EP2576989B1 - Turbine pour un turbocompresseur d'échappement - Google Patents

Turbine pour un turbocompresseur d'échappement Download PDF

Info

Publication number
EP2576989B1
EP2576989B1 EP11716836.9A EP11716836A EP2576989B1 EP 2576989 B1 EP2576989 B1 EP 2576989B1 EP 11716836 A EP11716836 A EP 11716836A EP 2576989 B1 EP2576989 B1 EP 2576989B1
Authority
EP
European Patent Office
Prior art keywords
turbine
exhaust gas
housing part
spiral
internal combustion
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.)
Active
Application number
EP11716836.9A
Other languages
German (de)
English (en)
Other versions
EP2576989A2 (fr
Inventor
Siegfried Sumser
Torsten Hirth
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.)
Mercedes Benz Group AG
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 EP2576989A2 publication Critical patent/EP2576989A2/fr
Application granted granted Critical
Publication of EP2576989B1 publication Critical patent/EP2576989B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F01D17/14—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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the invention relates to a turbine for an exhaust gas turbocharger of the type indicated in the preamble of patent claim 1.
  • An internal combustion engine for a motor vehicle comprising an exhaust gas turbocharger, which comprises a compressor in an intake tract of the internal combustion engine and a turbine in an exhaust gas tract of the internal combustion engine, wherein the turbine comprises a turbine housing which comprises a spiral duct coupled to an exhaust pipe of the exhaust gas system and a turbine wheel which is arranged within a receiving space of the turbine housing and for driving a non-rotatably connected to the turbine wheel compressor wheel of the compressor can be acted upon by the spiral duct feasible exhaust gas of the internal combustion engine.
  • the turbine comprises an adjusting device, by means of which a spiral inlet cross section of the spiral channel and a nozzle cross section of the spiral channel to the receiving space are jointly adjustable.
  • a turbine according to the invention for an exhaust gas turbocharger of an internal combustion engine comprising at least two spiral channels which can flow through exhaust gas of the internal combustion engine and have respective spiral inlet cross sections, is characterized in that the housing part is common in at least one further housing part in one of the spiral channels Turbine formed receiving space is received, which exhaust gas of the internal combustion engine via the respective spiral inlet cross-sections can be flowed into the spiral channels.
  • an inlet pressure level of the turbine is optionally increased by the back pressure of an exhaust gas purification device, in particular a soot filter, which is arranged in the flow direction of the exhaust gas downstream of the turbine, which requires a further reduction of the turbine in size or dimensions.
  • an exhaust gas purification device in particular a soot filter
  • This is accompanied by the problem that such a reduction of the turbine is usually accompanied by a deterioration of the efficiency of the turbine.
  • the turbine according to the invention makes it possible to make it small in terms of its dimensions or dimensions in order to represent a desired Aufstau . This allows high EGR rates. In other words, a particularly large amount of exhaust gas can be recirculated from an exhaust side of the internal combustion engine to an air side thereof and supplied to an air sucked by the internal combustion engine, whereby the emissions, in particular nitrogen oxide and soot emissions, of the internal combustion engine can be lowered.
  • the described, high power requirement on the compressor side of the exhaust gas turbocharger through the turbine is satisfactory because it allows a congestion charging operation of their associated internal combustion engine.
  • the receiving space formed by the further housing part acts as a collecting space in which the exhaust gas of the internal combustion engine is first collected and dammed before it flows through the spiral channels and drives the turbine wheel, which in turn via a shaft with which it is rotatably connected, a compressor wheel can drive on the compressor side of the exhaust gas turbocharger.
  • the turbine has a low number of parts, which is associated with low cost and with a high operating reliability of the turbine.
  • the spiral channels each have at least one nozzle cross-section via which the turbine wheel of the turbine accommodated in the first housing part can be acted upon with exhaust gas, the nozzle cross-sections being juxtaposed along the axis of rotation of the turbine wheel and / or about the axis of rotation over a circumference of the turbine Turbine are distributed.
  • the turbine can be adapted to different requirements to satisfy the requirements for the representations of a desired Heillander air exhaust gas supply and low emissions of the internal combustion engine.
  • the turbine comprises an adjusting device by means of which the respective spiral inlet cross sections and / or the respective nozzle cross sections of the spiral channels are adjustable, wherein, for example, the spiral inlet cross section and the nozzle cross section of one of the spiral channels are adjustable together by means of the adjusting device and / or wherein the spiral inlet cross section and the nozzle cross section of the other Spiral channels are adjustable together by means of the adjustment, the turbine is at different operating points at least almost in the whole Characteristic map of the internal combustion engine adaptable both in low and medium load ranges as well as in full load ranges.
  • the adjusting device also allows an adjustment of the Aufstau s the turbine, whereby an air and exhaust gas recirculation demand for the satisfaction of consumption and emission requirements in a particularly wide range can be influenced.
  • the turbine is advantageous in particular in the context of an application in a passenger car, wherein the internal combustion engine has a transient behavior. Due to the variable Aufstauhot the turbine despite the transient behavior of the internal combustion engine during a drive of the passenger car acceptable driving behavior can be displayed, and that also in internal combustion engines, which have according to the downsizing concept only a small displacement and high specific power.
  • the adjusting device comprises, for example, each spiral channel at least one Versperranalysis, by means of which the spiral inlet cross section and / or the nozzle cross section is adjustable, wherein the Versperranalysis is formed tongue-shaped.
  • the turbine is thus designed as a so-called tongue slider segment turbine, which has a small number of parts and a pairing of the flow-relevant spiral channels with a cost-effective and robust turbine housing conception.
  • the first housing has more than the described two spiral channels and thus more than two spiral segments.
  • the spiral channels which are also referred to as multi-segment spirals are shown in the turbine through the first housing part and thus separated from the second housing part, for example, by a precise manufacturing process and with the second housing part, which acts as a collection housing and includes the Mehrsegmentspiralen and is designed gas-tight environment , connected.
  • the second housing part, the receiving space is formed, for example helically, in addition to a gas-tight flow environment of the exhaust gas of the internal combustion engine to the spiral inlet cross sections of the spiral channels and a support function of the turbine or the entire exhaust gas turbocharger together with a protection against bursting protection of a turbine rotor, which the turbine wheel, the shaft, the compressor of the compressor of the exhaust gas turbocharger and optionally further components.
  • the first, the spiral channels forming housing part and / or the or the Verperrharm the adjustment is or are for example by a casting process, in particular a precision casting, manufactured and / or sheet metal parts with advantageously very smooth flow surfaces, which is a very precise adjustment of the spiral channels and optionally of the or the locking body allows.
  • the second housing part surrounding the first housing part optionally has a relatively simple geometry, so that it is produced inexpensively by a relatively rough standard sand casting method. This keeps the cost of the turbine according to the invention low.
  • the connection of the two housing parts takes place for example by means of a cost-effective assembly, joining and / or sealing technique, wherein it is also possible that the first housing part is cast into the second housing part.
  • a pairing of the second housing part having the receiving space and the first housing part having the spiral channels by means of the turbine according to the invention leads to the second housing part and a plurality of different second housing parts being insert parts which, for example, two, three, four, five, six have seven or more spiral channels in conjunction with adapted adjustment, an advantageous kit for generating a diverse turbine behavior is created.
  • This kit then provides an adapted thermodynamic behavior of the turbine in a wide range of internal combustion engine applications that can be operated with efficient combinations and turbine simplification.
  • the second housing part can be used as a common part, which thus keeps the cost of the modular system low.
  • the Fig. 1 shows an internal combustion engine 10 with six cylinders 12.
  • the air is compressed by the compressor 20 by means of a compressor wheel 24, whereby the air is heated.
  • To cool the thus compressed and heated air it continues to flow according to directional arrows 26 to a charge air cooler 28 and further according direction arrows 30 to an air collector 32, via which it is supplied to the cylinders 12 according to directional arrows 34.
  • the sucked and compressed air is supplied with fuel and burned, resulting in a rotation of a crankshaft 36 of the internal combustion engine 10 according to a directional arrow 38 results.
  • the compressor 20 arranged on an air side 40 of the internal combustion engine 10 serves to provide a desired air supply to the internal combustion engine 10 for displaying a desired power or torque level of the internal combustion engine 10.
  • the internal combustion engine 10 can be designed small in terms of its stroke volume and thus in terms of its dimensions, which is associated with a low weight, high specific power, low fuel consumption and thus low CO 2 emissions.
  • An exhaust gas of the internal combustion engine 10 resulting from the combustion in the cylinders 12 is first guided by means of exhaust casings 42 on an exhaust side 44 of the internal combustion engine to an exhaust gas recirculation device 45, by means of which exhaust gas of the internal combustion engine 10 can be traced from the exhaust side 44 to the air side 40.
  • the exhaust gas recirculation device 45 comprises an exhaust gas recirculation valve 46, by means of which a certain amount of recirculated exhaust gas, which is tuned to a present operating point of the internal combustion engine 10, can be set.
  • the exhaust gas flows according to a directional arrow 52 to an exhaust gas recirculation cooler 50, by which the exhaust gas is cooled before it is supplied according to a direction arrow 48 of the sucked from the internal combustion engine 10 air.
  • This admission of the intake air with the recirculated exhaust gas leads to a reduction of emissions, in particular of nitrogen oxide and particulate emissions, of the internal combustion engine 10, as a result of which it not only has low fuel consumption, high performance but also low emissions.
  • the exhaust gas is feasible by means of the exhaust piping 42 to a turbine 54 of the exhaust gas turbocharger 22, wherein the turbine 54 is formed as a single-flow, so-called tongue slide multi-segment turbine, which in connection with the Fig. 2 is explained.
  • the turbine 54 comprises a first housing part 56 which has three spiral channels 58 through which exhaust gas from the internal combustion engine 10 can flow.
  • the spiral channels 58 have respective spiral inlet cross sections A S and respective nozzle cross sections A R.
  • a turbine wheel 60 of the turbine 54 is rotatably received.
  • the exhaust gas of the internal combustion engine 10 now enters via the respective spiral inlet cross sections A S in the spiral channels 58 and flows through the respective nozzle cross sections A R, the turbine 60, whereby the turbine wheel 60 is driven by the exhaust gas and rotates.
  • the turbine wheel 60 is connected to a shaft 62 of the exhaust gas turbocharger 22, with which the compressor wheel 24 is non-rotatably connected, whereby the compressor wheel 24 is driven by the turbine wheel 60 via the shaft 62.
  • the shaft 62 has an axis of rotation 63.
  • the turbine 54 also includes an adjusting device 64, which in turn comprises an adjusting ring 66 which is connected to three locking bodies in the form of tongue slides 68, of which each tongue slide 68 is associated with a spiral channel 58.
  • the adjusting ring 66 is according to directional arrows 70 about the axis of rotation 63 of Turbine wheel 60 rotatable, whereby the spiral inlet cross sections A S and the circumferentially of the turbine wheel 60 distributed uniformly over its circumference arranged nozzle cross sections A R are adjustable.
  • the turbine 54 By the spiral channels 58, through which a plurality of segments of the turbine 54 are formed, a shock charging operation of the internal combustion engine 10 is initially possible.
  • the turbine 54 now includes a further housing part 72, through which a gas-tight closed by the other housing part 72 to the environment and the spiral channels 58 common receiving space 74 is formed, in which the first housing part 56 is received the further housing part 72 may surround the first housing part 56 on the side of a bearing device and thus on a side facing the compressor wheel 24 and / or on a side opposite this side, ie on the side of a turbine outlet.
  • the further housing part 72 has an inflow channel 76, in which exhaust gas can flow in via the exhaust piping 42 in accordance with a directional arrow 78 and which passes the exhaust gas further into the receiving space 74.
  • the inflow channel 76 tapers in the flow direction of the exhaust gas according to the direction arrow 78.
  • the introduced via the inlet channel 76 into the receiving space 74 exhaust gas is first collected in the receiving space 74 and can flow through the spiral channels 58 to the turbine wheel 60. A mixture and a collection of the exhaust gas takes place in the flow direction of the exhaust gas through the exhaust piping 42 upstream of the first housing part 56th
  • the spiral channels 58 each have an at least substantially trumpet-shaped inlet channel 80, via which the exhaust gas can enter the spiral channels 58.
  • the turbine 54 has a high variability, resulting in different Aufstau and thus different EGR rates can be displayed. Likewise, this allows the representation of a specific air supply of the internal combustion engine 10 to satisfy high bathogenic torque requirements. Furthermore, the turbine 54 has a low number of parts, which is associated with low cost and high reliability.
  • twin-flow turbines analogous to the design of the turbine 54, wherein then along the axis of rotation 63 of the turbine 60 next to the first housing part 56, an additional housing part with at least two spiral channels, for example in the form of the first housing part 56, is arranged is received in an additional, formed by the additional housing part according to the further housing part 72 additional receiving space according to the receiving space 74.
  • the receiving spaces are then arranged in parallel and separated from each other gas-tight.
  • two parallel-connected housing parts 56 are provided, each having a certain stowage effect and cause a certain surge charging the two gas-tight collecting chambers with separate cylinder groups of the cylinder 12 of the internal combustion engine 10, for example by means of a Krümmerteils, whereby with a two-sided adjustment according to the adjustment 64th and corresponding tongue slider 68 a variable, quasi double-flow impact turbine is shown, which can also bring an asymmetric Aufstau , depending on the application, with it.
  • the adjusting device 64 of the turbine 54 is controlled or regulated by a control device 82 of the internal combustion engine 10, which adjusts the adjusting device 64 in order to adapt the turbine 54 to a currently existing operating point of the internal combustion engine 10.
  • the exhaust gas flows through the turbine outlet according to a direction arrow 88 from the turbine 54 and flows through an exhaust aftertreatment device 90, which for example comprises a catalyst, in particular a nitrogen oxide catalyst, and optionally a particulate filter, after which the exhaust gas according to a Directional arrow 92 purified to the environment.
  • an exhaust aftertreatment device 90 which for example comprises a catalyst, in particular a nitrogen oxide catalyst, and optionally a particulate filter, after which the exhaust gas according to a Directional arrow 92 purified to the environment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Claims (10)

  1. Turbine pour un turbocompresseur à gaz d'échappement (22) d'un moteur à combustion interne (10), comportant au moins une partie de carter (56) comprenant au moins deux canaux en spirale (58) pouvant être traversés par des gaz d'échappement du moteur à combustion interne (10) et présentant des sections respectives d'entrée en spirale (As), caractérisée en ce que la partie de carter (58) étant réceptionnée dans un espace de logement (74) commun aux canaux en spirale (58) et formé par au moins une autre partie de carter (72) de la turbine (54), espace à partir duquel des gaz d'échappement du moteur à combustion interne (10) peuvent entrer dans les canaux en spirale (58) par les sections respectives d'entrée en spirale (As).
  2. Turbine selon la revendication 1, caractérisée en ce que les canaux en spirale (58) présentent respectivement au moins une section de tuyère (AR), par laquelle une roue de turbine (60) de la turbine (54) réceptionnée dans la première partie de carter (56) peut être alimentée en gaz d'échappement, les sections de tuyère (AR) étant disposées le long d'un axe de rotation (62) de la roue de turbine (60) adjacentes les unes aux autres et/ou étant réparties autour de l'axe de rotation (62) sur une circonférence de la roue de turbine (60).
  3. Turbine selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que la turbine (54) comprend un dispositif de réglage (64), qui permet de régler les sections d'entrée en spirale (64) respectives et/ou les sections de tuyère (AR) respectives des canaux en spirale (58).
  4. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'un des canaux en spirale (58) et/ou l'au moins un autre canal en spirale parmi les canaux en spirale (58) sont conçus en tant que canal en spirale complet, en particulier présentant un angle de contact supérieur à 350 degrés, et/ou en tant que canal en spiral partiel, en particulier présentant un angle de contact dans une plage comprise entre 350 degrés inclus et 30 degrés inclus.
  5. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que la première partie de carter (56) comprenant les canaux en spirale (58) est conçue selon un procédé de moulage à modèle perdu et/ou en tant qu'élément de tôle.
  6. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'autre partie de carter (72) formant l'espace de réception (74) est conçue selon un procédé de coulage en sable.
  7. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que la première partie de carter (72) est moulée dans l'autre partie de carter (72).
  8. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'autre partie de carter (72) présente un canal d'admission (76) par lequel les gaz d'échappement du moteur à combustion interne (10) peuvent entrer dans l'espace de réception (74).
  9. Turbine selon la revendication 8, caractérisée en ce que le canal d'admission (76) présente dans la direction d'écoulement (78) des gaz d'échappement vers l'espace de réception (74) une section d'écoulement qui se modifie, en particulier qui se rétrécit.
  10. Turbine selon l'une quelconque des revendications précédentes, caractérisée en ce que l'espace de réception (74) est hélicoïdal.
EP11716836.9A 2010-05-28 2011-04-20 Turbine pour un turbocompresseur d'échappement Active EP2576989B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010021928 DE102010021928A1 (de) 2010-05-28 2010-05-28 Turbine für einen Abgasturbolader
PCT/EP2011/002018 WO2011147510A2 (fr) 2010-05-28 2011-04-20 Turbine pour une turbosoufflante à gaz d'échappement

Publications (2)

Publication Number Publication Date
EP2576989A2 EP2576989A2 (fr) 2013-04-10
EP2576989B1 true EP2576989B1 (fr) 2015-02-25

Family

ID=44060862

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11716836.9A Active EP2576989B1 (fr) 2010-05-28 2011-04-20 Turbine pour un turbocompresseur d'échappement

Country Status (6)

Country Link
US (1) US8997485B2 (fr)
EP (1) EP2576989B1 (fr)
JP (1) JP5445810B2 (fr)
CN (1) CN103097667B (fr)
DE (1) DE102010021928A1 (fr)
WO (1) WO2011147510A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010014096A1 (de) * 2010-04-07 2011-10-13 Daimler Ag Verbrennungskraftmaschine
US10287979B2 (en) * 2012-11-12 2019-05-14 United Technologies Corporation Split intermediate case
DE112015001237B4 (de) * 2014-05-20 2021-06-24 Borgwarner Inc. Abgasturbolader
DE102017009452A1 (de) * 2017-10-11 2019-04-11 Daimler Ag Verbrennungskraftmaschine für ein Kraftfahrzeug und Kraftfahrzeug mit einer solchen Verbrennungskraftmaschine

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3137477A (en) * 1960-10-25 1964-06-16 Geratebau Eberspacher Ohg Gas turbine having adjustable nozzle flow means
FR1418849A (fr) * 1964-05-30 1965-11-26 Renault Moteur rotatif diesel suralimenté par turbo-compresseur
CH577632A5 (fr) * 1974-07-09 1976-07-15 Charmilles Sa Ateliers
US4177005A (en) * 1975-09-06 1979-12-04 Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft (M.A.N.) Variable-throat spiral duct system for rotary stream-flow machines
JPS52137523A (en) * 1976-05-14 1977-11-17 Ishikawajima Harima Heavy Ind Co Ltd Impulse turbine
JPS5918230A (ja) * 1982-07-21 1984-01-30 Kanesaka Gijutsu Kenkyusho:Kk 低圧縮比タ−ボ過給圧縮着火エンジン
DE3302186A1 (de) * 1983-01-24 1984-07-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Abgasturbolader fuer brennkraftmaschinen
JPS59203823A (ja) * 1983-05-02 1984-11-19 Honda Motor Co Ltd タ−ボチヤ−ジヤ装置
JPS61178034U (fr) * 1985-04-26 1986-11-06
JP2003035152A (ja) * 2001-07-25 2003-02-07 Daido Steel Co Ltd ターボ過給機ハウジングおよびその製造方法
DE10212675B4 (de) * 2002-03-22 2006-05-18 Daimlerchrysler Ag Abgasturbolader in einer Brennkraftmaschine
US8250760B2 (en) * 2004-05-03 2012-08-28 Honeywell International Inc. Center housing of a turbine for a turbocharger and method of manufacturing the same
US20060230759A1 (en) * 2005-04-13 2006-10-19 Semrau H A Variable geometry turbocharger
DE102006003599A1 (de) * 2006-01-25 2007-08-16 Siemens Ag Kompressorgehäuse für einen Abgasturbolader
US7428814B2 (en) * 2006-03-08 2008-09-30 Melvin Hess Pedersen Turbine assemblies and related systems for use with turbochargers
US7694518B2 (en) * 2007-08-14 2010-04-13 Deere & Company Internal combustion engine system having a power turbine with a broad efficiency range
DE102007055615A1 (de) * 2007-11-20 2009-05-28 Mann + Hummel Gmbh Gehäuse für einen Radialverdichter
DE102008020406A1 (de) * 2008-04-24 2009-10-29 Daimler Ag Abgasturbolader für eine Brennkraftmaschine eines Kraftfahrzeugs und Brennkraftmaschine
DE102008032492A1 (de) * 2008-07-05 2010-01-07 Daimler Ag Turbinengehäuse für einen Abgasturbolader einer Brennkraftmaschine
DE102008039085A1 (de) * 2008-08-21 2010-02-25 Daimler Ag Brennkraftmaschine mit einem Abgasturbolader
US8113770B2 (en) * 2009-02-03 2012-02-14 Honeywell International Inc. Turbine assembly for an exhaust gas-driven turbocharger having a variable nozzle
DE102010014096A1 (de) * 2010-04-07 2011-10-13 Daimler Ag Verbrennungskraftmaschine

Also Published As

Publication number Publication date
CN103097667B (zh) 2015-03-11
US8997485B2 (en) 2015-04-07
WO2011147510A2 (fr) 2011-12-01
US20130104539A1 (en) 2013-05-02
JP5445810B2 (ja) 2014-03-19
WO2011147510A3 (fr) 2013-03-28
CN103097667A (zh) 2013-05-08
EP2576989A2 (fr) 2013-04-10
DE102010021928A1 (de) 2011-12-01
JP2013530335A (ja) 2013-07-25

Similar Documents

Publication Publication Date Title
WO2010020323A1 (fr) Turbocompresseur entraîné par les gaz d'échappement pour un moteur à combustion interne d'un véhicule automobile
EP2705222B1 (fr) Turbine pour un turbocompresseur à gaz d'échappement
EP2742219B1 (fr) Moteur à combustion interne pour véhicule
DE102008049782A1 (de) Abgasturbolader für eine Brennkraftmaschine
WO2010121684A1 (fr) Moteur à combustion interne et procédé permettant de faire fonctionner un moteur à combustion interne
WO2010069301A2 (fr) Turbines à variabilité intégrale pour turbocompresseurs
WO2012076095A1 (fr) Turbine pour turbocompresseur sur gaz d'échappement
EP2576989B1 (fr) Turbine pour un turbocompresseur d'échappement
WO2011054513A1 (fr) Moteur en v
DE102012023118A1 (de) Verbrennungskraftmaschine für einen Kraftwagen
EP2058484A1 (fr) Moteur à combustion interne suralimenté
WO2012065675A1 (fr) Turbine destinée à un turbocompresseur à gaz d'échappement d'un moteur à combustion interne
EP2058485B1 (fr) Moteur à combustion interne chargé et procédé de fonctionnement d'un tel moteur à combustion interne
WO2011110209A1 (fr) Moteur thermique à admission à pression d'aspiration
DE102012016984B4 (de) Turbine für einen Abgasturbolader sowie Verbrennungskraftmaschine mit einer solchen Turbine
DE102014218345A1 (de) Aufgeladene Brennkraftmaschine mit in Reihe angeordneten Abgasturboladern
DE102011120168A1 (de) Verdichter für einen Abgasturbolader
DE102014220680A1 (de) Brennkraftmaschine mit Mixed-Flow-Turbine umfassend eine Leiteinrichtung
DE102014220679B4 (de) Brennkraftmaschine mit Mixed-Flow-Turbine umfassend eine Leiteinrichtung und Abgasrückführung
DE202014104419U1 (de) Aufgeladene Brennkraftmaschine mit in Reihe angeordneten Abgasturboladern
DE102010055101A1 (de) Verdichter, insbesondere für einen Abgasturbolader, sowie Abgasturbolader
DE102011016529A1 (de) Turbine für einen Abgasturbolader sowie Verbrennungskraftmaschine mit einer solchen Turbine
DE102010021926A1 (de) Verbrennungskraftmaschine
EP2058486B1 (fr) Moteur à combustion interne suralimenté et procédé de fonctionnement d'un tel moteur à combustion interne
DE102009014350A1 (de) Verdichterrad sowie Verdichter und Verfahren

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20121128

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

R17D Deferred search report published (corrected)

Effective date: 20130328

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140916

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011005966

Country of ref document: DE

Effective date: 20150409

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 712178

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150415

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20150225

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150525

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150526

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150625

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011005966

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150420

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150430

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150430

26N No opposition filed

Effective date: 20151126

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110420

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 712178

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150430

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150625

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160420

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190426

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20190429

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502011005966

Country of ref document: DE

Owner name: MERCEDES-BENZ GROUP AG, DE

Free format text: FORMER OWNER: DAIMLER AG, 70327 STUTTGART, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011005966

Country of ref document: DE

Representative=s name: JENSEN & SON, GB

Ref country code: DE

Ref legal event code: R081

Ref document number: 502011005966

Country of ref document: DE

Owner name: DAIMLER AG, DE

Free format text: FORMER OWNER: DAIMLER AG, 70327 STUTTGART, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011005966

Country of ref document: DE

Representative=s name: JENSENS IP LIMITED, IE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011005966

Country of ref document: DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011005966

Country of ref document: DE

Representative=s name: JENSENS IP LIMITED, IE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200420

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502011005966

Country of ref document: DE

Owner name: MERCEDES-BENZ GROUP AG, DE

Free format text: FORMER OWNER: DAIMLER AG, STUTTGART, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011005966

Country of ref document: DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230427

Year of fee payment: 13