EP2216517B1 - Dispositif de protection contre l'éclatement d'un compresseur radial - Google Patents

Dispositif de protection contre l'éclatement d'un compresseur radial Download PDF

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Publication number
EP2216517B1
EP2216517B1 EP10150616A EP10150616A EP2216517B1 EP 2216517 B1 EP2216517 B1 EP 2216517B1 EP 10150616 A EP10150616 A EP 10150616A EP 10150616 A EP10150616 A EP 10150616A EP 2216517 B1 EP2216517 B1 EP 2216517B1
Authority
EP
European Patent Office
Prior art keywords
compressor
housing
axial
support element
webs
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
EP10150616A
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German (de)
English (en)
Other versions
EP2216517A1 (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 EP10150616A priority Critical patent/EP2216517B1/fr
Publication of EP2216517A1 publication Critical patent/EP2216517A1/fr
Application granted granted Critical
Publication of EP2216517B1 publication Critical patent/EP2216517B1/fr
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Classifications

    • 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
    • A63H37/00—Jokes; Confetti, streamers, or other dance favours ; Cracker bonbons or the like
    • 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 insert wall that takes place in the case of a bursting compressor impeller direct axial momentum transferring wegfrise 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 is made up of a, at an angle, preferably perpendicular to the axial direction oriented support member 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 after the support element in a direction perpendicular to the axial - so in the circumferential direction and / or in the radial direction - are arranged offset to 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, thereby supporting 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 may 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 peripheral support ring 13, and the fastening webs 15, twice deflected, thereby achieving an axially soft bending construction.
  • the housing insert 10 When Ver Whyrbersten 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.
  • a support ring which is oriented strictly perpendicular to the axial direction, it is also possible to provide a support ring oriented at an angle, preferably at an angle in the range between 60 ° and 90 ° to the axial direction, which is also compressed according to the invention and can thus absorb rupture energy.

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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)

Claims (11)

  1. Compresseur d'une turbosoufflante à gaz d'échappement, comprenant une roue de compresseur (1) pouvant tourner autour d'un axe, un boîtier de compresseur extérieur (20) ainsi qu'un insert de boîtier (10) disposé radialement à l'extérieur de la roue de compresseur (1), l'insert de boîtier comprenant un contour de paroi d'insert (11) qui, conjointement avec un moyeu de la roue de compresseur (1), limite un canal d'écoulement (61),
    caractérisé en ce que
    l'insert de boîtier (10) s'applique contre une butée axiale (21) du boîtier de compresseur extérieur (20), orientée vers la roue de compresseur, un élément flexible (111) étant prévu pour le transfert des forces axiales depuis le contour de paroi d'insert (11) jusqu'au boîtier de compresseur extérieur (20), l'élément flexible (111) comprenant au moins deux nervures (14, 15) orientées axialement et disposées de manière décalée l'une par rapport à l'autre, ainsi qu'un élément porteur (13) reliant les nervures (14, 15) l'une à l'autre, l'élément porteur (13) étant orienté suivant un angle par rapport à la direction axiale et étant disposé entre les nervures (14, 15) par rapport à la direction axiale.
  2. Compresseur selon la revendication 1, dans lequel l'élément flexible (111) comprend un élément porteur (13) en forme de segment annulaire, l'élément porteur (13) étant orienté dans la direction périphérique de la roue de compresseur, et l'élément porteur (13) présentant plusieurs nervures orientées axialement (14) sur un côté axial et au moins une nervure orientée axialement (15) sur l'autre côté axial.
  3. Compresseur selon la revendication 1, dans lequel l'élément flexible (111) comprend un élément porteur (13) de forme annulaire, l'élément porteur (13) étant disposé dans la direction périphérique de la roue de compresseur, et l'élément porteur (13) présentant plusieurs nervures (14, 15) orientées axialement sur les deux côtés axiaux.
  4. Compresseur selon la revendication 1, dans lequel l'élément porteur (13) est orienté perpendiculairement à la direction axiale et est disposé entre les nervures (14, 15) par rapport à la direction axiale.
  5. Compresseur selon la revendication 4, dans lequel l'élément flexible (111) comprend un élément porteur (13) en forme de segment annulaire, l'élément porteur (13) étant orienté dans la direction périphérique de la roue de compresseur et l'élément porteur (13) présentant plusieurs nervures orientées axialement (14) sur un côté axial et au moins une nervure orientée axialement (15) sur l'autre côté axial.
  6. Compresseur selon la revendication 4, dans lequel l'élément flexible (111) comprend un élément porteur annulaire (13), l'élément porteur (13) étant disposé dans la direction périphérique de la roue de compresseur et l'élément porteur (13) présentant plusieurs nervures orientées axialement (14, 15) sur les deux côtés axiaux.
  7. Compresseur selon l'une quelconque des revendications 1 à 6, dans lequel, pour le transfert des forces axiales depuis le contour de paroi d'insert (11) jusqu'à la butée axiale (21) du boîtier de compresseur extérieur (20), l'élément flexible (111) est disposé dans le flux de forces entre le contour de paroi d'insert (11) et la butée axiale (21).
  8. Compresseur selon l'une quelconque des revendications 1 à 6, dans lequel l'élément flexible (111) fait partie du boîtier de compresseur extérieur (20) et est disposé, pour le transfert des forces axiales depuis le contour de paroi d'insert (11) jusqu'au boîtier de compresseur (20) de la butée axiale (21), dans le flux de forces entre le contour de paroi d'insert (11) et l'élément flexible (111).
  9. Compresseur selon l'une quelconque des revendications 1 à 6, dans lequel, pour le transfert des forces axiales depuis le contour de paroi d'insert (11) à l'élément flexible (111), l'élément flexible (111) comprend une bague de centrage périphérique (12) qui est connectée au contour de paroi d'insert (11) par le biais d'une nervure de liaison (16).
  10. Compresseur selon la revendication 9, dans lequel la nervure de liaison (16) est pourvue d'une double courbure entre le contour de paroi d'insert (11) et l'élément flexible (111), c'est-à-dire est réalisée avec un profil axial en forme de S.
  11. Turbosoufflante à gaz d'échappement comprenant un compresseur selon l'une quelconque des revendications 1 à 6.
EP10150616A 2009-02-04 2010-01-13 Dispositif de protection contre l'éclatement d'un compresseur radial Active EP2216517B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10150616A EP2216517B1 (fr) 2009-02-04 2010-01-13 Dispositif de protection contre l'éclatement d'un compresseur radial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP09152067A EP2216516A1 (fr) 2009-02-04 2009-02-04 Dispositif de protection contre l'éclatement d'un compresseur radial
EP10150616A EP2216517B1 (fr) 2009-02-04 2010-01-13 Dispositif de protection contre l'éclatement d'un compresseur radial

Publications (2)

Publication Number Publication Date
EP2216517A1 EP2216517A1 (fr) 2010-08-11
EP2216517B1 true EP2216517B1 (fr) 2012-07-11

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP09152067A Withdrawn EP2216516A1 (fr) 2009-02-04 2009-02-04 Dispositif de protection contre l'éclatement d'un compresseur radial
EP10150616A Active EP2216517B1 (fr) 2009-02-04 2010-01-13 Dispositif de protection contre l'éclatement d'un compresseur radial

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP09152067A Withdrawn EP2216516A1 (fr) 2009-02-04 2009-02-04 Dispositif de protection contre l'éclatement d'un compresseur radial

Country Status (5)

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

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JPH066240Y2 (ja) * 1988-07-19 1994-02-16 三菱重工業株式会社 遠心圧縮機
GB9027168D0 (en) * 1990-12-14 1991-02-06 Rolls Royce Business Ventures Turbine scroll
DE10050931C5 (de) * 2000-10-13 2007-03-29 Man Diesel Se Turbomaschine mit radial durchströmten Laufrad
TW576886B (en) 2001-05-04 2004-02-21 Abb Turbo Systems Ag Turbocharger having a radial-flow compressor and burst-protection arrangement for a radial-flow compressor of a turbocharger
US6962480B2 (en) * 2003-11-12 2005-11-08 Honeywell International, Inc. Thermally stabilized turbine scroll retention ring for uniform loading application
EP1586745B1 (fr) 2004-04-13 2015-07-29 ABB Turbo Systems AG Carter de compresseur
DE102004027594B4 (de) 2004-06-05 2006-06-29 Man B & W Diesel Ag Strömungsmaschine mit radial durchströmtem Verdichterrad
DE102004028133C5 (de) 2004-06-09 2017-10-26 Man Diesel & Turbo Se Strömungsmaschine, insbesondere Abgasturbolader
EP1719879B1 (fr) * 2005-05-03 2008-01-30 ABB Turbo Systems AG Dispositif de protection en cas d'éclatement pour compresseur radial
DE102005039820B4 (de) 2005-08-22 2007-06-28 Man Diesel Se Containment-Sicherung für Strömungsmaschinen mit radial durchströmtem Verdichterrad
US7871243B2 (en) 2007-06-05 2011-01-18 Honeywell International Inc. Augmented vaneless diffuser containment

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US20100192570A1 (en) 2010-08-05
US8393851B2 (en) 2013-03-12
KR101157440B1 (ko) 2012-06-22
EP2216517A1 (fr) 2010-08-11
EP2216516A1 (fr) 2010-08-11
CN101793266A (zh) 2010-08-04
JP2010180882A (ja) 2010-08-19
JP5074541B2 (ja) 2012-11-14
KR20100089776A (ko) 2010-08-12
CN101793266B (zh) 2012-07-18

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