation of the charge air cooler in the housing of the suction tube with the at least one projection on the inside of the housing. Due to the preformed recess in the outer component of the assembly process of the intercooler is easier to carry out, in particular with less effort. This embodiment can also be applied to both a retractable and a usable intercooler.
  • the corrugated ribs are designed weakened in the region of the wave crest, in particular pre-perforated.
  • the corrugated fins may be cut by a cut, e.g. with a knife, be interrupted in the recess.
  • the intercooler on its front side in the installation direction a collecting plate, wherein the outer component of the radiator block projects beyond this collecting plate to a supernatant.
  • This embodiment is particularly advantageous in the case of a charge air cooler which can be inserted laterally into the intake manifold housing. In this way it can be prevented that the front collecting plate interferes with the projection on the inside of the housing during the assembly process, which is intended to engage in the recess in the outer component or to form this recess when inserting the intercooler into the intake manifold.
  • the projection of the outer member of the radiator block is preferably at least about 20%, more preferably at least about 30%, even more preferably at least about 40% of a height of the outer member in the direction transverse to the charging air flow direction.
  • the projection of the outer member of the radiator block is preferably at most about 80%, at most about 70%, even more preferably at most about 60% of the height of the outer member in the direction transverse to the charging air flow direction.
  • the intercooler on its front side in the installation direction a collecting plate and this front collecting plate of the intercooler is provided with at least one guide element, in which the at least one projection on the inside of the housing during the assembly process of the intercooler in the Housing can intervene.
  • the guide element is preferably formed substantially complementary to the projection on the inside of the intake manifold and dimensioned slightly larger than this. This embodiment is particularly advantageous in the case of a charge air cooler which can be inserted laterally into the housing.
  • the guide member supports the correct insertion direction of the charge air cooler in the intake manifold and the correct positioning of the preformed or yet to be formed training relative to the projection on the inside of the housing.
  • the number of guide elements preferably corresponds to the number of projections, but can also be selected smaller or larger.
  • the projection on the inside of the housing in the installation direction of the intercooler on an increasing depth perpendicular to the charge air flow direction is particularly advantageous in the case of an intercooler which can be inserted laterally into the housing, since it facilitates the shaping of the recess in the outer component.
  • the term "increasing depth” is to be understood to mean all embodiments in which the depth of the projection on the side of the insertion opening is smaller than at the other end preferably continuous or stepwise.
  • an average slope of the depth of the protrusion is preferably at least about 0.1 °, more preferably at least about 0.25 °, even more preferably at least about 0.35 °.
  • the average slope of the depth of the protrusion is preferably at most about 5 °, more preferably at most about 2 °, even more preferably at most about 1 °.
  • a ratio of a height of the outer member of the radiator block transverse to the charge air flow direction to a depth of the protrusion on the inside of the housing is at least about 0.3, more preferably at least about 0.5.
  • the ratio of the height of the outer member of the radiator block to the depth of the protrusion on the inside of the housing is preferably at most about 3: 1, more preferably at most about 2: 1.
  • the ratios given here refer to the mean depth of these projections.
  • FIG. 1 Therein, partly schematic view of a perspective view of a charge air cooler according to a first embodiment of the invention; a fragmentary perspective view, partly in section, of a connection between the intercooler and the intake manifold according to the first embodiment; a partial perspective view of an almost voltstieri inserted into the intake manifold intercooler according to a second embodiment of the invention; a partial perspective view of the fully inserted into the intake manifold intercooler of Figure 3; a perspective cross-sectional view of the inserted into the intake manifold intercooler of Figure 3;
  • FIG. 6 shows a perspective longitudinal sectional view of the charge air cooler of FIG. 3 inserted into the intake manifold housing along line A-A in FIG. 5;
  • FIG. 7 shows a perspective longitudinal sectional view of the charge air scoop of FIG. 3 inserted into the intake manifold housing along line B - B in FIG. 5;
  • Fig. 8 is a perspective view of a charge air cooler according to a third
  • Embodiment of the invention 9 is a sectional view with a projection on the housing and recess on the radiator.
  • 10 is a sectional view with a projection on the housing and recess on the radiator.
  • Fig. 1 1 is a sectional view with a projection on the housing and recess on the radiator;
  • FIG. 12 shows a view of the radiator block with tube bottom
  • FIG. Fig. 13 is a view of the radiator block with tube bottom
  • Fig. 14 a tube sheet
  • FIG. 15 is a detail of FIG. 14; FIG.
  • Fig. 16 is a view of a heat exchanger
  • Fig. 17 is a view of a section of the collecting tank with tube bottom and corrugated fin.
  • FIGS 1 to 7 show intercooler according to a first and a second embodiment, which are integrated in a suction pipe of an internal combustion engine of a motor vehicle.
  • the two embodiments are described below together, since they differ only slightly.
  • the housing 10 of the intake manifold defines a charge air passage through which charge air in a charge air flow direction L is supplied to the engine.
  • this charge air duct of the intercooler 12 is integrated, which in this embodiment can be inserted through a corresponding opening 14 in the housing 10 laterally in this housing 10 in a mounting direction M substantially perpendicular to the charge air flow direction L of the charge air through the charge air duct.
  • the charge air duct or the intake manifold housing 10 Downstream of the intercooler 12, the charge air duct or the intake manifold housing 10 typically branches into a plurality of intake passages (not shown) which are flanged to a cylinder head of the internal combustion engine.
  • the intercooler 12 has a radiator block 16 which is formed substantially cuboid, wherein the longitudinal direction of the radiator block 16 is aligned substantially parallel to the installation direction M of the charge air cooler 11 and thus perpendicular to the charging air flow direction L through the housing 10 of the suction tube, so that the radiator block 16th The charge air can flow through the radiator block 16.
  • the radiator block 16 of the intercooler 12 is constructed substantially from a plurality of tubes 18 arranged one above another and cooling fins 20 arranged therebetween for enlarging the heat exchange surface. As can be seen in FIG. 5, in this exemplary embodiment, moreover, two stacks of tubes 18 in the charge air flow direction L are arranged one behind the other in order to increase the cooling capacity.
  • the radiator block 16 closes on both sides, which face an inside of the housing 10 perpendicular to the charge air flow direction L and to the longitudinal direction of the intercooler 12, in each case with an outer component in the form of an outer cooling rib 22.
  • the cooling fins 20, 22 extend in the charge air flow direction L over both stacks of the tubes 18.
  • the radiator block 16 of the intercooler 12 is limited by a collecting plate 24, 26.
  • the two collection plates 24, 26 are provided with openings, in which the tubes 18 of the radiator block 16 are inserted.
  • the components 18-26 of the radiator block 16 are preferably brazed or welded together.
  • the rear collecting plate 24 simultaneously forms a fastening flange, which projects beyond the opening 14 of the housing 10, so that the intercooler 12 is screwed or riveted to the housing 10 with this collecting plate 24 (cf. FIGS. 1 and 2) or crimped or clipped (cf. FIGS 7) can be (alternatively welded or glued).
  • a sealing element 42 for example in the form of an O-ring seal, is preferably also arranged.
  • the rear collecting plate 24 is connected to a first header 28 and the front header plate 26 is connected to a second header 30.
  • the collectors 28, 30 are each formed by a kind of cover which is connected to the respective collecting plate 24, 26, in particular welded, soldered or glued.
  • the first collector 28 is provided with an inlet connection pipe 32 and a drain connection pipe 34 (compare FIGS. 3 and 6).
  • the two nozzles 32, 34 are integrally formed with the first collector 28 (eg molded) or welded or soldered to this.
  • the first header 28 is, for example, one between the two stacks arranged partition plate divided.
  • the second header 30 is integrally formed with or fixedly connected to the radiator block 16; Alternatively, the second collector 30 may also be formed as part of the intake manifold housing 10.
  • a cooling fluid (e.g., water) is supplied to the first header 28 through the inlet spigot 32, which is split from the header to, for example, the upstream tubes 18 of the radiator block 16 in the charge air flow direction L. After flowing through the tubes 18 and the heat exchange with the charge air, the cooling fluid passes into the second collector 30 and is redirected from there into the ström exhaustive tubes 18 of the radiator block 16. After flowing through the downstream tubes 18 and the renewed heat exchange with the charge air, the cooling fluid passes back into the first collector 28 and is discharged therefrom via the drain port 34.
  • a cooling fluid e.g., water
  • two substantially strip- or rib-like projections 36 are formed on the inner sides of the intake manifold housing 10 facing the outer cooling ribs 22 of the radiator block 16.
  • the projections 36 are integrally formed with the housing 10 (see Figures 2 and 5), but they may also be formed as separate components and connected to the housing 10.
  • the projections 36 are substantially perpendicular to the charge air flow direction L and perpendicular to the longitudinal direction M of the radiator block 16 in the interior of the charge air duct. In addition, the projections 36 are substantially parallel to each other and substantially parallel to the longitudinal direction M of the radiator block. In addition, the two projections 36 on one side of the radiator block 16 in Charge air flow direction L arranged substantially symmetrically to the center of the radiator block 16.
  • the outer cooling fins 22 of the radiator block 16 are plastically deformed by the inwardly projecting projections 36 during insertion of the charge air cooler 12 through the opening 14 in the housing 10 of the suction tube.
  • 16 groove-like recesses 38 are formed in the outer cooling fins 22 of the radiator block, which are formed substantially complementary to the projections.
  • the recesses 38 likewise run essentially parallel to one another and essentially parallel to the installation direction or longitudinal direction M of the intercooler 10.
  • the leakage current of the charge air may be greater than with conventional charge air coolers with side parts without it to a noticeable increase in the temperature of the charge air comes
  • the omission of side parts of the intercooler 12 also advantageously reduces the weight and the manufacturing cost of the intercooler 12.
  • the projections 36 each have a depth Z perpendicular to the charge air flow direction L and the outer cooling fins 22 each have a height H perpendicular to the charge air flow direction L.
  • the front header 26 and the second header 30 are dimensioned such that the outer fins 22 of the radiator block 16 surround them protrude beyond a supernatant U (see Figure 1).
  • a ratio H / Z in this embodiment is in the range of about 0.5 to about 2.
  • the projection U of the outer cooling fins 22 in this embodiment is in the range of 30-70%, typically 40-60% of the height H of the fins 22nd
  • the projections 36 are preferably formed in the installation direction M of the intercooler 12 with an increasing depth Z.
  • FIG. 8 shows a charge air cooler 12 according to a further exemplary embodiment.
  • the same components are given the same reference numbers as in Figures 1 to 7 of the first and second embodiments.
  • the intercooler 12 of this embodiment differs from the intercooler of the first embodiment described above in that the front header plate 26 is provided with guide members 40 in the form of notches. When inserting the intercooler 12 into the housing 10 of the suction tube, the projections 36 engage the housing in these guide elements 40 to guide the intercooler 12.
  • the guide elements 40 With the help of the guide elements 40, the correct insertion of the intercooler 12 is simplified in the intake manifold 10.
  • the supernatant U of the outer cooling fins 22 via the front collecting plate 26 can be less or not formed compared to the above embodiments.
  • the invention has been explained with reference to embodiments in which the intercooler 12 is inserted through a lateral opening 14 in the intake manifold 10 and the recesses 38 for the labyrinth seals between the radiator block 16 of the charge air cooler 12 and the intake manifold 10 during the assembly process directly through the projections 36 at the housing 10 are formed.
  • the recesses 38 are also embodiments in which the recesses 38 are preformed in the outer components 22 of the radiator block 16, for example, groove-like and the projections 36 on the housing 10 then simply engage during mounting in these recesses 38.
  • additional elastomeric seals may be inserted between the recesses and the protrusions to improve the sealing effect.
  • the suction tubular housing 10 is formed divided in the region of the intercooler 12, so that the intercooler 12 can be used between the two housing parts.
  • the components of the intercooler 12 according to the invention are preferably all made of a light metal such as aluminum and soldered together. Such a solution is particularly safe and permanently cool fluid-tight, cool efficient and inexpensive to produce.
  • the intake manifold 10 is made for example of a plastic or a metal (preferably at high charging pressures or temperatures)
  • FIG. 9 shows an alternative embodiment of the invention.
  • the charge air cooler 102 integrated in the intake manifold 101 in this case has an arrangement 100 according to the invention.
  • the heat exchanger such as intercooler 102, formed such that the radiator block 103 is formed at its outer, the housing 104 of the suction pipe 101 opposite end not with a cooling element, such as a corrugated fin, but with at least two juxtaposed flat tubes 105 and the projection 106 of the housing 104 of the suction pipe 101 between the tubes 105 engages.
  • the projection 106 engages in a cooling element 107, which is arranged below the tubes 105.
  • the projection 106 bends the cooling element 107 at least locally and digs when inserted into the housing formally in the cooling element. As a result, a channel 108 is produced in the cooling element, which receives the projection 106.
  • the combination protrusion channel 106, 108 forms a kind of labyrinth seal for sealing a flow around the charge air cooler by the charge air.
  • the projection 106 is divided approximately in the middle and has a groove 109. This causes the projection 108 are formed with its two tongues 1 10, 1 1 1 in resilient, and are acted upon by the insertion into the housing and the generation of the channel 108 to each other so that they then under bias outside to the wall areas the gutter rest and effect an improved seal.
  • the projection 106 thus engages between the tubes of the intercooler, advantageously without touching them, and immersed in the cooling element.
  • the projection can be made in two parts and rest elastically on the recess or groove. This improved sealing feature is not limited to the embodiment of Figure 9, but may be applied to the other embodiments of this application.
  • FIG. 10 shows a further alternative embodiment of the invention.
  • the outer parts 151 of the heat exchanger block 150 are not formed as a cooling element, such as a corrugated fin, but are a body that may be solid or formed as a foam body.
  • the foam body is advantageously designed as a metal foam body, in particular aluminum foam body.
  • the outer part can also be a geometrically shaped part, which for example has a preformed channel 152 for receiving the projection 153.
  • FIG. 11 shows a further alternative of the invention, according to which the projection or also the corresponding recess is designed such that the projection 180 has an element 181 which effects an undercut.
  • the element is advantageously formed so that the projection 180 is T- or L-shaped.
  • the corresponding one Recess has a shape that it can accommodate the projection thus formed.
  • the outer component of the heat exchanger is not the cooling element, such as corrugated rib, but is a solid material or a foamed material, such as an aluminum foam
  • FIG. 12 shows a section of a charge air cooler 200 according to the present invention, wherein only the tube plate 201 with the tubes 203 pushed into the tube openings 202 can be seen.
  • the tube plate 201 is widened in the radial direction relative to the body 204 of the charge air cooler so that a projection in the housing of the charge air cooler produces a groove or recess in the housing of the charge air cooler upon insertion of the charge air cooler, which together with the projection produces a type of labyrinth seal.
  • the recess is advantageously produced in the region of a gap between two rows of tubes.
  • FIGS. 13 to 17 show a further embodiment in which the tubesheet has a recess in the region between the rows of tubes, so that the projection of the housing of the suction tube can be accommodated favorably in the outer surface of the charge air cooler.
  • FIG. 13 shows the view of the body 220 of the cooler without collecting box
  • the tube bottom 221 has in the area between the tubes 222 has a recess at the upper edge, which is advantageously designed at the lower edge so.
  • FIG. 14 shows the tubesheet 221 with the recess 223 at the upper and at the lower edge, which are arranged approximately centrally of the longitudinal sides.
  • FIG. 15 shows a section in which the projection is shown in greater detail. It is approximately parallelogram-like executed with a depth of about 1, 5 mm and a bottom width of about 2 mm.
  • FIG. 16 shows the heat exchanger 230 with attachment flange 231, tube-rib block 232 and end-side tube plate 233 with collection box 234.
  • the upper and lower layers 235 and 236 are preferably designed as corrugated ribs or similarly soft elements.
  • FIG. 17 shows a detail of the front collecting box 234 with tube bottom 233 and corrugated fin 235. It can be seen that both the collecting box and the tubesheet have a recess into which a projection of the housing can engage. In this case, the corrugated rib is then deformed in this area and forms together with the projection, not shown, a labyrinth seal.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compressor (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

L'invention concerne un tube aspirant pour un moteur à combustion interne d'un véhicule automobile, qui présente un boîtier (10) définissant un canal d'air de suralimentation et un refroidisseur d'air de suralimentation (12) avec un bloc de radiateur (16) qui est disposé dans le boîtier (10) de telle sorte qu'il puisse être parcouru par l'air de suralimentation. Le bloc de radiateur (16) du refroidisseur d'air de suralimentation (12) se termine, d'un côté tourné vers le boîtier (10), par un élément structurel extérieur, de préférence une ailette de refroidissement (22), et dans cet élément structurel extérieur (22) du bloc de radiateur (16) est réalisé au moins un évidement (38) qui s'étend au moins sur une partie de la longueur du bloc de radiateur (16) essentiellement transversalement à la direction d'écoulement de l'air de suralimentation (L). En outre, d'un côté interne du boîtier (10) tourné vers le bloc de radiateur (16) du refroidisseur d'air de suralimentation (12) est disposée au moins une saillie (36) qui s'étend au moins sur une partie du côté interne du boîtier (10) essentiellement transversalement à la direction d'écoulement de l'air de suralimentation (L) et qui vient en prise de manière étanche au moins en partie dans l'au moins un évidement (38) du bloc de radiateur (16).
EP11804557.4A 2010-12-20 2011-12-20 Tube aspirant avec refroidisseur d'air de suralimentation intégré Withdrawn EP2655828A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063602A DE102010063602A1 (de) 2010-12-20 2010-12-20 Saugrohr mit integriertem Ladeluftkühler
PCT/EP2011/073488 WO2012085008A1 (fr) 2010-12-20 2011-12-20 Tube aspirant avec refroidisseur d'air de suralimentation intégré

Publications (1)

Publication Number Publication Date
EP2655828A1 true EP2655828A1 (fr) 2013-10-30

Family

ID=45443107

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11804557.4A Withdrawn EP2655828A1 (fr) 2010-12-20 2011-12-20 Tube aspirant avec refroidisseur d'air de suralimentation intégré

Country Status (8)

Country Link
US (1) US9175596B2 (fr)
EP (1) EP2655828A1 (fr)
JP (1) JP6084164B2 (fr)
KR (1) KR101857465B1 (fr)
CN (1) CN103314195B (fr)
BR (1) BR112013015423A2 (fr)
DE (2) DE102010063602A1 (fr)
WO (1) WO2012085008A1 (fr)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2975768B1 (fr) * 2011-05-26 2016-01-29 Valeo Systemes Thermiques Echangeur thermique, notamment pour vehicule automobile, et dispositif d'admission d'air correspondant
FR2975765B1 (fr) 2011-05-26 2016-01-29 Valeo Systemes Thermiques Echangeur thermique, notamment pour vehicule automobile, et dispositif d'admission d'air correspondant
DE102012206106A1 (de) * 2012-04-13 2013-10-17 Behr Gmbh & Co. Kg Anordnung eines Ladeluftkühlers in einem Ansaugrohr
DE102012212110A1 (de) * 2012-07-11 2014-01-16 Mahle International Gmbh Frischluftversorgungseinrichtung und Herstellungsverfahren
CN103075278B (zh) * 2012-10-31 2015-12-09 中国北方发动机研究所(天津) 一种集成中冷器的进气管
US9709342B2 (en) 2013-02-13 2017-07-18 Modine Manufacturing Company Heat exchanger arrangement in a housing
DE102013002523A1 (de) 2013-02-13 2014-08-14 Modine Manufacturing Company Wärmetauscheranordnung in einem Gehäuse
DE102013002478A1 (de) 2013-02-13 2014-08-14 Modine Manufacturing Company Wärmetauscheranordnung in einem Gehäuse
DE102013202448A1 (de) * 2013-02-14 2014-08-14 Mahle International Gmbh Frischluftanlage
DE102013205316A1 (de) * 2013-03-26 2014-10-02 Behr Gmbh & Co. Kg Frischluftanlage
DE102014202466A1 (de) * 2014-02-11 2015-08-13 MAHLE Behr GmbH & Co. KG Ladeluftkühler für eine Frischluftanlage einer Brennkraftmaschine
DE102014226865A1 (de) 2014-12-22 2016-06-23 Mahle International Gmbh Ladeluftkühler-Anordnung
DE102015203858A1 (de) * 2015-03-04 2016-09-08 Mahle International Gmbh Wärmeübertrager und Verfahren zur Herstellung eines Wärmeübertragers
US20160297282A1 (en) * 2015-04-10 2016-10-13 Denso International America, Inc. Hvac heat exchanger air seal
DE102015210962A1 (de) * 2015-06-15 2016-12-15 Mahle International Gmbh Wärmeübertrager
DE102015010885A1 (de) * 2015-08-20 2017-02-23 Modine Manufacturing Company Wärmetauscher und Herstellungsverfahren
DE102016200456A1 (de) 2016-01-15 2017-07-20 Mahle International Gmbh Abgaswärmeübertrager
CN108603735B (zh) * 2016-02-01 2020-08-04 达纳加拿大公司 塑料外壳内的结构整体的热交换器
US11137212B2 (en) * 2016-06-23 2021-10-05 Hanon Systems Bypass seal for plate heater matrix
US10697354B2 (en) * 2016-08-25 2020-06-30 Hanon Systems Heat exchanger
US9890692B1 (en) 2017-06-22 2018-02-13 Brett Turnage Modular intercooler system
EP3564613A1 (fr) * 2018-05-03 2019-11-06 Mann+Hummel GmbH Échangeur de chaleur, système d'admission d'air avec échangeur de chaleur et procédé de montage d'un échangeur de chaleur
DE102019218509A1 (de) * 2019-11-28 2021-06-02 Volkswagen Aktiengesellschaft Brennkraftmaschine mit einem Ladeluftkühler sowie mit einer Kontrollvorrichtung zur Steuerung oder Regelung eines elektrisch betriebenen Elements eines Fahrzeuges
CN110940208A (zh) * 2019-12-10 2020-03-31 江西莱利电气有限公司 冷却器
CN111456841B (zh) * 2020-05-06 2023-09-01 江苏赛麟汽车科技有限公司 一种集成进气水冷式中冷器
US11639792B2 (en) * 2020-06-24 2023-05-02 Rheem Manufacturing Company Single-piece refractory for a water heating assembly
CN113028866B (zh) * 2021-04-13 2022-10-21 浙江银轮机械股份有限公司 中冷器芯体、气室组件及中冷器
KR102532045B1 (ko) * 2022-10-28 2023-05-12 주식회사 스마트파워 바이오가스 발전기의 효율을 향상시킨 발전기용 인터쿨러

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050061026A1 (en) * 2003-09-23 2005-03-24 Choi Jae Sik Evaporator core with a separable tube and a fin for a vehicle
EP2470761A1 (fr) * 2009-08-26 2012-07-04 Behr GmbH & Co. KG Refroidisseur de gaz pour moteur à combustion interne

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3107010C2 (de) * 1981-02-25 1985-02-28 Dieter Christian Steinegg-Appenzell Steeb Metallkühler zum Kühlen eines unter hohem Druck durchströmenden Fluids durch Luft
JP2667012B2 (ja) * 1989-08-11 1997-10-22 ヤンマーディーゼル株式会社 エンジンの空気冷却器
DE4307504C1 (de) * 1993-03-10 1994-09-22 Mtu Friedrichshafen Gmbh Wärmetauscher, insbesondere Ladeluftkühler einer Brennkraftmaschine
DE10214467A1 (de) * 2002-03-30 2003-10-09 Modine Mfg Co Abgaswärmetauscher für Kraftfahrzeuge
DE10354382A1 (de) * 2003-11-20 2005-06-16 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Ladeluftkühler für Kraftfahrzeuge
DE102005049310A1 (de) * 2005-10-12 2007-04-19 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für Kraftfahrzeuge
DE102005053924B4 (de) * 2005-11-11 2016-03-31 Modine Manufacturing Co. Ladeluftkühler in Plattenbauweise
DE102006005106A1 (de) * 2006-02-04 2007-08-09 Modine Manufacturing Co., Racine Wärmetauscher mit einer Anschlussplatte, insbesondere Ladeluftkühler
DE102006019024A1 (de) * 2006-04-25 2007-10-31 Modine Manufacturing Co., Racine Wärmetauscher für Kraftfahrzeuge
DE102006040851A1 (de) * 2006-08-31 2008-03-06 Mahle International Gmbh Wärmeübertragereinrichtung
DE102007030464A1 (de) 2007-06-29 2009-01-08 Volkswagen Ag Saugrohr für eine Brennkraftmaschine
DE602007008714D1 (de) * 2007-07-11 2010-10-07 Joao De Deus & Filhos S A Wärmetauscheranordnung
US8225852B2 (en) 2008-04-30 2012-07-24 Dana Canada Corporation Heat exchanger using air and liquid as coolants
DE102009012024A1 (de) 2009-03-10 2010-09-16 Behr Gmbh & Co. Kg Ladeluftkühler zur Anordnung in einem Saugrohr
DE102009025282A1 (de) 2009-06-15 2010-12-16 Behr Gmbh & Co. Kg Saugrohr mit integriertem Ladeluftkühler
DE102009050258B3 (de) 2009-10-21 2010-11-18 Mann + Hummel Gmbh Saugrohr einer Brennkraftmaschine und Kühlfluidladeluftkühler

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050061026A1 (en) * 2003-09-23 2005-03-24 Choi Jae Sik Evaporator core with a separable tube and a fin for a vehicle
EP2470761A1 (fr) * 2009-08-26 2012-07-04 Behr GmbH & Co. KG Refroidisseur de gaz pour moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2012085008A1 *

Also Published As

Publication number Publication date
CN103314195B (zh) 2016-02-24
DE112011104459A5 (de) 2013-12-05
WO2012085008A1 (fr) 2012-06-28
JP6084164B2 (ja) 2017-02-22
DE102010063602A8 (de) 2013-05-08
US9175596B2 (en) 2015-11-03
CN103314195A (zh) 2013-09-18
DE102010063602A1 (de) 2012-06-21
JP2014503738A (ja) 2014-02-13
KR20140004688A (ko) 2014-01-13
KR101857465B1 (ko) 2018-05-14
BR112013015423A2 (pt) 2016-09-20
US20140000569A1 (en) 2014-01-02

Similar Documents

Publication Publication Date Title
WO2012085008A1 (fr) Tube aspirant avec refroidisseur d'air de suralimentation intégré
EP1544564B1 (fr) Echangeur de chaleur à tubes plats et tube plat pour échangeur de chaleur
EP2470761B1 (fr) Refroidisseur de gaz pour moteur à combustion interne
EP2031338B1 (fr) Echangeur thermique
DE102013006956B4 (de) Luftführendes Bauteil mit einem Ladeluftkühler
EP2906893B1 (fr) Échangeur thermique
EP1279805B1 (fr) Refroidisseur de l'air de charge aéroréfrigérée
EP1435503B1 (fr) Echangeur de chaleur et ensemble échangeur de chaleur pour véhicules automobiles
EP1769210B1 (fr) Echangeur thermique, en particulier refroidisseur d'air de suralimentation
EP1504230B2 (fr) Echangeur thermique, notamment refroidisseur d'air de suralimentation
EP3169964B1 (fr) Échangeur de chaleur
EP0864838B1 (fr) Echangeur de chaleur pour véhicule automobile
WO2008125309A2 (fr) Échangeur de chaleur
EP2443330A1 (fr) Collecteur d'admission à refroidisseur d'air de suralimentation intégré
EP1800078A1 (fr) Echangeur de chaleur de gaz d'echappement refroidi par air, en particulier refroidisseur de gaz d'echappement pour vehicules automobiles
EP1701125A2 (fr) Echangeur de chaleur à tubes plats et tube plat pour échangeur de chaleur
DE112017005178T5 (de) Wärmetauscher mit Umgehungsdichtung mit Rückhalteklammer
WO2010015433A1 (fr) Unité de transfert de chaleur pour un moteur à combustion interne
DE102007043992A1 (de) Ladeluftmodul für eine Verbrennungskraftmaschine
DE102015110974B4 (de) Abgaswärmeübertrager mit mehreren Wärmeübertragerkanälen
EP1972879B1 (fr) Échangeur de chaleur, en particulier radiateur pour liquide de refroidissement dans un véhicule automobile
EP1956212A1 (fr) Agencement d'un refroidisseur d'air de suralimentation dans un système d'aspiration d'un moteur à combustion interne
EP1706698A1 (fr) Echangeur de chaleur
DE102007025878A1 (de) Wärmeübertrager, insbesondere Ladeluftkühler
DE102008006153B3 (de) Luftansaugkanalsystem mit einem integrierten Ladeluftkühler

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130722

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE INTERNATIONAL GMBH

Owner name: MAHLE BEHR GMBH & CO. KG

17Q First examination report despatched

Effective date: 20170329

RIC1 Information provided on ipc code assigned before grant

Ipc: F28D 7/16 20060101ALI20181023BHEP

Ipc: F28D 21/00 20060101ALI20181023BHEP

Ipc: F28F 9/007 20060101ALI20181023BHEP

Ipc: F02B 29/04 20060101ALI20181023BHEP

Ipc: F28F 9/013 20060101AFI20181023BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20181206

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20190417