EP2216516A1 - Berstschutzvorrichtung für Radialverdichter - Google Patents

Berstschutzvorrichtung für Radialverdichter Download PDF

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Publication number
EP2216516A1
EP2216516A1 EP09152067A EP09152067A EP2216516A1 EP 2216516 A1 EP2216516 A1 EP 2216516A1 EP 09152067 A EP09152067 A EP 09152067A EP 09152067 A EP09152067 A EP 09152067A EP 2216516 A1 EP2216516 A1 EP 2216516A1
Authority
EP
European Patent Office
Prior art keywords
compressor
housing
insert
axial
wall contour
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.)
Withdrawn
Application number
EP09152067A
Other languages
German (de)
English (en)
French (fr)
Inventor
Joel Schlienger
Patrick Aberle
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.)
Accelleron Industries AG
Original Assignee
ABB Turbo Systems 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 ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Priority to EP09152067A priority Critical patent/EP2216516A1/de
Priority to EP10150616A priority patent/EP2216517B1/de
Priority to KR1020100009538A priority patent/KR101157440B1/ko
Priority to US12/699,453 priority patent/US8393851B2/en
Priority to JP2010022968A priority patent/JP5074541B2/ja
Priority to CN2010101187676A priority patent/CN101793266B/zh
Publication of EP2216516A1 publication Critical patent/EP2216516A1/de
Withdrawn legal-status Critical Current

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Classifications

    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63H—TOYS, e.g. TOPS, DOLLS, HOOPS OR BUILDING BLOCKS
    • A63H37/00—Jokes; Confetti, streamers, or other dance favours ; Cracker bonbons or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63H—TOYS, e.g. TOPS, DOLLS, HOOPS OR BUILDING BLOCKS
    • A63H29/00—Drive mechanisms for toys in general
    • A63H29/10—Driving mechanisms actuated by flowing media
    • A63H29/14—Driving mechanisms actuated by flowing media by a water stream
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63H—TOYS, e.g. TOPS, DOLLS, HOOPS OR BUILDING BLOCKS
    • A63H5/00—Musical or noise- producing devices for additional toy effects other than acoustical
    • 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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/04—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position
    • F01D21/045—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position special arrangements in stators or in rotors dealing with breaking-off of part of rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0292—Stop safety or alarm devices, e.g. stop-and-go control; Disposition of check-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F42—AMMUNITION; BLASTING
    • F42B—EXPLOSIVE CHARGES, e.g. FOR BLASTING, FIREWORKS, AMMUNITION
    • F42B4/00—Fireworks, i.e. pyrotechnic devices for amusement, display, illumination or signal purposes
    • F42B4/04—Firecrackers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the invention relates to the field of exhaust gas turbochargers for supercharged internal combustion engines.
  • It relates to a compressor of an exhaust gas turbocharger with a device for ensuring the compressor-side Berstschutzfind the exhaust gas turbocharger.
  • exhaust gas turbochargers are nowadays used by default with one of the combustion chamber of the internal combustion engine air for the combustion process supplying compressor and an exhaust gas turbine in the exhaust tract of the internal combustion engine. With the supercharging of the internal combustion engine, the amount of air and fuel in the cylinders is increased and from this a considerable increase in power for the internal combustion engine is obtained.
  • the exhaust gas turbocharger used for this purpose is composed of a rotor consisting of a compressor wheel and a turbine wheel as well as the shaft bearing, the flow-guiding housing parts (compressor housing, turbine housing) and the bearing housing.
  • the exhaust gas turbocharger of the exhaust gas turbocharger is charged accordingly with a large exhaust gas flow
  • very high peripheral speeds are achieved at the blade tips of the turbine and compressor wheels.
  • the maximum permissible rotor speed of a turbocharger is a function of the wheel size, the geometry and the strength values of the materials used. In general, the rotating components are subject to very high centrifugal forces and thus high material tensions. Defects in the material structure can possibly lead to bursting of the compressor or turbine wheel, with unpredictable consequences for the adjacent housing.
  • the initial failure pattern of a compressor wheel can be described by a blade break or a multi-part hub burst.
  • the blades When shovels burst, the blades fail in the foot area of the compressor, leaving the wheel hub intact.
  • the hub area usually breaks down into two to four fragments.
  • the most critical case of the compressor rupture is the 3-part hub break with three roughly equal fragments (3x120 ° sectors).
  • the burst protection concept (containment concept) of an exhaust gas turbocharger is to be interpreted as meaning that all fragments, in the case of a multi-part hub burst, are retained within the outer casing casing at a predetermined bursting speed.
  • WO 02/090722 is a predetermined breaking point in the flow channel over the blades of the compressor radially outwardly bounding housing insert wall provided to prevent in the case of Ver Whyrradberstens the axial thrown away housing parts or components attached to the compressor housing.
  • EP 1-586-745 is prevented by means of a support flange and a sufficiently large distance of the support flange to the housing wall, that takes place in the case of a bursting compressor a direct axial momentum transfer from flying compressor wheel on the air inlet housing, thus reducing the load on the upper connections between the housing parts and the breaking of the compound and the Leakage of the fragments prevented.
  • the housing insert wall is supplemented with holding means to thereby catch the axially forwardly thrown fragments of the compressor wheel and the housing insert wall respectively to jam.
  • the object of the invention is to make the housing assembly of a compressor of an exhaust gas turbocharger burstable in the event of a failed compressor wheel by the outer housing connections between the compressor housing and the bearing housing are protected against failure.
  • a housing composite which comprises a voltage applied to an axial stop of the outer compressor housing housing insert and a bending element in the power flow between the flow channel limiting insert wall contour and the outer compressor housing.
  • the bending element consists of a perpendicular to the axial direction oriented support element, which is optionally formed as a circumferential support ring, and in the axial direction upstream and downstream webs together, the webs axially in front of the support member and the webs axially to the support member in a Direction vertical to the axial - ie in the circumferential direction and / or in the radial direction - are offset from one another.
  • the burst-caused axial force flow between the insert wall contour and the outer compressor housing is deflected twice, thereby achieving an axially soft bending construction.
  • the axial load in the outer housing connections (screws) is significantly reduced.
  • the bending element is plastically axially compressed in the area of the circumferential ring, thereby reducing kinetic rupture energy.
  • the outer compressor housing via the contact surfaces of the fastening webs of the housing insert and finally into the connection to the bearing housing to be protected.
  • the inventive bursting concept provides for the case of a compressor burst on the smallest possible space and with a small number of standard screws for a high axial relief of the connection between the compressor housing and the bearing housing.
  • the kinetic energy released during failure is mainly absorbed by a plastic deformation of the inner housing parts.
  • the outer housing casing and the housing connecting screws are largely relieved.
  • Fig. 1 shows an exhaust gas turbocharger according to the prior art with a centrifugal compressor and a radial turbine.
  • the turbine 9 is mounted on the shaft 8 or integral therewith.
  • the turbine housing 90 encloses the turbine wheel and limits the flow channels, which lead the hot exhaust gas from the internal combustion engine via the turbine wheel to the exhaust systems.
  • the compressor 1 is also mounted on the shaft 8.
  • the compressor housing 10 is usually composed of a plurality of housing parts and is screwed by means of an external attachment 7 on the bearing housing. Depending on the design concept, the multipart compressor housing is assembled in a specific order. In the illustrated case, only the inner compressor housing, the housing insert 10, in the outer compressor housing, the spiral housing 20, inserted and possibly force-locking or form-fitting fastened thereto with fasteners.
  • the unit of inner and outer compressor housing is pushed over the already arranged on the shaft compressor wheel 1 and connected to the bearing housing 80.
  • the inner compressor housing 10 as indicated in the illustrated case, pressed when connecting to the bearing housing in the region of the diffuser downstream of the compressor outlet via diffuser blades 19 against a contact surface of the bearing housing 80 and thus clamped in operation between the outer compressor housing 20 and the bearing housing 80 ,
  • Fig. 2 shows an enlarged section of a compressor housing which is constructed analogously to the preceding, but which has a has designed according to the invention housing insert 10.
  • the housing insert is secured to the outer compressor housing (volute) 20 and, in the case of a bladed diffuser, is optionally clamped between the outer compressor housing 20 and the bearing housing 80 via the blade 19 of the diffuser.
  • the housing insert 10 is formed in one piece, but comprises a plurality of functional subregions.
  • the insert wall contour 11 delimits the flow channel 61 against the radially inner side.
  • the air which is to be supplied to the combustion chambers of the internal combustion engine then flows between the hub of the compressor wheel 1 and the insert wall contour 11.
  • the insert wall contour 11 is aligned axially in a radial compressor in the input area and then extends in the radial direction and opens into a spiral collecting space 62 of the outer compressor housing.
  • the insert wall contour can be provided with a predetermined breaking point 17, which selectively breaks the insert wall contour in the event of a burst of the compressor wheel, and thereby supports the energy reduction in the interior of the housing insert provided according to the invention.
  • the housing insert For centering the housing insert 10 on the outer compressor housing 20, the housing insert comprises a centering ring 12, which rests on the outer compressor housing.
  • the bearing surface can be sealed by means of a sealing element (sealing ring).
  • the outer compressor housing 20 in the region of the support surface for centering a closer to the compressor inlet side (ie in the figure to the left) narrowing cross-section, which can result in bursting a jamming of the centering in the constriction of the support surface on the outer compressor housing. With such a jamming part of the rupture energy in the region of the centering ring 12 can be reduced.
  • the centering ring 12 is connected via a connecting web 16 with the inner insert wall contour 11.
  • the connecting web 16 can, as in the Fig. 2 is indicated, optionally double curved (S-shaped) to be executed.
  • S-shaped connecting web 16 is heavily loaded on bending and thereby achieves a high axial resilience of the housing insert with a burst-related impact load on the outer housing connections
  • axially directed webs 14 lead to a support ring 13 which rests on likewise axially directed fastening webs 15 on an axial stop 21 of the outer compressor housing 20.
  • the fastening webs are optionally fastened by means of fastening means 18 on the outer compressor housing, for example, screws or screw pins may be arranged in openings provided for this purpose in the fastening webs.
  • the support ring may optionally be divided into a plurality of ring-segment-shaped support elements, which support elements then each have at least one web on both axial end sides, wherein the webs are arranged offset to one another on the opposite end faces.
  • the webs 14 between the support ring 13 and the centering ring 12 are distributed along the circumference of the support ring.
  • the fastening webs 15 are also distributed along the circumference of the support ring, but are arranged offset to the webs 14.
  • the fastening webs and the webs can be arranged offset from each other in addition to or instead of the offset in the circumferential direction and in the radial direction.
  • the fastening webs 15, the support ring 13, the webs 14 between the support ring and the centering ring and the centering ring 12 together form a bending element 111.
  • Fig. 3 and Fig. 4 show the removed housing insert 10 with the flexure construction.
  • the webs of the bending element 111 are offset in this embodiment in each case by half a pitch in the circumferential direction. Thanks to this offset of the power flow between the centering ring 12 and the axial stop 21 on the outer compressor housing 20 via the webs 14 between the centering ring and the support ring, the rotating support ring 13, and the fastening webs 15, twice deflected, thereby achieving an axially soft bending construction.
  • the housing insert 10 When Ver emphasizerber the housing insert 10 can be rotated by the impact of the compressor wheel fragments in the circumferential direction, which can lead to a shearing of the connection 18 between the mounting webs 15 and the outer compressor housing and thus a partial dissipation of the kinetic burst energy.
  • the axial bursting forces are introduced via the housing insert 10 into the outer compressor housing 20 and finally into the outer housing connection 7.
  • the housing connection 7 remains intact and the bearing housing 80 and the outer compressor housing 20 holds together.
  • a large part of the energy degraded in the housing insert is thus always to ensure that the housing connection 7 remains intact and the bearing housing 80 and the outer compressor housing 20 holds together.
  • the fragments thrown outwards may become wedged between the housing insert and the bearing housing in such a way that high axial forces load the outer compressor housing as well as the bearing housing in addition to the housing insert.
  • the axial forces are transmitted to the centering ring 12.
  • the axial forces are transmitted via the webs 14 to the support ring 13.
  • the peripheral support ring 13 is plastically upset in the sequence in the region of the connection to the webs 14, as shown in the Fig. 4 is indicated by the dotted course of the support ring 13 '. Due to the plastic deformation of the support ring kinetic rupture energy is reduced.
  • only a fraction of the initially existing rupture energy reaches the outer compressor housing 20 via the bearing surfaces of the fastening webs 15 and finally into the housing connection 7 to be protected in the radially outer region of the compressor housing.
  • the webs and the rings of the flexure are constructively designed so that for normal turbocharger operation a sufficiently high rigidity is achieved and the insert wall is assumed to be rigid, so that the games between the compressor and the housing are not affected. Furthermore, when designing the bending element, it must be ensured that the natural frequencies of the insert wall obtained do not come within the frequency range of the motor-induced excitation spectrum.
  • the housing insert may be made of a cast material (e.g., GGG-40).
  • the insert wall contour 11 can optionally delimit a cavity surrounding the flow channel 61 radially against the flow channel, in which already partially compressed air from the region of the compressor wheel blades can be guided back into the suction region.
  • an at least partially circumferential slot in the area of the compressor wheel blades can optionally be embedded in the insert wall contour.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP09152067A 2009-02-04 2009-02-04 Berstschutzvorrichtung für Radialverdichter Withdrawn EP2216516A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP09152067A EP2216516A1 (de) 2009-02-04 2009-02-04 Berstschutzvorrichtung für Radialverdichter
EP10150616A EP2216517B1 (de) 2009-02-04 2010-01-13 Berstschutzvorrichtung für Radialverdichter
KR1020100009538A KR101157440B1 (ko) 2009-02-04 2010-02-02 파열 보호부
US12/699,453 US8393851B2 (en) 2009-02-04 2010-02-03 Bursting protection
JP2010022968A JP5074541B2 (ja) 2009-02-04 2010-02-04 バーストに対する保護
CN2010101187676A CN101793266B (zh) 2009-02-04 2010-02-04 破裂保护

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09152067A EP2216516A1 (de) 2009-02-04 2009-02-04 Berstschutzvorrichtung für Radialverdichter

Publications (1)

Publication Number Publication Date
EP2216516A1 true EP2216516A1 (de) 2010-08-11

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ID=40469896

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09152067A Withdrawn EP2216516A1 (de) 2009-02-04 2009-02-04 Berstschutzvorrichtung für Radialverdichter
EP10150616A Active EP2216517B1 (de) 2009-02-04 2010-01-13 Berstschutzvorrichtung für Radialverdichter

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP10150616A Active EP2216517B1 (de) 2009-02-04 2010-01-13 Berstschutzvorrichtung für Radialverdichter

Country Status (5)

Country Link
US (1) US8393851B2 (ja)
EP (2) EP2216516A1 (ja)
JP (1) JP5074541B2 (ja)
KR (1) KR101157440B1 (ja)
CN (1) CN101793266B (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010064047A1 (de) * 2010-12-23 2012-06-28 Man Diesel & Turbo Se Strömungsmaschine
WO2013124614A1 (en) * 2012-02-23 2013-08-29 Napier Turbochargers Limited Turbocharger
EP2821596A1 (de) * 2013-07-05 2015-01-07 ABB Turbo Systems AG Lufteintritt eines Verdichters eines Abgasturboladers
DE102015003296A1 (de) 2015-03-14 2015-12-03 Daimler Ag Abgasturbolader für eine Verbrennungskraftmaschine sowie Verfahren zum Betreiben eines solchen Abgasturboladers
WO2018197213A1 (de) * 2017-04-28 2018-11-01 Continental Automotive Gmbh Turbolader mit sollbruchstelle für eine brennkraftmaschine

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DE102009049841B4 (de) * 2009-10-14 2015-01-15 Mtu Friedrichshafen Gmbh Gasturbomaschine und Brennkraftmaschine
DE102010064025A1 (de) * 2010-12-23 2012-06-28 Abb Turbo Systems Ag Berstschutz
DE102013209063A1 (de) * 2012-09-26 2014-03-27 Bosch Mahle Turbo Systems Gmbh & Co. Kg Radialverdichter für einen Abgasturbolader
US9371835B2 (en) * 2013-07-19 2016-06-21 Praxair Technology, Inc. Coupling for directly driven compressor
FR2997444B1 (fr) * 2012-10-31 2018-07-13 Snecma Moyeu de carter pour une turbomachine
DE102014204768A1 (de) * 2013-05-16 2014-11-20 Bosch Mahle Turbo Systems Gmbh & Co. Kg Radialverdichter für einen Abgasturbolader
WO2015098826A1 (ja) * 2013-12-24 2015-07-02 三菱重工業株式会社 圧縮機および過給機
CN103925017B (zh) * 2014-03-04 2015-06-17 大同北方天力增压技术有限公司 用于涡轮增压器涡轮箱的防爆裂装置
GB201404050D0 (en) * 2014-03-07 2014-04-23 Cummins Ltd A turbine
JP6139463B2 (ja) * 2014-05-20 2017-05-31 トヨタ自動車株式会社 内燃機関
JP6404082B2 (ja) * 2014-10-28 2018-10-10 三菱重工業株式会社 遠心圧縮機およびそれを備えた過給機
US9995179B2 (en) * 2014-12-17 2018-06-12 Progress Rail Locomotive Inc. Compressor assembly for turbocharger burst containment
JP6001707B2 (ja) * 2015-02-25 2016-10-05 株式会社オティックス 過給機用のコンプレッサハウジング
DE102015014550A1 (de) * 2015-11-11 2017-05-11 Man Diesel & Turbo Se Ansaugsystem für einen Abgasturbolader und Abgasturbolader
DE102016111081B4 (de) * 2016-06-17 2024-08-01 Man Energy Solutions Se Strömungsmaschine
DE102016125143A1 (de) * 2016-12-21 2018-06-21 Man Diesel & Turbo Se Radialverdichter und Turbolader
DE102018102704A1 (de) * 2018-02-07 2019-08-08 Man Energy Solutions Se Radialverdichter
JP2021105385A (ja) * 2019-12-27 2021-07-26 三菱重工エンジン＆ターボチャージャ株式会社 コンプレッサカバーおよび該コンプレッサカバーを備える遠心圧縮機
JP7286017B2 (ja) * 2020-06-04 2023-06-02 三菱重工マリンマシナリ株式会社 タービンハウジングおよび過給機
US11519423B1 (en) * 2021-11-11 2022-12-06 Progress Rail Locomotive Inc. Compressor joint

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FR2342397A1 (fr) * 1976-02-26 1977-09-23 Mtu Muenchen Gmbh Disque de recouvrement pour rotor radial de turbo-machine, notamment de moteur a reaction a turbine a gaz
DE10050931C1 (de) * 2000-10-13 2002-08-14 Man B & W Diesel Ag Turbomaschine mit radial durchströmten Laufrad
WO2002090722A1 (de) 2001-05-04 2002-11-14 Abb Turbo Systems Ag Berstschutzvorrichtung für radialverdichter von turboladern
EP1586745A1 (de) 2004-04-13 2005-10-19 ABB Turbo Systems AG Verdichtergehäuse
GB2414769A (en) 2004-06-05 2005-12-07 Man B & W Diesel Ag Turbo-machine with impeller containment assembly.
EP1719879A1 (de) * 2005-05-03 2006-11-08 ABB Turbo Systems AG Berstschutzvorrichtung für Radialverdichter
EP2000633A2 (en) * 2007-06-05 2008-12-10 Honeywell International Inc. Augmented vaneless diffuser containment

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DE102004028133C5 (de) 2004-06-09 2017-10-26 Man Diesel & Turbo Se Strömungsmaschine, insbesondere Abgasturbolader
DE102005039820B4 (de) 2005-08-22 2007-06-28 Man Diesel Se Containment-Sicherung für Strömungsmaschinen mit radial durchströmtem Verdichterrad

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Publication number Priority date Publication date Assignee Title
FR2342397A1 (fr) * 1976-02-26 1977-09-23 Mtu Muenchen Gmbh Disque de recouvrement pour rotor radial de turbo-machine, notamment de moteur a reaction a turbine a gaz
DE10050931C1 (de) * 2000-10-13 2002-08-14 Man B & W Diesel Ag Turbomaschine mit radial durchströmten Laufrad
WO2002090722A1 (de) 2001-05-04 2002-11-14 Abb Turbo Systems Ag Berstschutzvorrichtung für radialverdichter von turboladern
EP1586745A1 (de) 2004-04-13 2005-10-19 ABB Turbo Systems AG Verdichtergehäuse
GB2414769A (en) 2004-06-05 2005-12-07 Man B & W Diesel Ag Turbo-machine with impeller containment assembly.
EP1719879A1 (de) * 2005-05-03 2006-11-08 ABB Turbo Systems AG Berstschutzvorrichtung für Radialverdichter
EP2000633A2 (en) * 2007-06-05 2008-12-10 Honeywell International Inc. Augmented vaneless diffuser containment

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010064047A1 (de) * 2010-12-23 2012-06-28 Man Diesel & Turbo Se Strömungsmaschine
WO2013124614A1 (en) * 2012-02-23 2013-08-29 Napier Turbochargers Limited Turbocharger
US9683578B2 (en) 2012-02-23 2017-06-20 Napier Turbochargers Limited Turbocharger
EP2821596A1 (de) * 2013-07-05 2015-01-07 ABB Turbo Systems AG Lufteintritt eines Verdichters eines Abgasturboladers
DE102015003296A1 (de) 2015-03-14 2015-12-03 Daimler Ag Abgasturbolader für eine Verbrennungskraftmaschine sowie Verfahren zum Betreiben eines solchen Abgasturboladers
WO2018197213A1 (de) * 2017-04-28 2018-11-01 Continental Automotive Gmbh Turbolader mit sollbruchstelle für eine brennkraftmaschine
US11060453B2 (en) 2017-04-28 2021-07-13 Vitesco Technologies GmbH Turbocharger with predetermined breaking point for an internal combustion engine

Also Published As

Publication number Publication date
US8393851B2 (en) 2013-03-12
CN101793266B (zh) 2012-07-18
JP5074541B2 (ja) 2012-11-14
CN101793266A (zh) 2010-08-04
KR101157440B1 (ko) 2012-06-22
KR20100089776A (ko) 2010-08-12
EP2216517B1 (de) 2012-07-11
JP2010180882A (ja) 2010-08-19
US20100192570A1 (en) 2010-08-05
EP2216517A1 (de) 2010-08-11

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