WO2005061870A1 - Moteur a combustion interne avec turbocompresseur a gaz d'echappement et reaspiration des gaz d'echappement - Google Patents

Moteur a combustion interne avec turbocompresseur a gaz d'echappement et reaspiration des gaz d'echappement Download PDF

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Publication number
WO2005061870A1
WO2005061870A1 PCT/EP2004/012833 EP2004012833W WO2005061870A1 WO 2005061870 A1 WO2005061870 A1 WO 2005061870A1 EP 2004012833 W EP2004012833 W EP 2004012833W WO 2005061870 A1 WO2005061870 A1 WO 2005061870A1
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WO
WIPO (PCT)
Prior art keywords
exhaust gas
combustion engine
internal combustion
control element
flow
Prior art date
Application number
PCT/EP2004/012833
Other languages
German (de)
English (en)
Inventor
Alfred KÜSPERT
Original Assignee
Daimlerchrysler 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 Daimlerchrysler Ag filed Critical Daimlerchrysler Ag
Publication of WO2005061870A1 publication Critical patent/WO2005061870A1/fr

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Classifications

    • 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
    • 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
    • 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • 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
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • 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 an internal combustion engine with an exhaust gas turbocharger and exhaust gas recirculation according to the preamble of claim 1.
  • An exhaust gas turbocharger is already known (DE 199 24 228 C2), the turbine housing of which has a double flow.
  • the regulation of the exhaust gas supply to a turbine wheel of the exhaust gas turbine takes place via an axial slide, which can completely cover one of the floods, so that the exhaust gas supply takes place via an upstream flood connection via a single flood to the turbine wheel.
  • Such control of the amount of exhaust gas is common in the non-fired operating range of the internal combustion engine, in which the internal combustion engine is intended to act as an engine brake (turbobrake).
  • the relatively small amount of exhaust gas in the engine braking mode is fed to the turbine wheel via the smaller flood, which is dimensioned correspondingly to the lower exhaust gas flow with its inlet cross section, so that a relatively high speed of the turbine wheel and a compressor connected to the turbine wheel via a shaft can be maintained.
  • the relatively high speed of the compressor wheel also results in engine braking Compression of the intake air and thus the corresponding engine braking power.
  • variable turbine geometry instead of the aforementioned slide valve solution, for example in the form of an adjustable, radial guide vane, which then blocks off a flood if necessary. It is also possible to provide the slide with a rigid guide grille, which is then introduced into the exhaust gas flood.
  • the provision of the variable turbine geometry and a slider is complex and also requires installation space.
  • the internal combustion engine according to the invention with exhaust gas turbocharger and exhaust gas recirculation with the characterizing features of claim 1 has the advantage that the turbocharger can be easily adapted to the various operating states of the internal combustion engine, in particular in exhaust gas recirculation operation and in engine braking operation, with the use of variable or rigid Guide vanes in front of the turbine or a slide in the turbine housing can be dispensed with.
  • good regulation of the flow to the turbine is possible, in which the build-up behavior on the exhaust gas turbine can be better adapted to the respective operating point.
  • the exhaust gas recirculation is provided for returning exhaust gas from the exhaust system into the intake tract, in which, depending on the state variables and operating parameters of the internal combustion engine, the amount of the recirculated exhaust gas mass flow can be set in a simple manner. It is advantageous that a first control element and a second control element can be used to very variably achieve a desired back pressure on the turbine, as a result of which the exhaust gas recirculation rate can be adjusted well in addition to the engine braking power.
  • the drawing shows a schematically simplified representation of an internal combustion engine 1, which is a diesel engine with an engine brake, in particular for use in commercial vehicles. In principle, however, the invention can also be applied to gasoline engines.
  • the internal combustion engine 1 has an exhaust gas turbocharger 2 with a turbine 3 in the exhaust line 4.
  • the turbine 3 has a turbine wheel 5, which is designed as a radial turbine and transmits the movement of the turbine wheel 5 via a shaft 7 to a compressor wheel 8 of a compressor 9.
  • the turbine 3 has a turbine housing which is designed with two passages 14, 15 or inflow channels 16, 17.
  • the two floods 14, 15 and inflow channels 16, 17 are separated from one another by a partition 18 of the turbine housing which is fixed to the housing.
  • the exhaust gas can be fed separately to the turbine wheel 5 via each flood 14, 15 or inflow channel 16, 17.
  • the exhaust gas supply takes place via the exhaust line 4, which is divided into two exhaust gas lines which are formed independently of one another, a first exhaust gas line 20 and a second exhaust gas line 21.
  • the first exhaust line 20 is assigned to the first flood 14 and the second exhaust line 21 is assigned to the second flood 15.
  • Each exhaust line 20, 21 is assigned to a defined number of cylinder outlets of the internal combustion engine.
  • the internal combustion engine 1 has six cylinders, a first cylinder bank 23, three cylinders and a second cylinder bank 24, likewise having three cylinders. In addition to the uniform division of the cylinder banks, a non-uniform one is also conceivable.
  • the first exhaust pipe 20 leads from the cylinder bank 23 assigned here to the first inflow duct 16 of the first flood 14.
  • the second Exhaust line 21 leads from the assigned second cylinder bank 24 to the second inflow channel 17 of the second flood 15.
  • a bypass line 25 connecting both exhaust gas lines 20, 21 is provided between the two exhaust gas lines 20, 21 upstream of the turbine 3.
  • a first control element 30, which can control the exhaust gas flow in the bypass line 25, is accommodated in the bypass line 25.
  • the first control element 30 is designed, for example, as a valve controlling the flow or as an adjustable throttle element or flap.
  • a second control element 31 is accommodated in the second exhaust gas line 21 upstream of the turbine 3 and downstream of an inlet point 26 to the bypass line 25, which also acts as a flow controlling valve or as a throttle element or Flap is formed.
  • an exhaust gas flow from the second cylinder bank 24 to the second flood 15 is possible.
  • the charge air cooler 37 Downstream of the compressor 9, the charge air cooler 37, through which the compressed air flows, is arranged in the intake tract 6. After leaving the charge air cooler 37, the air has the boost pressure p2S, with which it is optionally introduced with mixed exhaust gas from the bypass line 25 into the cylinder inlet of the internal combustion engine 1.
  • the exhaust gas back pressure p31 prevails from the cylinder outlet in the first exhaust line 20, which is assigned to the first cylinder bank 23; Exhaust gas back pressure p32 is present in second exhaust line 21, which is assigned to second cylinder bank 24. In the turbine 3, the exhaust gas is expanded to the low pressure p4 and finally blown off into the environment in the further course.
  • the second, larger flood 15 is dimensioned or designed so that a desired boost pressure can be achieved in fired operation.
  • the first, smaller flood 14 is dimensioned or designed in such a way that a required exhaust gas recirculation rate can be achieved, a certain engine braking power being guaranteed in engine braking operation.
  • the ratio of the inlet cross-section or Haisqueriteses of the first flood 14 per 1 1 stroke volume of the internal combustion engine 1 should be in a range of
  • the third control element 32 of the exhaust gas recirculation is set to an open position so that exhaust gas can primarily flow from the first exhaust line 20 into the intake tract 6.
  • the second control element 31 of the second exhaust gas line 21 is also set to an open position.
  • the pressure in the first exhaust line 20 p31 is greater than the pressure in the second exhaust line 21 p32.
  • the first control element 30 can therefore be used to vary the recirculation rate for the exhaust gas recirculation.
  • a maximum exhaust gas recirculation rate can thus be achieved in the closed position of the first control element 30 since p31 then has its maximum value.
  • a corresponding exhaust gas recirculation rate can be set by correspondingly varying the position of the first control element 30 or the flow in the bypass line 25.
  • the first control element 30 is brought permanently into an open position, so that a flow can take place in the bypass line 25.
  • the second control 31 in the second Exhaust line 21 is provided in order to be able to variably change its position or the flow in the second exhaust line 21.
  • the third control element 32 is permanently in its closed position during engine braking, so that there is no exhaust gas recirculation.
  • variable second control element 31 In the closed position of the variable second control element 31, no exhaust gas can reach the turbine wheel 5 through the second flood 15. The total amount of exhaust gas must therefore flow through the small tide 14 to the turbine wheel 5, which results in a high speed of the turbine wheel 5 or the connected compressor wheel 8 due to the maximum exhaust gas pressure p31, which results in a maximum boost pressure of the compressor 9 and thus maximum braking power in engine braking mode.
  • the braking power can be varied or adjusted accordingly in a simple manner.
  • the closed position of the second control element 31 it is thus possible to achieve very high engine braking powers by greatly increasing the exhaust gas back pressure p31 without exceeding the critical speed limit of the exhaust gas turbocharger 2. It is advantageous here that the first control element 30 and the second control element 31 can be used to very variably achieve a desired back pressure p31 on the feed turbine 3, as a result of which the engine braking power can be adjusted well.
  • first control valve 30 and the second control valve 31 and, if appropriate, also the third control valve 32 can be in a common housing for further optimization of the installation space be housed.
  • a corresponding constructive solution in the form of a multifunctional valve or throttle element is also conceivable.
  • All control elements 30, 31, 32 can be adjusted to their desired position by means of control signals that can be generated in a regulating and control device (not shown), for example an electronic engine control unit, in order to enable the flow rate to be controlled.
  • a regulating and control device for example an electronic engine control unit

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'objet de la présente invention concerne un moteur à combustion interne (1) avec turbocompresseur (2) à gaz d'échappement à construction simplifiée et commande améliorée. A cet effet, ledit compresseur comporte une turbine (3) à gaz d'échappement qui possède deux passages d'écoulement séparés (14, 15) à section transversale différente raccordés chacun à un collecteur (20; 21) d'échappement, une conduite de réaspiration (35) des gaz d'échappement conduisant du plus petit (14) des passages d'écoulement à une conduite d'aspiration (6) du moteur à combustion interne (1) pour la réaspiration des gaz d'échappement. Un premier élément de commande (30) destiné à commander le débit est situé dans une conduite de pontage (25) reliant les deux collecteurs d'échappement (20, 21) en amont des passages d'écoulement (14, 15) et un second élément de commande (31) destiné à commander le débit est situé dans le second collecteur d'échappement (21) associé au plus gros (15) des passages d'écoulement. Ces deux éléments de commande (30, 31) permettent de soumettre les deux passages séparés (14, 15) à l'effet des gaz d'échappement pour l'adaptation à divers états de fonctionnement du moteur à combustion interne (1).
PCT/EP2004/012833 2003-12-11 2004-11-12 Moteur a combustion interne avec turbocompresseur a gaz d'echappement et reaspiration des gaz d'echappement WO2005061870A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10357925.7 2003-12-11
DE10357925A DE10357925A1 (de) 2003-12-11 2003-12-11 Brennkraftmaschine mit Abgasturbolader und Abgasrückführung

Publications (1)

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WO2005061870A1 true WO2005061870A1 (fr) 2005-07-07

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DE (1) DE10357925A1 (fr)
WO (1) WO2005061870A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009018887A1 (fr) * 2007-08-04 2009-02-12 Daimler Ag Turbocompresseur à gaz d'échappement pour un moteur à combustion interne à pistons alternatifs
WO2009037120A2 (fr) * 2007-09-13 2009-03-26 Avl List Gmbh Procédé de régulation de la puissance de refroidissement d'un système de refroidissement d'un moteur à combustion interne
FR2945579A1 (fr) * 2009-05-15 2010-11-19 Inst Francais Du Petrole Procede et dispositif de controle de la quantite de gaz d'echappement recircules a l'admission d'un moteur a combustion interne suralimente
EP2295769A1 (fr) * 2009-08-14 2011-03-16 International Engine Intellectual Property Company, LLC. Système d'échappement pour frein de moteur
EP2154352A3 (fr) * 2008-08-12 2014-03-19 MAN Truck & Bus AG Procédé et dispositif destinés au fonctionnement d'un moteur à combustion interne multi-cylindrique
DE102013005885A1 (de) 2013-04-06 2014-10-09 Daimler Ag Turbine für einen Abgasturbolader
WO2018073608A1 (fr) * 2016-10-21 2018-04-26 Cummins Ltd Procédé de conception d'une turbine
CN108869109A (zh) * 2018-07-27 2018-11-23 湖南天雁机械有限责任公司 调节废气流量的集成控制阀
CN108894871A (zh) * 2018-06-26 2018-11-27 清华大学 一种带有双egr通道的非对称涡轮增压内燃机系统
US10215136B2 (en) 2014-08-26 2019-02-26 Borgwarner Inc. Adjustable, low loss valve for providing high pressure loop exhaust gas recirculation
US10301952B2 (en) 2014-05-19 2019-05-28 Borgwarner Inc. Dual volute turbocharger to optimize pulse energy separation for fuel economy and EGR utilization via asymmetric dual volutes
AT523038B1 (de) * 2019-12-06 2021-05-15 Avl List Gmbh Brennkraftmaschine

Families Citing this family (10)

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Publication number Priority date Publication date Assignee Title
DE102006009298A1 (de) 2006-03-01 2007-09-06 Daimlerchrysler Ag Brennkraftmaschine mit einem Abgasturbolader
DE112007001400A5 (de) 2006-06-21 2009-05-20 Daimler Ag Abgaskrümmer
DE102007025437A1 (de) 2007-05-31 2008-12-04 Daimler Ag Verfahren für eine Brennkraftmaschine mit einem Abgasturbolader
AT503869B1 (de) * 2007-09-27 2009-06-15 Avl List Gmbh Brennkraftmaschine mit einem mehrflutigen abgasturbolader
DE102007053778B4 (de) * 2007-11-12 2017-12-07 Ford Global Technologies, Llc Abgasrückführung bei einem Verbrennungsmotor mit zwei Turboladern
DE102009004417A1 (de) 2009-01-13 2010-07-15 Man Nutzfahrzeuge Aktiengesellschaft Verfahren zur Nachbehandlung eines Abgasstroms einer mehrzylindrigen Brennkraftmaschine eines Fahrzeuges sowie Abgasnachbehandlungsvorrichtung
DE102009004418A1 (de) 2009-01-13 2010-07-15 Man Nutzfahrzeuge Ag Verfahren zur Nachbehandlung eines Abgasstroms einer mehrzylindrigen Brennkraftmaschine eines Fahrzeuges sowie Abgasnachbehandlungsvorrichtung
DE102011115206A1 (de) * 2011-09-28 2013-03-28 Daimler Ag Abgasturbolader für eine Brennkraftmaschine
DE102012014189A1 (de) 2012-07-18 2014-01-23 Mtu Friedrichshafen Gmbh Brennkraftmaschine mit Abgasturbolader
DE102013020448A1 (de) * 2013-12-07 2015-06-11 Daimler Ag Verfahren zum Betreiben eines Kraftwagens

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DE10048237A1 (de) * 2000-09-29 2002-04-11 Daimler Chrysler Ag Abgasturbolader, aufgeladene Brennkraftmaschine und Verfahren hierzu
US20030154717A1 (en) * 2001-10-25 2003-08-21 Daimlerchrysler Ag Internal combustion engine with an exhaust turbocharger and an exhaust-gas recirculation device

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DE19924228C2 (de) 1999-05-27 2002-01-10 3K Warner Turbosystems Gmbh Mehrflutiger, regelbarer Abgasturbolader
DE10048237A1 (de) * 2000-09-29 2002-04-11 Daimler Chrysler Ag Abgasturbolader, aufgeladene Brennkraftmaschine und Verfahren hierzu
US20030154717A1 (en) * 2001-10-25 2003-08-21 Daimlerchrysler Ag Internal combustion engine with an exhaust turbocharger and an exhaust-gas recirculation device

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009018887A1 (fr) * 2007-08-04 2009-02-12 Daimler Ag Turbocompresseur à gaz d'échappement pour un moteur à combustion interne à pistons alternatifs
WO2009037120A2 (fr) * 2007-09-13 2009-03-26 Avl List Gmbh Procédé de régulation de la puissance de refroidissement d'un système de refroidissement d'un moteur à combustion interne
WO2009037120A3 (fr) * 2007-09-13 2009-05-07 Avl List Gmbh Procédé de régulation de la puissance de refroidissement d'un système de refroidissement d'un moteur à combustion interne
EP2154352A3 (fr) * 2008-08-12 2014-03-19 MAN Truck & Bus AG Procédé et dispositif destinés au fonctionnement d'un moteur à combustion interne multi-cylindrique
FR2945579A1 (fr) * 2009-05-15 2010-11-19 Inst Francais Du Petrole Procede et dispositif de controle de la quantite de gaz d'echappement recircules a l'admission d'un moteur a combustion interne suralimente
EP2295769A1 (fr) * 2009-08-14 2011-03-16 International Engine Intellectual Property Company, LLC. Système d'échappement pour frein de moteur
DE102013005885A1 (de) 2013-04-06 2014-10-09 Daimler Ag Turbine für einen Abgasturbolader
US10301952B2 (en) 2014-05-19 2019-05-28 Borgwarner Inc. Dual volute turbocharger to optimize pulse energy separation for fuel economy and EGR utilization via asymmetric dual volutes
US10215136B2 (en) 2014-08-26 2019-02-26 Borgwarner Inc. Adjustable, low loss valve for providing high pressure loop exhaust gas recirculation
WO2018073608A1 (fr) * 2016-10-21 2018-04-26 Cummins Ltd Procédé de conception d'une turbine
CN110100084A (zh) * 2016-10-21 2019-08-06 康明斯有限公司 设计涡轮机的方法
GB2571653A (en) * 2016-10-21 2019-09-04 Cummins Ltd Method of design of a turbine
CN110100084B (zh) * 2016-10-21 2021-06-08 康明斯有限公司 设计涡轮机的方法
GB2571653B (en) * 2016-10-21 2022-01-26 Cummins Ltd Method of design of a turbine
CN108894871A (zh) * 2018-06-26 2018-11-27 清华大学 一种带有双egr通道的非对称涡轮增压内燃机系统
CN108869109A (zh) * 2018-07-27 2018-11-23 湖南天雁机械有限责任公司 调节废气流量的集成控制阀
CN108869109B (zh) * 2018-07-27 2023-04-07 湖南天雁机械有限责任公司 调节废气流量的集成控制阀
AT523038B1 (de) * 2019-12-06 2021-05-15 Avl List Gmbh Brennkraftmaschine
AT523038A4 (de) * 2019-12-06 2021-05-15 Avl List Gmbh Brennkraftmaschine
EP3832085A1 (fr) * 2019-12-06 2021-06-09 AVL List GmbH Moteur à combustion interne

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