EP1356169A1 - Revetement insonorisant double couche et dispositif de pressurisation de fluide ; methode d'utilisation - Google Patents

Revetement insonorisant double couche et dispositif de pressurisation de fluide ; methode d'utilisation

Info

Publication number
EP1356169A1
EP1356169A1 EP01996188A EP01996188A EP1356169A1 EP 1356169 A1 EP1356169 A1 EP 1356169A1 EP 01996188 A EP01996188 A EP 01996188A EP 01996188 A EP01996188 A EP 01996188A EP 1356169 A1 EP1356169 A1 EP 1356169A1
Authority
EP
European Patent Office
Prior art keywords
liner
series
openings
cells
resonators
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.)
Granted
Application number
EP01996188A
Other languages
German (de)
English (en)
Other versions
EP1356169A4 (fr
EP1356169B1 (fr
Inventor
Zheji Liu
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.)
Dresser Rand Co
Original Assignee
Dresser Rand Co
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
Priority claimed from US09/745,862 external-priority patent/US6550574B2/en
Application filed by Dresser Rand Co filed Critical Dresser Rand Co
Publication of EP1356169A1 publication Critical patent/EP1356169A1/fr
Publication of EP1356169A4 publication Critical patent/EP1356169A4/fr
Application granted granted Critical
Publication of EP1356169B1 publication Critical patent/EP1356169B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • This invention relates to an acoustic liner of two layers and a fluid pressurizing device and method utilizing same.
  • Fluid pressurizing devices such as centrifugal compressors
  • centrifugal compressors are widely used in different industries for a variety of applications involving the compression, or pressurization, of a gas.
  • a typical compressor produces a relatively high noise level which is an obvious nuisance to the people in the vicinity of the device. This noise can also cause vibrations and structural failures.
  • the dominant noise source in a centrifugal compressor is typically generated at the locations of the impeller exit and the diffuser inlet, due to the high velocity of the fluid passing tlirough these regions.
  • the noise level becomes higher when discharge vanes are installed in the diffuser to improve pressure recovery, due to the aerodynamic interaction between the impeller and the diffuser vanes.
  • acoustic liners have been developed which are placed in the compressors, or similar devices, for controlling noise inside the gas flow paths.
  • These liners are often based on the well-known Helrnholtz resonator principle according to which the liners dissipate the acoustic energy when the sound waves oscillate through perforations in the liners, and reflect the acoustic energy upstream due to the local impedance mismatch caused by the liner.
  • Helrnholtz resonators are disclosed in U.S. patent Nos. 4,100,993; 4,135,603; 4,150,732; 4,189,027; 4,443,751; 4,944,362; and 5,624,518.
  • a typical Helrnholtz array acoustic liner is in the form of a three-piece sandwich structure consisting of honeycomb cells sandwiched between a perforated facing sheet and a back plate.
  • an acoustic liner is provided, as well as a fluid processing device and method inco orating same, according to which the liner attenuates noise and consists of one or more acoustic liners each including a plurality of cells fo ⁇ ned in a plate in a manner to form an array of resonators.
  • Fig. 1 is a cross-sectional view of a portion of a gas pressurizing device incorporating a pair of acoustic liners according to an embodiment of the present invention.
  • Fig. 2 is an enlarged cross-sectional view of one of the acoustic liners of Fig. 1.
  • Fig. 3 is an enlarged elevational view of a portion of the liner of Fig. 2.
  • Figs. 4 and 5 are views similar to that of Fig. 1, but depicting additional acoustic liners disposed at other locations in the fluid pressurizing device.
  • Fig. 1 depicts a portion of a high pressure fluid pressurizing device, such as a centrifugal compressor, including a casing 10 defining an impeller cavity 10a for receiving an impeller 12 which is mounted for rotation in the cavity. It is understood that a power-driven shaft (not shown) rotates the impeller 12 at a high speed, sufficient to impart a velocity pressure to the gas drawn into the compressor via the inlet.
  • a power-driven shaft (not shown) rotates the impeller 12 at a high speed, sufficient to impart a velocity pressure to the gas drawn into the compressor via the inlet.
  • the impeller 12 includes a plurality of impeller blades 12a arranged axi-symmetrically around the latter shaft for discharging the gas into a diffuser passage, or channel 14 formed in the casing 10 radially outwardly from the chamber 10a and the impeller 12.
  • the channel 14 receives the high pressure fluid from the impeller 12 before it is passed to a volute, or collector,16.
  • the diffuser channel 14 functions to convert the velocity pressure of the gas into static pressure which is coupled to a discharge volute, or collector 16 also formed in the casing and connected with the channel.
  • the discharge volute 16 couples the compressed gas to an outlet of the compressor.
  • a mounting bracket 20 is secured to an inner wall of the casing 10 defining the diffuser channel 14 and includes a base 22 disposed adjacent the outer end portion of the impeller and a plate 24 extending from the base and along the latter wall of the casing.
  • Two one-piece, unitary, annular acoustic liners 28 and 30 are mounted in a groove in the plate 24 of the bracket 20 in a abutting relationship and each is annular in shape and extends around the impeller 12 for 360 degrees.
  • the upper section of the liner 28 is shown in detail in Figs. 2 and 3, and is formed of an annular, relatively thick, unitary shell, or plate 32 preferably made of steel.
  • the plate 32 is attached to the bracket plate 24 in any conventional manner, such as by a plurality of bolts, or the like.
  • a series of relatively large cells, or openings, 34 are formed through one surface of the plate 32 and extend through a majority of the thickness of the plate but not through its entire thickness.
  • a series of relatively small cells 36 extend from the bottom of each cell 34 to the opposite surface of the plate 32.
  • Each cell 34 is shown having a disc-like cross section and each cell 36 is in the form of a bore for the purpose of example, it being understood that the shapes of the cells 34 and 36 can vary within the scope of the invention.
  • each cell 34 is formed by drilling a relative large-diameter counterbore through one surface of the plate 32, which counterbore extends through a majority of the thickness of the plate but not though the complete thickness of the plate.
  • Each cell 36 is formed by drilling a bore, or passage, through the opposite surface of the plate 32 to the bottom of a corresponding cell 34 and thus connects the cell 34 to the diffuser channel 14.
  • the cells 34 are formed in a plurality of annular extending rows along the entire annular area of the plate 32, with the cells 34 of a particular row being staggered, or offset, from the cells of its adjacent row(s).
  • a plurality of cells 36 are associated with each cell 34 and the cells 36 can be randomly disposed relative to their corresponding cell 34, or, alternately, can be formed in any pattern of uniform distribution.
  • the liner 30 is similar to the liner 28 and, as such, is formed of an annular, relatively thick, unitary shell, or plate 42 (Fig. 1), preferably made of steel, and is attached to the liner 28 in any conventional manner such as by a plurality of bolts, or the like.
  • a series of relatively large cells, or openings, 44 are formed through one surface of the plate 42 and a series of relatively small cells 46 extend from the bottom of each cell 34 to the opposite surface of the plate 32. Since the cells 44 and 46 are similar to the cells 34 and 36, respectively, they will not be described in further detail.
  • the liners 30 and 28 can be of different thickness.
  • the liners 28 and 30 are mounted in the bracket plate 24 with the surface of the liner 28 through which the cells 34 extend abutting the surface of the liner 30 through which the cells 46 extend. Also, the cells 34 of the liner 28 are in alignment with the cells 44 of the liner 30. The open ends of the cells 44 of the liner 30 are capped by the underlying wall of the plate 24 of the bracket 20, and the open ends of the cells 34 of the liner 28 are capped by the corresponding surface of the liner 30. The cells 34 of the liner 28 and the cells 44 of the liner 30 are connected by the cells 46 of the liner 30, due to their alignment.
  • the cells work collectively as an array of acoustic resonators in series.
  • the liners 28 and 30 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 28 and 30 so that the maximum sound attenuation occurs around the latter frequency.
  • the liner 48 extends in the bottom of the groove and is connected to the structure forming the groove in any conventional manner, such as by a plurality of bolts, or the like; and the liner 50 extends in the groove in an abutting relationship to the liner 48 and is connected to the liner 48 in any conventional manner, such as by a plurality of bolts, or the like.
  • the liner 50 partially defines, with the liner 30, the diffuser channel 14. Since the liners 48 and 50 are similar to, and functions the same as, the liners 28 and 30, they will not be described in any further detail.
  • the cells Due to the firm contact between the liners 48 and 50, and between the liner 48 and the corresponding wall of the casing 10, and due to the arrangement of the respective cells of the liners, the cells work collectively as arrays of acoustic resonators in series.
  • the liners 48 and 50 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass tlirough a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 48 and 50 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 48 and 50 enables them to attentuate noise in a much wider frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • two one-piece, unitary, annular liners 54 and 56 are mounted in a groove formed in the casing 10 to the rear of the impeller 12.
  • the liner 54 extends in the bottom of the groove and is connected to the structure forming the groove in any conventional manner, such as by a plurality of bolts, or the like; and the liner 56 extends in the groove in an abutting relationship to the liner 54 and is connected to the liner 54 in any conventional manner, such as by a plurality of bolts, or the like.
  • the liner 56 partially defines, with the liner 52, the chamber in which the impeller 12 rotates.
  • the liners 54 and 56 have a smaller outer diameter than the liners 28, 30, 48 and 50, but otherwise are similar to, and are mounted in the same manner as, the latter liners.
  • the cells Due to the firm contact between the liners 54 and 56, and between the liner 54 and the corresponding wall of the casing 10, and due to the arrangement of the respective cells of the liners, the cells work collectively as arrays of acoustic resonators in series. As such, the liners 54 and 56 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 54 and 56 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 54 and 56 enables them to attenuate noise in a broader frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • FIG. 5 depicts an inlet conduit 60 that introduces gas to the inlet of the impeller 12.
  • the upper portion of the conduit 60 is shown extending above the centerline C/L of the conduit and the casing 10, as viewed in Fig.
  • a one-piece, unitary, liner 64 is flush-mounted on the inner wall of the conduit 60 with the radial outer portion being shown.
  • the liner 64 is in the form of a curved shell, preferably cylindrical or conical in shape, is disposed in an annular groove formed in the inner surface of the conduit 60, and is secured in the groove in any known manner. Since the liner 64 is otherwise similar to the liners 28, 30, 48, 50, 52, 54, and 56, it will not be described in further detail.
  • a one-piece, unitary, liner 66 is also disposed in the latter annular groove and extends around the liner 64 with its inner surface abutting the outer surface of the liner 64.
  • the liner 66 is in the form of a curved shell, preferably cylindrical or conical in shape having a diameter larger than the diameter of the liner 64 and is secured to the liner 64 in any conventional manner, such as by a plurality of bolts, or the like. Since the liners 64 and 66 are otherwise similar to the liners 28, 30, 48, 50, 52, 54, and 56, and function in the same manner to significantly reduce the noise in the casing 10, they will not be described in further detail.
  • the cells Due to the firm contact between the liners 64 and 66, and between the liner 66 and the corresponding wall of the casing 10 defining the latter groove, and due to the arrangement of the respective cells of the liners, and their location relative the inlet conduit 60, the cells work collectively as arrays of acoustic resonators in series.
  • the liners 64 and 66 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will bypass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 64 and 66 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 64 and 66 enables them to attenuate noise in a broader frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • the number of the smaller cells per each larger cell of each liner can be varied spatially across the liners so that the entire liner is effective to attenuate noise in a broader frequency band. Consequently, the liners 28, 30, 48, 50, 52, 54, 56, 64, and 66 can efficiently and effectively attenuate noise, not just in constant speed machines, but also in variable speed compressors, or other fluid pressurizing devices.
  • the one-piece unitary construction of the liners in the above embodiments renders the liners mechanically stronger when compared to the composite designs discussed above.
  • the liners provide a very rigid inner wall to the internal flow in the fluid pressurizing device, and have less or no deformation when subject to mechanical and thermal loading, and thus have no adverse effect on the aerodynamic performance of a fluid pressurizing device, such as a centrifugal compressor, even when they are installed in the narrow passages such as the diffusor channels, or the like.
  • liners in accordance with the above embodiments are not limited to the number shown.
  • the liners to either side of the diffuser channel and/or the impeller and/or the inlet conduit.
  • a one-piece liner can be formed in which the cells are molded in their respective plates.
  • the relative dimensions, shapes, numbers and the pattern of the cells of each liner can vary.
  • the liners are not limited to use with a centrifugal compressor, but are equally applicable to other fluid pressurizing devices in which aerodynamic effects are achieved with movable blades.
  • Each liner can extend for degrees around the axis of the impeller and the inlet conduit as disclosed above; or each liner can be formed into segments which extend an angular distance less than 360 degrees.
  • the spatial references used above, such as “bottom”, “inner”, “outer”, “side” etc, are for the purpose of illustration only and do not limit the specific orientation or location of the structure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Abstract

Cette invention concerne un revêtement acoustique double couche (28) permettant d'abaisser le niveau phonique, qui comprend une pluralité de cellules (34) formées dans une plaque (32) de manière à constituer un ensemble de résonateurs, ainsi qu'un dispositif et un procédé de traitement de fluide intégrant un tel revêtement acoustique.
EP01996188A 2000-12-21 2001-11-08 Revetement insonorisant double couche et dispositif de pressurisation de fluide Expired - Lifetime EP1356169B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US745862 2000-12-21
US09/745,862 US6550574B2 (en) 2000-12-21 2000-12-21 Acoustic liner and a fluid pressurizing device and method utilizing same
US929193 2001-08-14
US09/929,193 US6601672B2 (en) 2000-12-21 2001-08-14 Double layer acoustic liner and a fluid pressurizing device and method utilizing same
PCT/US2001/047515 WO2002052110A1 (fr) 2000-12-21 2001-11-08 Revetement insonorisant double couche et dispositif de pressurisation de fluide ; methode d'utilisation

Publications (3)

Publication Number Publication Date
EP1356169A1 true EP1356169A1 (fr) 2003-10-29
EP1356169A4 EP1356169A4 (fr) 2004-10-13
EP1356169B1 EP1356169B1 (fr) 2006-06-14

Family

ID=27114526

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01996188A Expired - Lifetime EP1356169B1 (fr) 2000-12-21 2001-11-08 Revetement insonorisant double couche et dispositif de pressurisation de fluide

Country Status (6)

Country Link
EP (1) EP1356169B1 (fr)
JP (1) JP4088155B2 (fr)
CN (1) CN1318710C (fr)
CA (1) CA2432094C (fr)
DE (2) DE01996188T1 (fr)
WO (1) WO2002052110A1 (fr)

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EP3730803A1 (fr) * 2019-04-26 2020-10-28 Garrett Transportation I Inc. Turbocompresseur doté d'un compresseur centrifuge à garniture réglable comprenant une paroi d'entrée d'air comportant des cavités pour la suppression des fluctuations de bruit et de flux

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US9301519B2 (en) 2004-10-07 2016-04-05 Transmedics, Inc. Systems and methods for ex-vivo organ care
US8304181B2 (en) 2004-10-07 2012-11-06 Transmedics, Inc. Method for ex-vivo organ care and for using lactate as an indication of donor organ status
CA2584066C (fr) 2004-10-07 2018-01-23 Transmedics, Inc. Systemes et procedes de soins a des organes ex vivo
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US9078428B2 (en) 2005-06-28 2015-07-14 Transmedics, Inc. Systems, methods, compositions and solutions for perfusing an organ
ES2625850T3 (es) 2006-04-19 2017-07-20 Transmedics, Inc. Procedimientos para el cuidado de órganos ex vivo
US9457179B2 (en) 2007-03-20 2016-10-04 Transmedics, Inc. Systems for monitoring and applying electrical currents in an organ perfusion system
DE102007019884A1 (de) 2007-04-27 2008-11-06 Bayerische Motoren Werke Aktiengesellschaft Verdichter für einen Abgasturbolader
DE102007028742A1 (de) * 2007-06-21 2008-12-24 Daimler Ag Luftversorger, insbesondere für ein Luftversorgungssystem von Brennstoffzellen
US10750738B2 (en) 2008-01-31 2020-08-25 Transmedics, Inc. Systems and methods for ex vivo lung care
GB2468153A (en) * 2009-02-27 2010-09-01 Dyson Technology Ltd A silencing arrangement
CN102102663A (zh) * 2009-12-22 2011-06-22 沈阳申元气体压缩机厂 脉动衰减器
DE102011005025A1 (de) 2011-03-03 2012-09-06 Siemens Aktiengesellschaft Resonatorschalldämpfer für eine radiale Strömungsmaschine, insbesondere für einen Radialverdichter
DK2704560T3 (da) 2011-04-14 2022-05-23 Transmedics Inc Organbehandlingsopløsning til maskinperfusion ex-vivo af donorlunger
US8955643B2 (en) 2011-04-20 2015-02-17 Dresser-Rand Company Multi-degree of freedom resonator array
CN103498818A (zh) * 2013-09-06 2014-01-08 乐金空调(山东)有限公司 离心式压缩机消音装置
US9343059B2 (en) * 2013-09-24 2016-05-17 Board Of Regents, The University Of Texas System Underwater noise abatement panel and resonator structure
EP3151663B1 (fr) 2014-06-02 2020-09-23 Transmedics, Inc. Système de soins d'organes ex vivo
EP3229588A4 (fr) 2014-12-12 2019-03-13 Freed, Darren Appareil et procédé de perfusion d'organe
JP6934005B2 (ja) 2015-09-09 2021-09-08 トランスメディクス，インコーポレイテッド エキソビボ臓器管理システムのための大動脈カニューレ
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CN115076129B (zh) * 2022-06-23 2023-04-07 西安交通大学 一种具有自适应降噪功能的离心机扩压器

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EP3730803A1 (fr) * 2019-04-26 2020-10-28 Garrett Transportation I Inc. Turbocompresseur doté d'un compresseur centrifuge à garniture réglable comprenant une paroi d'entrée d'air comportant des cavités pour la suppression des fluctuations de bruit et de flux

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EP1356169A4 (fr) 2004-10-13
JP4088155B2 (ja) 2008-05-21
WO2002052110A1 (fr) 2002-07-04
DE60120769T2 (de) 2007-05-24
CN1489662A (zh) 2004-04-14
EP1356169B1 (fr) 2006-06-14
CN1318710C (zh) 2007-05-30
DE60120769D1 (de) 2006-07-27
CA2432094A1 (fr) 2002-07-04
JP2004525290A (ja) 2004-08-19
DE01996188T1 (de) 2005-07-14
CA2432094C (fr) 2010-07-27

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