US20100310365A1 - Turbocharger - Google Patents

Turbocharger Download PDF

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Publication number
US20100310365A1
US20100310365A1 US12/863,055 US86305508A US2010310365A1 US 20100310365 A1 US20100310365 A1 US 20100310365A1 US 86305508 A US86305508 A US 86305508A US 2010310365 A1 US2010310365 A1 US 2010310365A1
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US
United States
Prior art keywords
turbine housing
peripheral end
exhaust nozzle
seal member
gap
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
US12/863,055
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English (en)
Inventor
Yoshimitsu Matsuyama
Yukio Takahashi
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.)
IHI Corp
Original Assignee
IHI Corp
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 IHI Corp filed Critical IHI Corp
Assigned to IHI CORPORATION reassignment IHI CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUYAMA, YOSHIMITSU, TAKAHASHI, YUKIO
Publication of US20100310365A1 publication Critical patent/US20100310365A1/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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
    • 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
    • F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Definitions

  • the present invention relates to a turbocharger wherein gas is prevented from leaking from higher pressure side to lower pressure side through a gap between a turbine housing and an exhaust nozzle.
  • FIG. 1 shows a conventional variable displacement turbocharger to which the invention is applied.
  • turbine and compressor housings 1 and 2 are integrally assembled through a bearing housing 3 by fastening bolts 3 a and 3 b , a turbine impeller 4 in the turbine housing 1 being connected to a compressor impeller 5 in the compressor housing 2 by a turbine shaft 7 rotatably supported via a bearing 6 in the bearing housing 3 .
  • the bearing housing 3 is provided, on its turbine housing 1 side, with an exhaust nozzle 9 by which the fluid (exhaust gas) introduced into a scroll passage 8 in the turbine housing 1 is guided to the turbine impeller 4 .
  • the exhaust nozzle 9 comprises front and rear exhaust guide walls 10 and 11 on sides of the bearing and turbine housings 3 and 1 , respectively, integrally assembled together with a required distance being retained between them by, for example, three fixing members 12 arranged circumferentially.
  • an attachment member 13 fixed to a front surface of the front wall 10 i.e., a surface adjacent to the bearing housing 3
  • the exhaust nozzle 9 is positioned relative to the bearing housing 3 by a positioning pin 14 .
  • each of the nozzle vanes 15 is dually supported such that the nozzle vane 15 has vane shafts 16 a and 16 b fixed to opposite sides of the vane 15 and extending through the front and rear walls 10 and 11 , respectively.
  • the nozzle vane 15 may be supported in a cantilever manner only by the vane shaft 16 a extending through the front wall 10 .
  • reference numerals 17 a , 17 b , 17 c and 17 d designate a linked transmission mechanism for control of opening angle of the nozzle vanes 15 ; and 18 , a scroll passage formed in the compressor housing 2 .
  • a gap 19 which is unwanted by nature and which is however provided for countermeasure to, for example, possible thermal deformation of the turbine housing 1 between during being hot and during being cold and possible variations in accuracy of parts to be assembled.
  • the gap 19 may disadvantageously cause the exhaust gas in the passage 8 to vainly leak to a turbine impeller outlet 20 .
  • sealing piston rings 21 between an outer periphery on a downstream extension 11 ′ of the rear wall 11 and an inner surface 1 ′ of the turbine housing 1 confronting the extension 11 ′ so as to prevent the gas leakage and absorb any thermal deformation (see Patent Literature 1).
  • Patent Literature 1 As shown in FIG. 2 , formed on the outer periphery of the extension 11 ′ of the rear wall 11 is an annular groove 22 into which generally two sealing piston rings 21 are inserted with their closed gaps or cutouts being not aligned or overlapped with each other, thereby providing a sealing device 23 .
  • the piston rings 21 are pressed at their outer peripheries against the inner surface 1 ′ of the turbine housing 1 by spring force of the piston rings themselves to prevent the gas leakage.
  • the piston ring 21 is not an complete annulus but has a gap or cutout, so that even if the two piston rings 21 are arranged with their cutouts being not aligned, disadvantageously, gas may leak through the cutouts.
  • the piston rings 21 which are pressed for sealing against the inner surface 1 ′ of the turbine housing 1 through their predetermined spring force, must have high strength. Thus, even if the inner surface 1 ′ is machined with high degree of circularity, spacing may be produced between the inner surface 1 ′ and the piston rings 21 when the piston rings 21 have slight distortion in circularity, disadvantageously resulting in gas leakage through outer peripheries of the piston rings 21 .
  • the invention was made in view of the above and has its object to provide a turbocharger which is simple in structure and which can effectively prevent gas from leaking from higher pressure side to lower pressure side through a gap between a turbine housing and an exhaust nozzle.
  • the invention is directed to a turbocharger having an exhaust nozzle between a scroll passage of a turbine housing and a turbine impeller, a gap between a rear surface of said exhaust nozzle and said turbine housing and a sealing device for closing said gap, characterized in that said sealing device comprises a seal member in the form of an annulus with a part cut out for provision of a slit and having an inner peripheral end arranged along said turbine housing, said seal member being configured such that, by the action of gas pressure in the scroll passage, an outer peripheral end of the member approaches the rear surface of the exhaust nozzle, slit ends of the member approach to each other and an inner peripheral end of the member approaches said turbine housing, resulting in decrease in diameter of the member.
  • said slit is formed to have distance at the outer peripheral end greater than that at the inner peripheral end.
  • said seal member is substantially frustoconical to have diameter gradually increased from turbine housing side to exhaust nozzle side.
  • an inner peripheral end of a seal member is arranged along a step on a turbine housing so that, by the action of gas pressure in the scroll passage, an outer peripheral end of the seal member approaches the rear surface of the exhaust nozzle and, due to pressure difference between the gas pressure in the scroll passage and the pressure in the gap, the slit ends approach to each other and the inner peripheral end of the member approaches the step, leading to reduction in diameter of the seal member.
  • the invention has an excellent effect that, with a simple structure, a gap between the turbine housing and the rear surface of the exhaust nozzle can be closed with high sealability.
  • FIG. 1 is a sectional side view of a conventional turbocharger
  • FIG. 2 is a sectional side view of the nozzle and its vicinity in FIG. 1 ;
  • FIG. 3 is a sectional side view of a nozzle and its vicinity showing an embodiment of the invention
  • FIG. 4 is a sectional side view which is different from FIG. 3 in how to support the nozzle vanes of the exhaust nozzle;
  • FIG. 5 is a front view of the seal member shown in FIGS. 3 and 4 ;
  • FIG. 6 is a front view showing an example of slit shape in the seal member of FIG. 5 ;
  • FIG. 7 is a sectional side view showing a nozzle and its vicinity in a further embodiment of the invention.
  • FIG. 8 is a sectional side view showing a nozzle and its vicinity in a variation of FIG. 7 .
  • FIG. 3 is an embodiment of the invention applied to the turbocharger shown in FIGS. 1 and 2 in which a sealing device 25 is arranged between a turbine housing 1 and a rear surface 24 of an exhaust nozzle 9 so as to prevent gas in a scroll passage 8 from leaking via a gap 19 between the housing 1 and the surface 24 of the nozzle 9 to the turbine impeller 4 .
  • FIG. 3 shows an application to a turbocharger with the exhaust nozzle 9 where each of nozzle vanes 15 is supported at its opposite sides such that vane shafts 16 a and 16 b fixed to the opposite sides of the vane 15 extend through front and rear exhaust guide walls 10 and 11 , respectively.
  • the sealing device 25 is similarly applicable to the turbocharger with the exhaust nozzle 9 as shown in FIG. 4 where each of the nozzle vanes 15 is supported in a cantilever manner such that only the vane shaft 16 a extends through the front exhaust guide wall 10 .
  • a cylindrical step 27 in parallel with the turbine shaft is formed on an outer periphery of a portion 26 of the turbine housing 1 confronting the rear surface 24 of the exhaust nozzle 9 to provide the gap 19 ; and a seal member 29 is arranged on and fitted at its inner peripheral end 28 to the step 27 .
  • the seal member 29 comprises, as shown in FIG. 5 , a substantially frustoconical metal sheet which is peripherally cut out into C-shape to provide a slit 30 with width of the order of 0.2-0.8 mm.
  • the inner peripheral end 28 of the seal member 29 is bent, as shown in FIGS. 3 and 4 , in a direction away from the exhaust nozzle 9 to be fitted to the step 27 .
  • An outer peripheral end 33 of the seal member 29 comprises a conical straight portion 31 with diameter increased from the inner peripheral end 28 toward an outer peripheral end of the rear surface 24 of the exhaust nozzle 9 and a portion 32 curved for close contact with the rear surface 24 of the exhaust nozzle 9 .
  • the inner peripheral end 28 of the seal member 29 is fitted to the step 27 with slight spacing between them which allows its axial movement due to gas pressure in the scroll passage 8 .
  • the seal member 29 is formed to have deformation strength in terms of thickness which allows mutual approaching of the slit ends 29 a and 29 b due to the gas pressure in the scroll passage 8 for reduction in diameter.
  • the gas pressure in the scroll passage 8 acts on the seal member 29 ; in this time, the slit 30 in communication with the gap 19 has pressure lower than the gas pressure in the scroll passage 8 .
  • the slit ends 29 a and 29 b receive mutually attractive powers to approach to each other and the inner peripheral end 28 also approaches the step 27 , leading to reduction in diameter of the seal member 29 .
  • the slit 30 may be wedge-shaped as shown in FIG. 6 such that the distance of the same is gradually increased from distance S 1 at the inner peripheral end 28 to distance S 2 at the outer peripheral end 33 .
  • the turbine housing 1 is integrally assembled to the bearing housing 3 , using a fastening bolt 3 a as shown in FIG. 1 .
  • the seal member 29 arranged in the turbine housing 1 is urged by gas pressure in the scroll passage 8 (pressure difference between pressure in the scroll flow passage 8 and pressure in the gap 19 ) in a direction of arrow A, so that the curved portion 32 of the outer peripheral end 33 of the seal member 29 approaches and is closely fitted to the rear surface 24 of the rear wall 11 of the exhaust nozzle 9 .
  • the outer peripheral end 32 of the seal member 29 is closely fitted to the rear surface 24 of the exhaust nozzle 9 so that the spacing between the same and the exhaust nozzle 9 is closed and the slit ends 29 a and 29 b of the seal member 29 approach to each other and the inner peripheral end 28 approaches the step 27 , leading to reduction in diameter of the seal member 29 .
  • the gap 19 between the turbine housing 1 and the exhaust nozzle 9 can be closed with high sealability.
  • the slit 30 is formed such that the distance S 2 at the outer peripheral end 33 is greater than the distance S 1 at the inner peripheral end 28 , then as the seal member 29 is reduced in diameter, the slit ends 29 a and 29 b uniformly approach to each other into substantially close contact with each other, thereby further enhancing the sealability at slit 30 .
  • FIG. 7 shows a further embodiment of the invention in which a C-shaped seal member 29 has substantially L-shaped cross-section and is configured such that by the action of the gas pressure in the scroll passage 8 the outer peripheral end 33 approaches the rear surface of the rear wall 11 of the exhaust nozzle 9 , and as shown in FIG. 5 the slit ends 29 a and 29 b approach to each other and the inner peripheral end 28 approaches the step 27 formed on the turbine housing 1 , leading to reduction in diameter of the member. Also with the shape of the seal member 29 shown in FIG. 7 , the exhaust gas pressure in the scroll passage 8 is utilized to close the gap 19 so that leakage of exhaust gas through the gap 19 can be reduced.
  • the FIG. 7 shows a further embodiment of the invention in which a C-shaped seal member 29 has substantially L-shaped cross-section and is configured such that by the action of the gas pressure in the scroll passage 8 the outer peripheral end 33 approaches the rear surface of the rear wall 11 of the exhaust nozzle 9 , and as shown in FIG. 5 the slit ends 29 a and 29
  • a projection 35 extends from the turbine housing 1 to provide a guide spacing 34 at the outer periphery of the rear exhaust guide wall 11 , a guide chamber 36 in communication with the guide spacing 34 being formed on the turbine housing 1 to thereby provide a step 27 on which the seal member 29 is arranged.
  • the C-shaped seal member 29 may be stepped as shown in FIG. 8 such that the inner peripheral end 28 extends along the step 27 toward the exhaust nozzle 9 , extends radially outwardly and then extend in parallel with the turbine shaft toward the exhaust nozzle 9 so that the outer peripheral end 33 approaches the rear surface of the rear wall 11 of the exhaust nozzle 9 ; or it may be of other various shapes.
  • the above-mentioned seal member 29 which may be very simple in structure, can be produced at inexpensive costs and with high productivity.
  • the sealing device 25 with the seal member 29 is arranged for sealing upstream, in the exhaust gas flow, of a through-hole 16 ′ (i.e., at the scroll passage 8 side) via which each vane shaft 16 b extends through the rear exhaust guide wall 11 so that due to the fact that the pressure in the gap 19 downstream of the seal member 29 is lower than the pressure of the exhaust gas flowing through the exhaust nozzle 9 , the exhaust gas in the exhaust nozzle 9 flows through the through-hole 16 ′ for the vane shaft 16 b into the gap 19 ; moreover, due to the pressure difference between the pressure in the exhaust nozzle 9 and the pressure in the gap 19 , the nozzle vane 15 is urged and displaced to the rear exhaust guide wall 11 so that a flange 16 ′′ on the vane shaft 16 b is pushed to the rear wall 11 to close the through-hole 16 ′. As a result, the gas in the exhaust nozzle 9 is prevented from flowing through the through-hole 16 ′ for the vane shaft 16 b into
  • the turbocharger is provided with a seal member which is utilized for enhancement of the sealability of the turbocharger, the seal member being configured such that, by the action of the gas pressure in the scroll passage, the outer peripheral end approaches the rear surface of the exhaust nozzle, the slit ends approach to each other and the inner peripheral end approaches the turbine housing, leading to reduction in diameter of the member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
US12/863,055 2008-02-20 2008-12-09 Turbocharger Abandoned US20100310365A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2008-038423 2008-02-20
JP2008038423A JP2009197633A (ja) 2008-02-20 2008-02-20 ターボチャージャ
PCT/JP2008/003657 WO2009104232A1 (fr) 2008-02-20 2008-12-09 Turbocompresseur

Publications (1)

Publication Number Publication Date
US20100310365A1 true US20100310365A1 (en) 2010-12-09

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US12/863,055 Abandoned US20100310365A1 (en) 2008-02-20 2008-12-09 Turbocharger

Country Status (6)

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US (1) US20100310365A1 (fr)
EP (1) EP2243939A4 (fr)
JP (1) JP2009197633A (fr)
KR (1) KR101182121B1 (fr)
CN (1) CN101946069B (fr)
WO (1) WO2009104232A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120251298A1 (en) * 2011-04-04 2012-10-04 Simon Moore Turbine
US20140099191A1 (en) * 2011-07-20 2014-04-10 Ihi Charging Systems International Gmbh Turbine for an exhaust gas turbocharger
US20150013330A1 (en) * 2013-07-09 2015-01-15 Ford Global Technologies, Llc System and method for variable tongue spacing in a multi-channel turbine in a charged internal combustion engine
US20150056067A1 (en) * 2012-05-29 2015-02-26 Ihi Corporation Variable nozzle unit and variable-geometry turbocharger
US9074687B2 (en) 2010-01-29 2015-07-07 Ihi Corporation Sealing device for turbocharger
US20160146037A1 (en) * 2014-11-21 2016-05-26 Borgwarner Inc. Variable turbine geometry vane with single-axle, self-centering pivot feature
US10030576B2 (en) 2012-09-10 2018-07-24 Ihi Corporation Variable geometry system turbocharger
US20180291922A1 (en) * 2015-10-29 2018-10-11 Mitsubishi Heavy Industries, Ltd. Scroll casing and centrifugal compressor
US10934867B2 (en) 2016-01-20 2021-03-02 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Stationary-blade-type rotating machine and method for assembling stationary-blade-type rotating machine
US11118508B2 (en) * 2016-08-24 2021-09-14 Ihi Corporation Variable displacement turbocharger
US11136900B2 (en) * 2017-12-20 2021-10-05 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine and turbocharger
US11326615B2 (en) 2017-03-17 2022-05-10 Ihi Corporation Seal structure of variable nozzle unit, and variable capacity type turbocharger
US11459907B2 (en) 2018-10-18 2022-10-04 Ihi Corporation Variable capacity turbocharger

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JP5849445B2 (ja) * 2011-06-13 2016-01-27 株式会社Ihi 可変ノズルユニット及び可変容量型過給機
US8763393B2 (en) 2011-08-08 2014-07-01 Honeywell International Inc. Sealing arrangement between a variable-nozzle assembly and a turbine housing of a turbocharger
DE102012206302A1 (de) 2011-08-18 2013-02-21 Bosch Mahle Turbo Systems Gmbh & Co. Kg Variable Turbinen-/Verdichtergeometrie
DE102011081187A1 (de) * 2011-08-18 2013-02-21 Bosch Mahle Turbo Systems Gmbh & Co. Kg Variable Turbinen-/Verdichtergeometrie
US8820072B2 (en) * 2011-08-23 2014-09-02 Honeywell International Inc. Compressor diffuser plate
DE102011111702A1 (de) 2011-08-24 2013-02-28 Ihi Charging Systems International Gmbh Turbine für einen Abgasturbolader
DE102012006711A1 (de) * 2012-01-18 2013-07-18 Ihi Charging Systems International Gmbh Abgasturbolader
CN103375197B (zh) * 2012-04-17 2016-12-07 博世马勒涡轮系统有限两合公司 可变涡轮/压缩机几何结构
US9011089B2 (en) 2012-05-11 2015-04-21 Honeywell International Inc. Expansion seal
US9353637B2 (en) 2012-05-11 2016-05-31 Honeywell International Inc. Turbine exhaust housing
US9556880B2 (en) 2013-06-26 2017-01-31 Honeywell International Inc. Turbine exhaust seal
US10087940B2 (en) 2014-12-10 2018-10-02 Honeywell International Inc. Exhaust turbine assembly
US10550705B2 (en) 2014-12-10 2020-02-04 Garrett Transportation I Inc. Turbine exhaust seal
US10746099B1 (en) * 2019-04-03 2020-08-18 GM Global Technology Operations LLC Multi-step bore turbocharger

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9074687B2 (en) 2010-01-29 2015-07-07 Ihi Corporation Sealing device for turbocharger
US9163524B2 (en) * 2011-04-04 2015-10-20 Cummins Ltd. Variable geometry turbine seal
US20120251298A1 (en) * 2011-04-04 2012-10-04 Simon Moore Turbine
US20140099191A1 (en) * 2011-07-20 2014-04-10 Ihi Charging Systems International Gmbh Turbine for an exhaust gas turbocharger
US9618005B2 (en) * 2012-05-29 2017-04-11 Ihi Corporation Variable nozzle unit and variable-geometry turbocharger
US20150056067A1 (en) * 2012-05-29 2015-02-26 Ihi Corporation Variable nozzle unit and variable-geometry turbocharger
US10030576B2 (en) 2012-09-10 2018-07-24 Ihi Corporation Variable geometry system turbocharger
US10006354B2 (en) * 2013-07-09 2018-06-26 Ford Global Technologies, Llc System and method for variable tongue spacing in a multi-channel turbine in a charged internal combustion engine
US20150013330A1 (en) * 2013-07-09 2015-01-15 Ford Global Technologies, Llc System and method for variable tongue spacing in a multi-channel turbine in a charged internal combustion engine
US20160146037A1 (en) * 2014-11-21 2016-05-26 Borgwarner Inc. Variable turbine geometry vane with single-axle, self-centering pivot feature
US10240480B2 (en) * 2014-11-21 2019-03-26 Borgwarner Inc. Variable turbine geometry vane with single-axle, self-centering pivot feature
US20180291922A1 (en) * 2015-10-29 2018-10-11 Mitsubishi Heavy Industries, Ltd. Scroll casing and centrifugal compressor
US10934867B2 (en) 2016-01-20 2021-03-02 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Stationary-blade-type rotating machine and method for assembling stationary-blade-type rotating machine
US11118508B2 (en) * 2016-08-24 2021-09-14 Ihi Corporation Variable displacement turbocharger
US11326615B2 (en) 2017-03-17 2022-05-10 Ihi Corporation Seal structure of variable nozzle unit, and variable capacity type turbocharger
US11136900B2 (en) * 2017-12-20 2021-10-05 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine and turbocharger
US11459907B2 (en) 2018-10-18 2022-10-04 Ihi Corporation Variable capacity turbocharger

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WO2009104232A1 (fr) 2009-08-27
JP2009197633A (ja) 2009-09-03
CN101946069A (zh) 2011-01-12
KR101182121B1 (ko) 2012-09-13
EP2243939A4 (fr) 2011-08-03
CN101946069B (zh) 2012-07-18
KR20100093617A (ko) 2010-08-25
EP2243939A1 (fr) 2010-10-27

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