WO2011101005A1 - Turbine pour turbocompresseur à gaz d'échappement - Google Patents

Turbine pour turbocompresseur à gaz d'échappement Download PDF

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Publication number
WO2011101005A1
WO2011101005A1 PCT/EP2010/007296 EP2010007296W WO2011101005A1 WO 2011101005 A1 WO2011101005 A1 WO 2011101005A1 EP 2010007296 W EP2010007296 W EP 2010007296W WO 2011101005 A1 WO2011101005 A1 WO 2011101005A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
turbine
exhaust gas
floods
closed
Prior art date
Application number
PCT/EP2010/007296
Other languages
German (de)
English (en)
Inventor
Thomas Kuhn
Nils Brinkert
Original Assignee
Daimler Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Ag filed Critical Daimler Ag
Publication of WO2011101005A1 publication Critical patent/WO2011101005A1/fr

Links

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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
    • 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
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
    • 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
    • F01D17/146—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by throttling the volute inlet of radial machines or engines
    • 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
    • F01D17/148—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of rotatable members, e.g. butterfly valves
    • 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
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • 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
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • 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
    • 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 turbine for an exhaust gas turbocharger specified in the preamble of claim 1. Art.
  • a flow distribution device Upstream of the floods a flow distribution device is arranged with a bypass, which a rotary valve with a rotation axis and a
  • the rotary valve has two
  • This known exhaust gas turbocharger has further potential to improve the efficiency of the internal combustion engine in an efficient manner.
  • a turbine according to the invention for an exhaust gas turbocharger comprises
  • Turbine housing in which an acted upon by an exhaust gas of an internal combustion engine turbine wheel is received and which at least two at least partially fluidly separated from each other and can be flowed through by the exhaust gas Has floods. Furthermore, the turbine comprises at least one closed position closing off at least one bypass duct and at least one valve which can open the bypass duct at least in regions and via which the turbine wheel is at least part of the turbine
  • the at least two flows are fluidically separated from one another in a separation area by the valve, wherein the valve has at least one intermediate position in which the flow channel is closed and the at least two floods are fluidically connected to one another in the separation area.
  • the turbine according to the invention thus enables, on the one hand, a so-called surge charging of the internal combustion engine assigned to the turbine.
  • the exhaust gas of the internal combustion engine from a subset of a total amount
  • the turbine according to the invention allows at least a reduction of the effect of the surge charging and the representation of a charge accumulation, in which the flows of the turbine or the turbine housing upstream of the turbine, at least in the intermediate position of the valve fluidly connected or connectable.
  • Combustion engine can benefit. This disadvantage is at least significantly reduced by the turbine according to the invention, which leads to efficient operation of the internal combustion engine. This is accompanied by a reduction in the fuel consumption of the internal combustion engine, resulting in low C0 2 emissions.
  • Torque characteristic of the internal combustion engine is associated.
  • the turbine according to the invention has a low complexity, whereby the advantages mentioned are achieved efficiently, inexpensively and with high reliability.
  • the valve has, for example, the shape of an axial slide, in which the valve is at least substantially translationally movable in the axial direction. Also possible is a rotary valve in which the valve is at least substantially rotationally movable to first fluidly connect the at least two floods together and free to give in the connection and, if necessary, the flow channel.
  • the at least two floods of the turbine housing or the turbine may be symmetrical to each other or asymmetrical to each other, in any embodiment, the said advantages of the efficiency improvement and thus the fuel consumption reduction and better response associated.
  • FIG. 1 in fragmentary form a schematic longitudinal sectional view of a
  • Fig. 3 in part a perspective longitudinal sectional view of another
  • FIG. 4 shows a detail of a longitudinal sectional view of a further embodiment of the turbine according to the invention.
  • FIG. 1 shows a turbine 10 for an exhaust-gas turbocharger with a turbine housing 12 which has a first flow 14 and a second flow 16.
  • the floods 14 and 16 are of an exhaust gas of a corresponding to the exhaust gas turbocharger
  • Internal combustion engine can be flowed through and at least partially fluidly separated from each other by a wall 18 of the turbine housing 12. Furthermore, the turbine 10 has a flow channel 20 through which at least a subset of the total exhaust gas can flow.
  • the exhaust gas flowing through the bypass duct 20 is conveyed through the bypass duct 20 to a turbine wheel, not shown in FIG. 1 and received in the turbine housing 12 bypassed, whereby the exhaust gas can handle the turbine wheel without it and handle it.
  • the flow channel 20 can be closed by a valve 22 of the turbine 10 which can be adjusted between a closed position and at least one open position, or can be opened at least in regions.
  • the two flows 14 and 16 are fluidically separated from one another in a separation region 24 by the valve 22.
  • the valve 22 comprises a valve disk 30 which is fixedly connected to a shaft 32 translationally displaceable in the direction of a directional arrow 26, whereby the valve disk 30 can also be moved in accordance with the directional arrow 26.
  • the valve also includes a valve cover 35, wherein the valve stem 32 and the valve disk 30 are slidable relative to the valve cover 35.
  • valve stem 32 and thus the valve plate 30 spent in the direction of a direction arrow 27 by a stroke, while the valve cover 35 of the valve 22 by Federkraftbeaufschlagung by a on the valve cover 35 and on the other hand on a flow channel 20 forming wall 34 supported spring element 28 to how before remaining on a valve cover 36 corresponding to the valve seat 36, the valve 22 assumes an intermediate position, in which the
  • Bypass passage 20 is further closed by the valve cover 35 of the valve 22, the two floods 14 and 16, however, are fluidically interconnected in the separation region 24.
  • Shock charge shown which results from a reduction in volume of exhaust-carrying volumes between cylinders of the internal combustion engine and the turbine 10, so is characterized by the executed intermediate position of the valve 22, in which therefore the floods 14 and 16 are fluidly connected to each other, a congestion charge.
  • Circulation passage 20 releases. This represents the functionality of a so-called
  • Wastegate is to further reduce the performance of the turbine 10.
  • the turbine 10 thus enables a very high efficiency of
  • FIG. 2 shows a further embodiment of the turbine 10, wherein the same applies to the turbine 10 according to FIG. 1 as for the turbine according to FIG. 2.
  • the difference between the turbine 10 according to FIG. 2 and the turbine 10 according to FIG. 1 consists in the fact that the valve 22 comprises a first valve disk 30 ', which in at least one position of the valve 22 fluidly separates the floods 14 and 16 at least in regions ,
  • the valve disk 30 ' is fixedly connected to the valve stem 32.
  • the valve 22 according to FIG. 2 comprises a second valve disk 30 ", wherein the valve disk 30 'and the valve stem 32 in turn are displaceable relative to the valve disk 30".
  • valve stem 32 which is movable in the direction according to the directional arrow 26, is moved in the direction of the directional arrow 27, the valve disk 30 'is also moved in the direction of the directional arrow 27. The valve disk 30 "is not moved thereby and closes the flow channel 20.
  • valve disk 30 If the valve disk 30 'has covered the stroke hi, then the floods 14 and 16 are fluidically connected to one another in the separation region 24, whereby the already described transition from the impact charge to the accumulation charge is created. If the valve 22 is moved further in the direction of the directional arrow 27, then the valve disk 30 'takes with it the second valve disk 30 "of the valve 22, and the valve disk 30" hitherto closing the bypass channel 20 releases the bypass channel 20. For this purpose, the valve 22 is now to operate against the spring force of the spring element 28, which is supported on the one hand on the wall 34 and on the other hand on the valve plate 30 ". If the actuation of the valve 22 of the turbine 10 according to FIG.
  • FIG. 3 shows a further embodiment of the turbine 10 the valve 22, which comprises the valve stem 32 and only one valve disc 30 "'.
  • the valve 22 of the turbine 10 according to FIG. 3 is to be referred to as axial slide, which has a translational, linear movement for adjusting the valve 22.
  • axial slide which has a translational, linear movement for adjusting the valve 22.
  • the floods 14 and 16 are fluidically separated from each other by the valve 22 and the flow channel 20 is closed.
  • the turbine 10 according to FIG. 3 has a particularly simple, cost-effective and functionally reliable design, with simultaneous realization of all the advantages already mentioned. Incidentally, for the turbine according to FIG. 3, the same applies to the turbine 10 according to FIGS. 1 and 2.
  • valve 22 again comprises only the single valve disk 30 ''.
  • valve disk 30 '' is now not translational but by means of a rotary valve or pivoting mechanism can be actuated at least essentially rotationally via a lever arm 38 which is firmly connected on one side to the valve disk 30 "and on the other hand can be pivoted about a pivot axis 40.
  • the turbine 10 according to FIG. 4 also has a simple and thus cost-effective and functionally reliable design with the simultaneous realization of the aforementioned advantages.

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

Abstract

L'invention concerne une turbine (10) pour un turbocompresseur à gaz d'échappement, ladite turbine comprenant un carter de turbine (12) dans lequel est logée une roue de turbine qui peut être soumise à l'effet d'un gaz d'échappement d'un moteur à combustion interne et qui présente au moins deux flux (14, 16) séparés fluidiquement l'un de l'autre au moins par endroits et pouvant être traversés par le gaz d'échappement. La turbine comprend également au moins une soupape (22) pouvant être réglée entre une position de fermeture fermant au moins un canal de contournement (20) et au moins une position d'ouverture libérant le canal de contournement au moins par endroits et par l'intermédiaire de laquelle la roue de turbine doit être contournée par au moins une partie du gaz d'échappement, les deux flux (14, 16) ou plus étant séparés l'un de l'autre fluidiquement au moins par endroits dans une zone de séparation (24) par la soupape (22), lorsque celle-ci se trouve dans au moins une position, la soupape (22) présentant au moins une position intermédiaire dans laquelle le canal de contournement (20) est fermé et les deux flux (14, 16) ou plus sont reliés fluidiquement l'un à l'autre dans la zone de séparation (24).
PCT/EP2010/007296 2010-02-18 2010-12-01 Turbine pour turbocompresseur à gaz d'échappement WO2011101005A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010008411.5 2010-02-18
DE102010008411.5A DE102010008411B4 (de) 2010-02-18 2010-02-18 Turbine für einen Abgasturbolader

Publications (1)

Publication Number Publication Date
WO2011101005A1 true WO2011101005A1 (fr) 2011-08-25

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WO (1) WO2011101005A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102562268A (zh) * 2011-12-28 2012-07-11 上海交通大学 涡轮入口面积可变式涡轮增压系统
US9359939B2 (en) 2013-02-20 2016-06-07 Ford Global Technologies, Llc Supercharged internal combustion engine with two-channel turbine and method
US9366177B2 (en) 2013-02-20 2016-06-14 Ford Global Technologies, Llc Supercharged internal combustion engine with two-channel turbine and method
DE102016006719A1 (de) 2016-06-01 2017-02-09 Daimler Ag Turbine für einen Abgasturbolader
DE102016006718A1 (de) 2016-06-01 2017-12-07 Daimler Ag Turbine für einen Abgasturbolader
US10006342B2 (en) 2014-02-20 2018-06-26 Ford Global Technologies, Llc Exhaust flow valve for twin-scroll turbine and operating methods thereof
DE102013223778B4 (de) 2013-02-20 2018-12-20 Ford Global Technologies, Llc Aufgeladene Brennkraftmaschine mit gruppierten Zylindern und Verfahren zum Betreiben einer derartigen Brennkraftmaschine
CN109154229A (zh) * 2016-05-12 2019-01-04 大陆汽车有限公司 用于废气涡轮增压器的带双蜗壳涡轮机壳体和具有改善流出的阀装置的涡轮机
US11028765B2 (en) 2019-02-15 2021-06-08 Borgwarner Inc. Dual volute turbocharger and system including the same
US11047294B2 (en) 2019-02-15 2021-06-29 Borgwarner Inc. Method of controlling a valve of a dual volute turbocharger
US11408333B2 (en) 2019-02-15 2022-08-09 Borgwarner Inc. Valve assembly for a dual volute turbocharger and dual volute turbocharger including the same

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
KR102036848B1 (ko) * 2012-06-21 2019-10-25 보르그워너 인코퍼레이티드 배기가스 터보차저
DE102013002894B4 (de) 2013-02-20 2018-12-20 Daimler Ag Turbine für einen Abgasturbolader
DE102015105222A1 (de) 2015-04-07 2016-10-13 Ihi Charging Systems International Gmbh Regelvorrichtung für einen Abgasführungsabschnitt eines Abgasturboladers
DE102015218335B4 (de) 2015-09-24 2022-02-03 Vitesco Technologies GmbH Turbine für einen Abgasturbolader
DE102016208162A1 (de) 2016-05-12 2017-11-16 Continental Automotive Gmbh Abgasturbolader mit einer zweiflutigen Turbine und einer drehbaren Flutenverbindung
DE102016208158A1 (de) 2016-05-12 2017-11-16 Continental Automotive Gmbh Turbine für einen Abgasturbolader mit zweiflutigem Turbinengehäuse und Ventil-Anordnung zur Flutenverbindung und Wastegate-Steuerung
DE102016208159B4 (de) 2016-05-12 2022-02-03 Vitesco Technologies GmbH Turbine für einen Abgasturbolader mit zweiflutigem Turbinengehäuse und einem Ventil zur Flutenverbindung
DE102016208163A1 (de) 2016-05-12 2017-11-16 Continental Automotive Gmbh Turbine für einen Abgasturbolader mit zweiflutigem Turbinengehäuse und einem Linearventil zur Flutenverbindung und Wastegate-Steuerung
DE202016102796U1 (de) * 2016-05-25 2016-06-07 Borgwarner Inc. Verbindungsventil für Abgasturbolader mit mehrflutigen Turbinen
DE102017108094A1 (de) 2017-04-13 2018-10-18 Ihi Charging Systems International Gmbh Einstellvorrichtung für einen Abgasführungsabschnitt eines Abgasturboladers, Abgasführungsabschnitt für einen Abgasturbolader und Abgasturbolader
DE102018000185A1 (de) * 2018-01-12 2019-07-18 Daimler Ag Turbine für einen Abgasturbolader einer Verbrennungskraftmaschine, insbesondere für ein Kraftfahrzeug

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DE102004055571A1 (de) 2004-11-18 2006-06-08 Daimlerchrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE102005002246A1 (de) * 2005-01-18 2006-07-20 Daimlerchrysler Ag Brennkraftmaschine mit einer Abgasrückführungseinrichtung und Verfahren zum Betrieb einer Brennkraftmaschine
WO2008028666A1 (fr) * 2006-09-08 2008-03-13 Borgwarner Inc. Procédé et dispositif d'exploitation d'un moteur à combustion interne
WO2008157109A2 (fr) * 2007-06-12 2008-12-24 Borgwarner Inc. Système de soupape de dérivation d'un turbocompresseur
DE102007060415A1 (de) * 2007-12-14 2009-06-18 Daimler Ag Brennkraftmaschine und Verfahren zum Steuern einer Brennkraftmaschine für ein Kraftfahrzeug

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US3423926A (en) * 1966-08-31 1969-01-28 Garrett Corp Turbocharger control arrangement

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
DE102004055571A1 (de) 2004-11-18 2006-06-08 Daimlerchrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE102005002246A1 (de) * 2005-01-18 2006-07-20 Daimlerchrysler Ag Brennkraftmaschine mit einer Abgasrückführungseinrichtung und Verfahren zum Betrieb einer Brennkraftmaschine
WO2008028666A1 (fr) * 2006-09-08 2008-03-13 Borgwarner Inc. Procédé et dispositif d'exploitation d'un moteur à combustion interne
WO2008157109A2 (fr) * 2007-06-12 2008-12-24 Borgwarner Inc. Système de soupape de dérivation d'un turbocompresseur
DE102007060415A1 (de) * 2007-12-14 2009-06-18 Daimler Ag Brennkraftmaschine und Verfahren zum Steuern einer Brennkraftmaschine für ein Kraftfahrzeug

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102562268A (zh) * 2011-12-28 2012-07-11 上海交通大学 涡轮入口面积可变式涡轮增压系统
US9359939B2 (en) 2013-02-20 2016-06-07 Ford Global Technologies, Llc Supercharged internal combustion engine with two-channel turbine and method
US9366177B2 (en) 2013-02-20 2016-06-14 Ford Global Technologies, Llc Supercharged internal combustion engine with two-channel turbine and method
DE102013223778B4 (de) 2013-02-20 2018-12-20 Ford Global Technologies, Llc Aufgeladene Brennkraftmaschine mit gruppierten Zylindern und Verfahren zum Betreiben einer derartigen Brennkraftmaschine
US10006342B2 (en) 2014-02-20 2018-06-26 Ford Global Technologies, Llc Exhaust flow valve for twin-scroll turbine and operating methods thereof
US10767554B2 (en) 2016-05-12 2020-09-08 Continental Automotive Gmbh Turbine for an exhaust gas turbocharger with a two-volute turbine housing and a valve arrangement having improved outflow
CN109154229A (zh) * 2016-05-12 2019-01-04 大陆汽车有限公司 用于废气涡轮增压器的带双蜗壳涡轮机壳体和具有改善流出的阀装置的涡轮机
CN109154229B (zh) * 2016-05-12 2021-01-15 大陆汽车有限公司 用于废气涡轮增压器的涡轮机
WO2017207081A1 (fr) 2016-06-01 2017-12-07 Daimler Ag Turbine pour un turbocompresseur à gaz d'échappement
DE102016006718A1 (de) 2016-06-01 2017-12-07 Daimler Ag Turbine für einen Abgasturbolader
DE102016006719A1 (de) 2016-06-01 2017-02-09 Daimler Ag Turbine für einen Abgasturbolader
US11028765B2 (en) 2019-02-15 2021-06-08 Borgwarner Inc. Dual volute turbocharger and system including the same
US11047294B2 (en) 2019-02-15 2021-06-29 Borgwarner Inc. Method of controlling a valve of a dual volute turbocharger
US11408333B2 (en) 2019-02-15 2022-08-09 Borgwarner Inc. Valve assembly for a dual volute turbocharger and dual volute turbocharger including the same

Also Published As

Publication number Publication date
DE102010008411A1 (de) 2011-08-18
DE102010008411B4 (de) 2019-03-21

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