US20130045082A1 - Compressor of an exhaust-gas turbocharger - Google Patents

Compressor of an exhaust-gas turbocharger Download PDF

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Publication number
US20130045082A1
US20130045082A1 US13/643,097 US201113643097A US2013045082A1 US 20130045082 A1 US20130045082 A1 US 20130045082A1 US 201113643097 A US201113643097 A US 201113643097A US 2013045082 A1 US2013045082 A1 US 2013045082A1
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United States
Prior art keywords
compressor
inflow
inlet
wheel
exhaust
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
US13/643,097
Inventor
Udo Dellmann
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.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
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 BorgWarner Inc filed Critical BorgWarner Inc
Assigned to BORGWARNER INC. reassignment BORGWARNER INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DELLMANN, UDO
Publication of US20130045082A1 publication Critical patent/US20130045082A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
    • F01N1/165—Silencing apparatus characterised by method of silencing by using movable parts for adjusting flow area
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/16—Control of the pumps by bypassing charging air
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B2037/125—Control for avoiding pump stall or surge
    • 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 invention relates to a compressor of an exhaust-gas turbocharger, as per the preamble of claim 1 .
  • the compressor housing has an inflow duct which runs from the compressor outlet to the compressor inlet.
  • Said inflow duct is controlled by the overrun air recirculation valve in order, during operation of the exhaust-gas turbocharger, to prevent a pumping effect which may for example arise when, on account of a braking process of the motor vehicle, the throttle flap is closed but the exhaust-gas turbocharger would still run at high rotational speed.
  • the overrun air recirculation valve is opened and air is conducted from the compressor outlet, or the pressure side, to the compressor inlet, so as to ensure a continuous flow through the compressor wheel without a significant pressure build-up.
  • the inflow duct runs into the compressor inlet radially, which means that the inflow is directed toward the center of the shaft of the exhaust-gas turbocharger.
  • the inflow duct is arranged in the compressor housing in such a way as to open into the compressor inlet at least in the circumferential direction with respect to a tube inner diameter of the tubular compressor inlet.
  • Said opening may also be referred to as an at least substantially tangential opening, which leads to a tangential inflow, or an inflow directed in the circumferential direction, of the air recirculated from the pressure side into the inducted air, which inflow has at least substantially no disruptive influence on the compressor wheel and therefore reduces the flow noises explained in the introduction at least to such an extent that the noises are practically no longer perceptible.
  • the inflow directed substantially in the circumferential direction may also have an axial component directed in the flow direction in order to reduce inflow losses.
  • the compressor inlet may be provided with a cylindrical or frustoconical inflow section into which the inflow duct opens in the way explained above.
  • the inflow duct opens into the compressor inlet in such a way that the inflow of the recirculated air leads in the direction of rotation of the compressor wheel.
  • An inflow counter to the direction of rotation of the compressor wheel is, however, also possible in principle.
  • FIG. 1 shows a perspective, partially cut-away illustration of an exhaust-gas turbocharger which may be provided with a compressor according to the invention
  • FIGS. 2 , 3 show a first embodiment of a compressor according to the invention.
  • FIG. 4 shows a second embodiment of a compressor according to the invention.
  • FIG. 1 illustrates an exhaust-gas turbocharger 1 according to the invention which has a turbine housing 2 comprising an exhaust-gas inlet opening 3 and an exhaust-gas outlet opening 4 .
  • a turbine wheel 5 is arranged in the turbine housing 2 , which turbine wheel is fastened to a shaft 6 .
  • a multiplicity of blades, of which only the blade 7 is shown, is arranged in the turbine housing 2 between the exhaust-gas inlet opening 3 and the turbine wheel 5 .
  • the exhaust-gas turbocharger 1 has a compressor 8 , the compressor housing 10 of which is in the usual way connected via a bearing housing 9 to the turbine housing 2 .
  • a compressor wheel 11 is fastened to the second end of the shaft 6 .
  • FIGS. 2 and 3 clearly shows in FIG. 2 the compressor wheel by the three plotted arrows VR together with the label “direction of rotation VR”, which symbolizes the compressor wheel 11 with its associated direction of rotation.
  • the compressor wheel 11 is shown in FIG. 3 and is arranged on the shaft 6 .
  • FIG. 2 the inflow duct of the overrun air recirculation valve (not visible in the figures) is denoted by the reference numeral 14 , with said inflow duct 14 opening along the two dashed directions approximately in the circumferential direction or tangentially with respect to the inner diameter (see FIG. 4 , D I ).
  • FIG. 3 clearly shows an inflow duct opening 16 which opens into a tubular or funnel-shaped or frustoconical funnel inlet 12 , in such a way as to permit a tangential inflow of the air recirculated from the compressor outlet 13 .
  • the inflow here runs counter to the direction of rotation VR.
  • the dash-dotted parallel lines which are additionally shown in FIG. 2 and which are identified by the reference symbol ZK serve merely to clearly show the arrangement of the inflow duct according to the prior art. Said illustration of the dashed lines ZK clearly shows an arrangement of the inflow duct radially with respect to the shaft 6 , which is associated with the problems explained in the introduction.
  • said additional plotting of the known inflow duct ZK in FIG. 2 serves merely to clearly show the differences between the prior art and the invention; such an inflow duct ZK is not provided in the compressor according to the invention either in the embodiment according to FIGS. 2 and 3 or in the embodiment according to FIG. 4 .
  • FIG. 4 shows a second embodiment of the compressor 8 according to the invention, which like the embodiment according to FIGS. 2 and 3 self-evidently has a compressor housing 10 with a compressor inlet 12 (not visible in the selected illustration) and a compressor outlet 13 .
  • the inflow duct 15 likewise indicated in FIG. 4 by means of dashed lines has a first, rectilinearly running duct section 15 a and, adjoining the latter, a bent duct section 15 b which results in the above-explained opening aligned tangentially, or substantially in the circumferential direction, with respect to the inner diameter D I of the compressor inlet 12 .
  • the opening takes place such that the inflow of recirculated air runs in the direction of rotation VR of the compressor wheel 11 , which is likewise symbolized by the arrow YR in FIG. 4 .
  • FIGS. 1 to 4 Aside from the written disclosure of the invention, reference may additionally be made to the graphic illustration thereof in FIGS. 1 to 4 , in particular in FIGS. 2 to 4 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)

Abstract

A compressor (8) of an exhaust-gas turbocharger (1), having a compressor wheel (11) which can be driven in a compressor wheel direction of rotation (VR); having a compressor housing (10) in which the compressor wheel (11) is arranged, as viewed in the flow direction of the inducted air, between a preferably tubular compressor inlet (12) and a compressor outlet (13), and having an overrun air recirculation valve inflow duct (14, 15) which runs in the compressor housing (10) from the compressor outlet (13) to the compressor inlet (12), wherein the inflow duct (14, 15) opens into the compressor inlet (12) substantially in the circumferential direction with respect to the inner diameter (DI) of said compressor inlet (12).

Description

  • The invention relates to a compressor of an exhaust-gas turbocharger, as per the preamble of claim 1.
  • In the generic compressor which is provided with an overrun air recirculation valve, the compressor housing has an inflow duct which runs from the compressor outlet to the compressor inlet. Said inflow duct is controlled by the overrun air recirculation valve in order, during operation of the exhaust-gas turbocharger, to prevent a pumping effect which may for example arise when, on account of a braking process of the motor vehicle, the throttle flap is closed but the exhaust-gas turbocharger would still run at high rotational speed. In this situation, to prevent the stated effect, the overrun air recirculation valve is opened and air is conducted from the compressor outlet, or the pressure side, to the compressor inlet, so as to ensure a continuous flow through the compressor wheel without a significant pressure build-up.
  • In the already known design, the inflow duct runs into the compressor inlet radially, which means that the inflow is directed toward the center of the shaft of the exhaust-gas turbocharger.
  • Tests carried out within the context of the invention with said design of a known exhaust-gas turbocharger have shown that, on account of the stated opening of the inflow duct radially with respect to the shaft as a result of the inflow direction to the compressor wheel, flow noise is generated which can lead to undesired noise disturbance during the operation of a vehicle provided with an exhaust-gas turbocharger of said type.
  • In contrast, it is an object of the present invention to provide a compressor of the type specified in the preamble of claim 1, which compressor makes it possible to avoid or considerably reduce the explained flow noises, and also dampen any occurring resonances.
  • Said object is achieved by means of the features of claim 1.
  • According to said claim, the inflow duct is arranged in the compressor housing in such a way as to open into the compressor inlet at least in the circumferential direction with respect to a tube inner diameter of the tubular compressor inlet. Said opening may also be referred to as an at least substantially tangential opening, which leads to a tangential inflow, or an inflow directed in the circumferential direction, of the air recirculated from the pressure side into the inducted air, which inflow has at least substantially no disruptive influence on the compressor wheel and therefore reduces the flow noises explained in the introduction at least to such an extent that the noises are practically no longer perceptible.
  • The inflow directed substantially in the circumferential direction may also have an axial component directed in the flow direction in order to reduce inflow losses.
  • For this purpose, the compressor inlet may be provided with a cylindrical or frustoconical inflow section into which the inflow duct opens in the way explained above.
  • The subclaims relate to advantageous refinements of the invention.
  • In a particularly preferred embodiment, the inflow duct opens into the compressor inlet in such a way that the inflow of the recirculated air leads in the direction of rotation of the compressor wheel. An inflow counter to the direction of rotation of the compressor wheel is, however, also possible in principle.
  • Further details, advantages and features of the present invention will emerge from the following description of exemplary embodiments on the basis of the drawing, in which:
  • FIG. 1 shows a perspective, partially cut-away illustration of an exhaust-gas turbocharger which may be provided with a compressor according to the invention,
  • FIGS. 2, 3 show a first embodiment of a compressor according to the invention, and
  • FIG. 4 shows a second embodiment of a compressor according to the invention.
    •
  • FIG. 1 illustrates an exhaust-gas turbocharger 1 according to the invention which has a turbine housing 2 comprising an exhaust-gas inlet opening 3 and an exhaust-gas outlet opening 4.
  • Furthermore, a turbine wheel 5 is arranged in the turbine housing 2, which turbine wheel is fastened to a shaft 6.
  • A multiplicity of blades, of which only the blade 7 is shown, is arranged in the turbine housing 2 between the exhaust-gas inlet opening 3 and the turbine wheel 5.
  • Furthermore, the exhaust-gas turbocharger 1 has a compressor 8, the compressor housing 10 of which is in the usual way connected via a bearing housing 9 to the turbine housing 2. In the compressor housing 10, a compressor wheel 11 is fastened to the second end of the shaft 6. The details of the compressor 8 according to the invention will be explained below on the basis of FIGS. 2 to 4, which illustrate two embodiments of the compressor 8 according to the invention which may be used in the exhaust-gas turbocharger 1 illustrated in FIG. 1.
  • The embodiment according to FIGS. 2 and 3 clearly shows in FIG. 2 the compressor wheel by the three plotted arrows VR together with the label “direction of rotation VR”, which symbolizes the compressor wheel 11 with its associated direction of rotation. The compressor wheel 11 is shown in FIG. 3 and is arranged on the shaft 6.
  • In FIG. 2, the inflow duct of the overrun air recirculation valve (not visible in the figures) is denoted by the reference numeral 14, with said inflow duct 14 opening along the two dashed directions approximately in the circumferential direction or tangentially with respect to the inner diameter (see FIG. 4, DI). Here, FIG. 3 clearly shows an inflow duct opening 16 which opens into a tubular or funnel-shaped or frustoconical funnel inlet 12, in such a way as to permit a tangential inflow of the air recirculated from the compressor outlet 13. As is clearly shown in FIGS. 2 and 3, the inflow here runs counter to the direction of rotation VR.
  • The dash-dotted parallel lines which are additionally shown in FIG. 2 and which are identified by the reference symbol ZK serve merely to clearly show the arrangement of the inflow duct according to the prior art. Said illustration of the dashed lines ZK clearly shows an arrangement of the inflow duct radially with respect to the shaft 6, which is associated with the problems explained in the introduction. Here, it is mentioned once again that said additional plotting of the known inflow duct ZK in FIG. 2 serves merely to clearly show the differences between the prior art and the invention; such an inflow duct ZK is not provided in the compressor according to the invention either in the embodiment according to FIGS. 2 and 3 or in the embodiment according to FIG. 4.
  • FIG. 4 shows a second embodiment of the compressor 8 according to the invention, which like the embodiment according to FIGS. 2 and 3 self-evidently has a compressor housing 10 with a compressor inlet 12 (not visible in the selected illustration) and a compressor outlet 13. The inflow duct 15 likewise indicated in FIG. 4 by means of dashed lines has a first, rectilinearly running duct section 15 a and, adjoining the latter, a bent duct section 15 b which results in the above-explained opening aligned tangentially, or substantially in the circumferential direction, with respect to the inner diameter DI of the compressor inlet 12. Here, the opening takes place such that the inflow of recirculated air runs in the direction of rotation VR of the compressor wheel 11, which is likewise symbolized by the arrow YR in FIG. 4.
  • Aside from the written disclosure of the invention, reference may additionally be made to the graphic illustration thereof in FIGS. 1 to 4, in particular in FIGS. 2 to 4.
    • LIST OF REFERENCE SYMBOLS
    • 1 Exhaust-gas turbocharger
    • 2 Turbine housing
    • 3 Exhaust-gas inlet opening
    • 4 Exhaust-gas outlet opening
    • 5 Turbine wheel
    • 6 Shaft
    • 7 Blade
    • 8 Compressor
    • 9 Bearing housing
    • 10 Compressor housing
    • 11 Compressor wheel
    • 12 Compressor inlet
    • 13 Compressor outlet
    • 14 Overrun air recirculation valve inflow duct
    • 15 Overrun air recirculation valve inflow duct
    • 15 a, b Duct sections
    • 16 Duct opening
    • ZK Inflow duct of the prior art
    • VR Direction of rotation of the compressor wheel 11
    • DI Inner diameter of the compressor inlet 12

Claims (5)

1. A compressor (8) of an exhaust-gas turbocharger (1),
having a compressor wheel (11) which can be driven in a compressor wheel direction of rotation (VR);
having a compressor housing (10) in which the compressor wheel (11) is arranged, as viewed in the flow direction of the inducted air, between a compressor inlet (12) and a compressor outlet (13), and
having an overrun air recirculation valve inflow duct (14, 15) which runs in the compressor housing (10) from the compressor outlet (13) to the compressor inlet (12), wherein
the inflow duct (14, 15) opens into the compressor inlet (12) substantially in the circumferential direction with respect to the inner diameter (DI) of said compressor inlet (12).
2. The compressor as claimed in claim 1, wherein the inflow duct (15) opens into the compressor inlet (12) in such a way that the inflow of air takes place in the direction of rotation (VR) of the compressor wheel (11).
3. The compressor as claimed in claim 1, wherein the inflow duct (14) opens into the compressor inlet (12) in such a way that the inflow of air takes place counter to the direction of rotation (VR) of the compressor wheel (11).
4. The compressor as claimed in claim 1, wherein the inflow duct (14) opens into the compressor inlet (12) in such a way that the inflow of air has an axial component in the flow direction.
5. The compressor as claimed in claim 1, wherein compressor inlet (12) is tubular.
US13/643,097 2010-04-27 2011-04-20 Compressor of an exhaust-gas turbocharger Abandoned US20130045082A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010018429.2 2010-04-27
DE102010018429 2010-04-27
PCT/US2011/033181 WO2011139561A2 (en) 2010-04-27 2011-04-20 Compressor of an exhaust-gas turbocharger

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US20130045082A1 true US20130045082A1 (en) 2013-02-21

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US13/643,097 Abandoned US20130045082A1 (en) 2010-04-27 2011-04-20 Compressor of an exhaust-gas turbocharger

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US (1) US20130045082A1 (en)
JP (1) JP2013525685A (en)
KR (1) KR20130058689A (en)
CN (1) CN102859143A (en)
DE (1) DE112011101494T5 (en)
WO (1) WO2011139561A2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150377194A1 (en) * 2014-06-30 2015-12-31 Honda Motor Co., Ltd. Internal-combustion-engine supercharger
US20180058309A1 (en) * 2015-08-11 2018-03-01 Bayerische Motoren Werke Aktiengesellschaft Compressor of a Turbocharger Having an Air Recirculation Valve and Turbocharger and Motor Vehicle Having Such a Compressor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101989544B1 (en) * 2012-03-06 2019-09-30 보르그워너 인코퍼레이티드 Exhaust-gas turbocharger
CN103233899B (en) * 2013-05-20 2016-05-04 中国南方航空工业(集团)有限公司 Mechanical pressurizing apparatus and there is the piston engine of this device
EP3736419B1 (en) * 2018-07-06 2023-05-31 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger
DE102020111504A1 (en) 2020-04-28 2021-10-28 Bayerische Motoren Werke Aktiengesellschaft Compressor device

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US7475539B2 (en) * 2006-05-24 2009-01-13 Honeywell International, Inc. Inclined rib ported shroud compressor housing
US8161745B2 (en) * 2006-11-09 2012-04-24 Borgwarner Inc. Turbocharger

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JPS56167813A (en) * 1980-05-28 1981-12-23 Nissan Motor Co Ltd Surge preventing apparatus for turbocharger
JPH086601B2 (en) * 1989-05-19 1996-01-29 三菱重工業株式会社 Boost pressure control valve device
JP3493989B2 (en) * 1997-12-19 2004-02-03 日産自動車株式会社 Centrifugal supercharger
JP2002195046A (en) * 2000-12-26 2002-07-10 Hitachi Ltd Exhaust gas turbine for internal combustion engine and the exhaust gas turbine supercharger
WO2007088043A1 (en) * 2006-02-02 2007-08-09 Borgwarner Inc. Turbocharger

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7475539B2 (en) * 2006-05-24 2009-01-13 Honeywell International, Inc. Inclined rib ported shroud compressor housing
US8161745B2 (en) * 2006-11-09 2012-04-24 Borgwarner Inc. Turbocharger

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150377194A1 (en) * 2014-06-30 2015-12-31 Honda Motor Co., Ltd. Internal-combustion-engine supercharger
US9982590B2 (en) * 2014-06-30 2018-05-29 Honda Motor Co., Ltd. Internal-combustion-engine supercharger
US20180058309A1 (en) * 2015-08-11 2018-03-01 Bayerische Motoren Werke Aktiengesellschaft Compressor of a Turbocharger Having an Air Recirculation Valve and Turbocharger and Motor Vehicle Having Such a Compressor
US10774731B2 (en) * 2015-08-11 2020-09-15 Bayerische Motoren Werke Aktiengesellschaft Compressor of a turbocharger having an air recirculation valve and turbocharger and motor vehicle having such a compressor

Also Published As

Publication number Publication date
DE112011101494T5 (en) 2013-02-07
KR20130058689A (en) 2013-06-04
WO2011139561A3 (en) 2012-02-09
CN102859143A (en) 2013-01-02
JP2013525685A (en) 2013-06-20
WO2011139561A2 (en) 2011-11-10

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Owner name: BORGWARNER INC., MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DELLMANN, UDO;REEL/FRAME:029191/0287

Effective date: 20110427

STCB Information on status: application discontinuation

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