US20110286837A1 - Exhaust-gas turbocharger - Google Patents

Exhaust-gas turbocharger Download PDF

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Publication number
US20110286837A1
US20110286837A1 US13/110,421 US201113110421A US2011286837A1 US 20110286837 A1 US20110286837 A1 US 20110286837A1 US 201113110421 A US201113110421 A US 201113110421A US 2011286837 A1 US2011286837 A1 US 2011286837A1
Authority
US
United States
Prior art keywords
collar
exhaust
gas turbocharger
edge
inner housing
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.)
Abandoned
Application number
US13/110,421
Other languages
English (en)
Inventor
Christian Smatloch
Elmar Grussmann
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.)
Benteler Automobiltechnik GmbH
Original Assignee
Benteler Automobiltechnik 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 Benteler Automobiltechnik GmbH filed Critical Benteler Automobiltechnik GmbH
Assigned to BENTELER AUTOMOBILTECHNIK GMBH reassignment BENTELER AUTOMOBILTECHNIK GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GRUSSMANN, ELMAR, SMATLOCH, CHRISTIAN
Publication of US20110286837A1 publication Critical patent/US20110286837A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/243—Flange connections; Bolting arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the present invention relates to an exhaust-gas turbocharger.
  • turbocharger Internal combustion engines in particular for motor vehicles are increasingly charged by fluid flow machines to further improve efficiency and thereby reduce fuel consumption.
  • An example of a fluid flow machine is a turbocharger.
  • the turbocharger and especially the turbocharger housing should be accurately suited to the power characteristic of the engine at hand.
  • gap dimensions have to be maintained before, during, and after operation. Temperature differences of up to several 100° C. are encountered between various operating conditions, causing the various structural parts and used materials as well as material thicknesses to undergo expansions which deviate from one another. In the event of an expansion, gap dimensions change so that the presence of an unwanted blow-by within the turbocharger may be encountered. This adversely affects efficiency.
  • components may come into contact with one another as a result of different expansions. In the worst case scenario, components collide, causing damage or a total breakdown of the turbocharger.
  • German Pat. No. DE 100 22 052 A1 proposes a decoupling of exhaust-conducting components and supporting and sealing outer structures. While the exhaust-conducting components of a turbocharger are exposed to high thermal stress and thus glow during operation, the thermal stress on the sealing outer structure is markedly less. However, also the outer housing is subject to very high thermal stress and flow-based stress especially in the regions of attachment onto the bearing housing of a turbocharger and also at the inflow sides of the relatively hot exhausts.
  • the outer housing of an exhaust-gas turbocharger is normally made of unshaped sheet-metal shells which are typically welded by thermal joining with the bearing flanges. Also coupled with the bearing flanges is an inner housing of the exhaust-gas turbocharger.
  • the inner housing normally rests against the bearing flanges or is additionally coupled with the bearing flanges by a material joint. When the inner housing rests upon the bearing flanges, different thermal expansion coefficients may cause leakage and thus may cause a blow-by.
  • the heat impact zone of the thermal joining process is weakened in terms of geometry and material as a consequence of the thermal joining process. This region may thus encounter fatigue fracture and even crack formation under extreme stress conditions.
  • an exhaust-gas turbocharger includes an outer housing, a bearing flange connected to the outer housing by a material joint, a turbine wheel rotatable about a rotation axis, and an inner housing formfittingly connected to the bearing flange and formed with a collar which has at least one section in contact with an inner edge of the bearing flange in a direction of the rotation axis of the turbine wheel.
  • the term “collar”, as used in the specification relates to a projection which represents a circular section in the inner housing.
  • the collar points hereby with its projection in the direction of the rotation axis of the turbine wheel.
  • a coupling of the inner housing with the bearing flange via the collar and the inner edge refers in particular to a configuration of the collar as facing away from an interior space of the inner housing so as to be able to contact the edge of the bearing flange. This is beneficial because the inner housing can be positioned in radial and axial directions in an optimum manner so that rubbing or contact of the turbine housing is prevented during operation.
  • a formfitting coupling is ensured by a contact between inner housing and the bearing flange in at least one section via the collar and the edge. This formfitting coupling further compensates the required manufacturing tolerances as encountered during the production process of the exhaust-gas turbocharger.
  • a turbocharger with optimized gap width can thus be realized by a coupling in accordance with the invention.
  • the collar has a bearing-flange-proximal end and is defined by a diameter which may increase in a direction toward the bearing-flange-proximal end.
  • the diameter of the collar increases in the direction of the bearing flange to be coupled with the inner housing.
  • the collar receives a bulged configuration. This enhances flow dynamics and the bulged or flared configuration causes an even and/or reduced stress pattern in the collar.
  • the collar and the edge may touch one another in a formfitting manner so that the collar is arranged with an undercut in relation to the edge.
  • the presence of a formfitting seat between the collar and the edge is established.
  • the collar engages behind the edge so as to establish a locking function or a fit.
  • the establishment of a particularly firm seat between inner housing and bearing flange is an important aspect of the present invention.
  • the collar has in a transition zone between the inner housing and the collar a foot region which is defined by a bending radius.
  • a configuration of the collar in the form of a collared hole.
  • the collared hole extends from the inner housing and includes in relation to the inner housing a foot region in which the collar merges in a substantially funnel-shaped and/or cylinder-shaped collar portion.
  • the foot region can be defined by a bending radius which does not necessarily have to be constant but may vary about the rotation movement.
  • the foot region in particular, i.e. the transition between inner housing and collar, provides the turbocharger with a beneficial stress pattern.
  • the edge may have a geometry which is complementary to a geometry of the bending radius of the foot region.
  • the edge and the collar thus bear upon one another at least in one area to further promote an advantageous formfitting coupling. This is beneficial in particular when positioning the inner housing in radial and axial directions and in terms of a dimensional precision of the inner housing during operation of the turbocharger.
  • the collar and the edge touch one another with flat contact at least in one area of the bending radius of the foot region. This has a positive effect on the operation of the turbocharger. Any encountered expansions of components and resultant stress are thus streamlined in such a way as to establish a firm and tight seat between inner housing and bearing flange during the entire operation in the absence of critical stress peaks.
  • the collar and the edge may touch one another with flat contact in the direction of the rotation axis of the turbine wheel at least in one contact area which is oriented in the direction of the rotation axis of the turbine wheel.
  • the central orientation axis of the contact area extends hereby oriented essentially in the direction of the rotation axis of the turbine wheel. This is beneficial because of the presence of elastic reserves of the inner housing and the collar. Stress caused by different thermal expansions of components can be dispersed in particular in the contact area in the direction of the rotation axis of the turbine wheel to thereby extend the life of a turbocharger according to the invention.
  • the inner housing may be made of two half-shells, with one of the half-shells facing the bearing flange and having an S-shaped configuration.
  • the collar may be a component of an end portion of the S-shaped configuration. This reduces costs for manufacturing the half-shell.
  • the half-shell can be manufactured in one operating step in a forming tool.
  • any stress encountered in the inner housing and also between the inner housing and the outer housing can be advantageously compensated in a spring-like manner by the S-shaped configuration.
  • the inner housing can expand in relation to the outer housing without adversely affecting the efficiency or the operation of the exhaust-gas turbocharger.
  • the inner housing can have a wall thickness of less than 1.5 mm.
  • a wall thickness of less than 1 mm is preferred.
  • the wall thickness for the inner housing can be selected very small.
  • the exhaust-gas turbocharger can therefore be brought more rapidly to operating temperature and thus operates in an optimum efficiency range.
  • the overall system of the internal combustion engine and also the exhaust-gas aftertreatment can be brought more rapidly to operating temperature so that the starting behavior of for example a catalytic converter produces less emission during the start-up phase.
  • the collar and the edge may be coupled with one another by a material joint.
  • a material joint Currently preferred is a coupling of the collar and the edge by a radial circumferential weld seam.
  • the formfitting connection may be supplemented by a material joint. This has a positive effect on the life of the connection as well as on the tightness of the connection.
  • the collar can engage behind the edge and can be coupled with the edge through thermal joining in a circumferential joining zone at a bearing-flange-proximal end of the collar.
  • a weakening in this region as a result of heat impact by the thermal joining process and the presence of the weld seam is of no consequence as this region is not directly exposed to the flow of hot and highly corrosive exhaust gas. Again, this extends the life of an exhaust-gas turbocharger according to the invention.
  • FIG. 1 is a sectional view of an exhaust-gas turbocharger according to the present invention.
  • FIG. 2 shows an enlarged detailed view of coupling in an area between bearing flange and inner housing.
  • the exhaust-gas turbocharger 1 includes an outer housing 2 and an inner housing 3 arranged in the outer housing 2 .
  • Both the outer housing 2 and the inner housing 3 are each made of two half-shells, with the outer housing 2 comprised of a left half-shell 4 and a right half-shell 5 as relating to the drawing plane, and the inner housing 3 comprised of a left half-shell 6 and a right half-shell 7 .
  • the half-shells 4 , 5 , 6 , 7 have each a substantial S-shaped configuration.
  • the half-shells 6 , 7 of the inner housing 3 and the half-shells 4 , 5 of the outer housing 3 overlap one another, as indicated by reference numeral 8 by way of example.
  • the overlap 8 is configured in such a way that the right half-shells 5 , 6 overlap the left half-shells 4 , 6 , respectively.
  • the half-shells 4 , 5 , 6 , 7 are coupled to one another by a material joint in the form of a circumferential weld seam 9
  • the inner housing 3 is arranged on the left-hand side in relation to the drawing plane within the outer housing 2 with a sliding seat 10 .
  • the inner housing 3 Accommodated in the inner housing 3 is a turbine wheel 11 which is supported within the exhaust-gas turbocharger 1 by a turbine wheel shaft 12 , only indicated here.
  • the turbine wheel shaft 12 is thus determinative for the rotation axis 13 of the turbine wheel 11 .
  • the outer housing 2 is coupled on the right-hand side as relating to the drawing plane with a bearing flange 14 .
  • the coupling is realized by a formfit in a contact zone 15 and by a material joint in the form of a circumferential weld seam 9 .
  • the bearing flange 14 is further provided with an inner edge 16 .
  • the edge 16 defines an opening O within the bearing flange 14 .
  • the opening O is traversed by a collar 17 of the inner housing 3 so that the collar 17 is able to contact upon the edge 16 .
  • the collar 17 is defined by an internal diameter DI and an outer diameter DA which increases in the direction of the bearing flange 14 .
  • the collar 17 thus engages behind or is arranged in undercutting relationship to the bearing flange 14 in the area of the edge 16 to establish a firm formfitting engagement.
  • the presence of a circumferential weld seam 18 further reinforces the fixed positioning between the collar 17 and the edge 16 .
  • FIG. 2 shows an enlarged detailed view of coupling in an area between the collar 17 of the inner housing 3 and the edge 16 of the bearing flange 14 .
  • the edge 16 is illustrated with a bending radius R which extends in the direction of the bearing flange 14 .
  • the bending radius R may be variable depending on the function and thus need not be defined as a constant.
  • the collar 17 has a foot region 19 which corresponds to the contour of the bending radius R so as to establish a substantially flat contact.
  • the collar 17 and the edge 16 are also in substantial flat contact in a contact area 20 , with the contact surface having a center axis 21 which is oriented substantially in the direction of the rotation axis 13 (not shown here) of the turbine wheel 11 .
  • the inner housing 3 has a wall thickness W which is less than 1.5 mm. Currently preferred is a wall thickness of less than 1 mm.
  • a relief clearance 22 is provided between the bearing flange 14 and the inner housing 3 to ensure a reliable seat of the inner housing 3 upon the bearing flange 14 and a good tightness in the presence of thermal expansions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
US13/110,421 2010-05-20 2011-05-18 Exhaust-gas turbocharger Abandoned US20110286837A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010021114.1-13 2010-05-20
DE102010021114A DE102010021114A1 (de) 2010-05-20 2010-05-20 Abgasturbolader

Publications (1)

Publication Number Publication Date
US20110286837A1 true US20110286837A1 (en) 2011-11-24

Family

ID=43629590

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/110,421 Abandoned US20110286837A1 (en) 2010-05-20 2011-05-18 Exhaust-gas turbocharger

Country Status (4)

Country Link
US (1) US20110286837A1 (ja)
EP (1) EP2388455B1 (ja)
JP (1) JP2011241835A (ja)
DE (1) DE102010021114A1 (ja)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120282084A1 (en) * 2009-11-13 2012-11-08 Continental Automotive Gmbh Receptacle device for the rotor assembly of a turbocharger
US20120294709A1 (en) * 2011-05-19 2012-11-22 Benteler Automobiltechnik Gmbh Turbine housing of an exhaust-gas turbocharger
WO2015119829A1 (en) * 2014-02-04 2015-08-13 Borgwarner Inc. Exhaust-gas turbocharger
US20160201513A1 (en) * 2015-01-14 2016-07-14 Benteler Automobiltechnik Gmbh Turbine housing for an exhaust turbocharger
US9410470B2 (en) 2014-04-22 2016-08-09 Benteler Automobiltechnik Gmbh Exhaust manifold
US9416719B2 (en) 2013-08-30 2016-08-16 Benteler Automobiltechnik Gmbh Exhaust manifold with insulation sleeve
US9447698B2 (en) * 2012-05-09 2016-09-20 Benteler Automobil Technik Gmbh Double-walled turbocharger housing, flange and connection thereof
US20160290163A1 (en) * 2013-12-27 2016-10-06 Mitsubishi Heavy Industries, Ltd. Turbine housing
US9518501B2 (en) 2014-03-20 2016-12-13 Benteler Automobiltechnik Gmbh Exhaust manifold for exhaust system of a combustion engine
US9677453B2 (en) 2014-03-20 2017-06-13 Benteler Automobiltechnik Gmbh Exhaust manifold for an exhaust system of a combustion engine
US20180216494A1 (en) * 2017-01-30 2018-08-02 Honeywell International Inc. Sheet metal turbine housing with containment dampers
US20180216490A1 (en) * 2017-01-30 2018-08-02 Honeywell International Inc. Sheet metal turbine housing with biaxial volute configuration
US20190301304A1 (en) * 2018-03-27 2019-10-03 Man Energy Solutions Se Turbocharger
US10472988B2 (en) 2017-01-30 2019-11-12 Garrett Transportation I Inc. Sheet metal turbine housing and related turbocharger systems
US10519806B2 (en) * 2015-11-06 2019-12-31 Calsonic Kansei Corporation Turbine housing
US10544703B2 (en) 2017-01-30 2020-01-28 Garrett Transportation I Inc. Sheet metal turbine housing with cast core
US10570779B2 (en) * 2015-03-23 2020-02-25 Calsonic Kansei Corporation Turbine housing
US10823009B2 (en) * 2018-11-07 2020-11-03 Man Energy Solutions Se Method for working a housing of a turbocharger
US11732729B2 (en) 2021-01-26 2023-08-22 Garrett Transportation I Inc Sheet metal turbine housing

Families Citing this family (7)

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Publication number Priority date Publication date Assignee Title
JP5910114B2 (ja) * 2012-01-27 2016-04-27 トヨタ自動車株式会社 タービンハウジング及び排気タービン過給機
WO2014209852A1 (en) * 2013-06-28 2014-12-31 Borgwarner Inc. Turbocharger compressor-end carbon face seal
EP2851616A1 (en) 2013-09-19 2015-03-25 Alstom Technology Ltd Flue gas heat recovery integration
DE102013111561A1 (de) * 2013-10-21 2015-04-23 Ihi Charging Systems International Gmbh Abgasturbolader
DE102014116445B4 (de) 2014-11-11 2016-08-11 Benteler Automobiltechnik Gmbh Turbinengehäuse für einen Abgasturbolader
JP2016156279A (ja) * 2015-02-23 2016-09-01 カルソニックカンセイ株式会社 タービンハウジング
DE102017103980A1 (de) * 2017-02-27 2018-08-30 Man Diesel & Turbo Se Turbolader

Citations (1)

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US7074009B2 (en) * 2000-06-07 2006-07-11 Borgwarner, Inc. Casing assembly for the turbine of an exhaust turbochanger

Family Cites Families (8)

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DE29909018U1 (de) 1999-05-26 2000-09-28 Heinrich Gillet GmbH & Co. KG, 67480 Edenkoben Turbinengehäuse für Abgasturbolader
DE10028160C2 (de) * 2000-06-07 2003-03-27 Borgwarner Inc Gehäusegruppe für die Turbine eines Abgas-Turboladers
JP2002054447A (ja) * 2000-08-09 2002-02-20 Aisin Takaoka Ltd タービンハウジング
JP2003293779A (ja) * 2002-03-29 2003-10-15 Toyota Motor Corp タービンハウジング
DE10218436C1 (de) * 2002-04-25 2003-08-14 Benteler Automobiltechnik Gmbh Abgasturbine für einen Turbolader
JP2006161573A (ja) * 2004-12-02 2006-06-22 Toyota Motor Corp ターボチャージャのタービンハウジング
JP4448064B2 (ja) * 2005-06-24 2010-04-07 トヨタ自動車株式会社 タービンハウジング
DE102008052552B4 (de) * 2008-10-21 2015-06-11 Benteler Automobiltechnik Gmbh Turbinengehäuse und Verfahren zu seiner Herstellung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7074009B2 (en) * 2000-06-07 2006-07-11 Borgwarner, Inc. Casing assembly for the turbine of an exhaust turbochanger

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120282084A1 (en) * 2009-11-13 2012-11-08 Continental Automotive Gmbh Receptacle device for the rotor assembly of a turbocharger
US20120294709A1 (en) * 2011-05-19 2012-11-22 Benteler Automobiltechnik Gmbh Turbine housing of an exhaust-gas turbocharger
US9097181B2 (en) * 2011-05-19 2015-08-04 Benteler Automobil Technik Gmbh Turbine housing of an exhaust-gas turbocharger
US9447698B2 (en) * 2012-05-09 2016-09-20 Benteler Automobil Technik Gmbh Double-walled turbocharger housing, flange and connection thereof
US9416719B2 (en) 2013-08-30 2016-08-16 Benteler Automobiltechnik Gmbh Exhaust manifold with insulation sleeve
US20160290163A1 (en) * 2013-12-27 2016-10-06 Mitsubishi Heavy Industries, Ltd. Turbine housing
US10145267B2 (en) * 2013-12-27 2018-12-04 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine housing
WO2015119829A1 (en) * 2014-02-04 2015-08-13 Borgwarner Inc. Exhaust-gas turbocharger
US9518501B2 (en) 2014-03-20 2016-12-13 Benteler Automobiltechnik Gmbh Exhaust manifold for exhaust system of a combustion engine
US9677453B2 (en) 2014-03-20 2017-06-13 Benteler Automobiltechnik Gmbh Exhaust manifold for an exhaust system of a combustion engine
US9410470B2 (en) 2014-04-22 2016-08-09 Benteler Automobiltechnik Gmbh Exhaust manifold
US20160201513A1 (en) * 2015-01-14 2016-07-14 Benteler Automobiltechnik Gmbh Turbine housing for an exhaust turbocharger
CN105781634A (zh) * 2015-01-14 2016-07-20 本特勒尔汽车技术有限公司 用于废气涡轮增压器的涡轮壳体
US10094243B2 (en) * 2015-01-14 2018-10-09 Benteler Automobiltechnik Gmbh Turbine housing for an exhaust turbocharger
US10570779B2 (en) * 2015-03-23 2020-02-25 Calsonic Kansei Corporation Turbine housing
US10519806B2 (en) * 2015-11-06 2019-12-31 Calsonic Kansei Corporation Turbine housing
US20180216494A1 (en) * 2017-01-30 2018-08-02 Honeywell International Inc. Sheet metal turbine housing with containment dampers
US10436069B2 (en) * 2017-01-30 2019-10-08 Garrett Transportation I Inc. Sheet metal turbine housing with biaxial volute configuration
US10472988B2 (en) 2017-01-30 2019-11-12 Garrett Transportation I Inc. Sheet metal turbine housing and related turbocharger systems
US10494955B2 (en) * 2017-01-30 2019-12-03 Garrett Transportation I Inc. Sheet metal turbine housing with containment dampers
US10544703B2 (en) 2017-01-30 2020-01-28 Garrett Transportation I Inc. Sheet metal turbine housing with cast core
US20180216490A1 (en) * 2017-01-30 2018-08-02 Honeywell International Inc. Sheet metal turbine housing with biaxial volute configuration
US11035254B2 (en) 2017-01-30 2021-06-15 Garrett Transportation I Inc Sheet metal turbine housing with cast core
US20190301304A1 (en) * 2018-03-27 2019-10-03 Man Energy Solutions Se Turbocharger
US11041408B2 (en) * 2018-03-27 2021-06-22 Man Energy Solutions Se Turbocharger
US10823009B2 (en) * 2018-11-07 2020-11-03 Man Energy Solutions Se Method for working a housing of a turbocharger
US11732729B2 (en) 2021-01-26 2023-08-22 Garrett Transportation I Inc Sheet metal turbine housing

Also Published As

Publication number Publication date
JP2011241835A (ja) 2011-12-01
DE102010021114A1 (de) 2011-11-24
EP2388455B1 (de) 2017-04-05
EP2388455A3 (de) 2013-10-23
EP2388455A2 (de) 2011-11-23

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Owner name: BENTELER AUTOMOBILTECHNIK GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SMATLOCH, CHRISTIAN;GRUSSMANN, ELMAR;REEL/FRAME:026301/0359

Effective date: 20110513

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION