EP2063130A1 - Dispositif d'atténuation de bruit pour un compresseur centrifuge - Google Patents

Dispositif d'atténuation de bruit pour un compresseur centrifuge Download PDF

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Publication number
EP2063130A1
EP2063130A1 EP07022502A EP07022502A EP2063130A1 EP 2063130 A1 EP2063130 A1 EP 2063130A1 EP 07022502 A EP07022502 A EP 07022502A EP 07022502 A EP07022502 A EP 07022502A EP 2063130 A1 EP2063130 A1 EP 2063130A1
Authority
EP
European Patent Office
Prior art keywords
centrifugal compressor
resonator
suction nozzle
compressor discharge
side resonator
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Withdrawn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
EP07022502A
Other languages
German (de)
English (en)
Inventor
Chiel Schoeman
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Priority to EP07022502A priority Critical patent/EP2063130A1/fr
Priority to PCT/EP2008/065934 priority patent/WO2009065904A1/fr
Priority to EP08851643A priority patent/EP2209997A1/fr
Priority to US12/743,578 priority patent/US20100278635A1/en
Publication of EP2063130A1 publication Critical patent/EP2063130A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D29/66—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

Definitions

  • the invention relates to a centrifugal compressor discharge or suction nozzle, a centrifugal compressor discharge or suction nozzle formed as a pipe section piece adapted to be mounted on a centrifugal compressor nozzle, a centrifugal compressor comprising the centrifugal compressor discharge or suction nozzle, and a centrifugal compressor arrangement comprising the centrifugal compressor.
  • centrifugal compressor In chemical and petrochemical plants a centrifugal compressor is commonly used for pressurising process gas.
  • the centrifugal compressor comprises at least one suction nozzle and at least one discharge nozzle, wherein said nozzles are connected to plant piping. Through the suction nozzle process gas flows into the centrifugal compressor to be compressed therein. The compressed process gas exits the centrifugal compressor through the discharge nozzle to be delivered to downstream plant components.
  • the centrifugal compressor comprises at least one rotor with at least one impeller. Downstream of the impeller the centrifugal compressor comprises a diffuser. The impeller and the diffuser are aerodynamically effective to compress the process gas. During operation of the compressor the rotor rotates thereby generating noise.
  • the noise is a combination of discrete frequency noise (tonal noise) related to the so-called blade passing frequency and its higher harmonics.
  • the noise generates a high noise exposure of the environment and can cause structural failures of the centrifugal compressor and the piping due to vibration cracking.
  • a remedy to reduce the noise intensity level of the centrifugal compressor is to cover the centrifugal compressor with a noise hood.
  • the noise hood is able to reduce the noise exposure of the environment.
  • the noise-hood is cost-intensive and needs to be taken into consideration with respect to space requirement being problematic in a plant with limited space.
  • Another remedy to reduce the noise intensity level of the centrifugal compressor is to provide the downstream piping of the centrifugal compressor with a piping silencer.
  • the piping silencer is flown through by the process gas and therefore induces a high flow resistance resulting in an adverse pressure loss.
  • the piping silencer is costly in construction and large in geometrical dimensions.
  • the centrifugal compressor discharge or suction nozzle comprises at least one side resonator integrally formed in the centrifugal compressor discharge or suction nozzle.
  • the centrifugal compressor discharge or suction nozzle is formed as a pipe section piece adapted to be mounted on a centrifugal compressor nozzle, comprising at least one side resonator integrated into the pipe section piece.
  • various stacked rings can be installed forming one or more side resonator(s).
  • the centrifugal compressor comprises the centrifugal compressor discharge or suction nozzle.
  • the centrifugal compressor arrangement comprises the centrifugal compressor.
  • the process gas discharging the centrifugal compressor is interfered by tonal noise generated within the centrifugal compressor during its operation at a specific frequency band.
  • the tonal noise is related to the so-called blade passing frequency and its higher harmonics.
  • the discharge or suction nozzle of the centrifugal compressor comprises the side resonator(s), whereby the side resonator(s) is (are) in direct cooperation with the discharge or inlet process gas. Since the side resonator(s) is (are) appropriate to reduce the tonal noise by the effects of acoustic impedance, the side resonator(s) act(s) like an acoustic mirror at the specific frequency band of the tonal noise.
  • the geometrical dimensions of the side resonator(s) determine the frequency band in which the resonator(s) is (are) active. Therefore, it is possible to attenuate the frequency band in which the blade passing frequency is active. As a consequence of this, during operation of the centrifugal compressor, its noise emission level is lower.
  • the process gas passes the side resonator without disturbing the process gas flow in the discharge or suction nozzle. Therefore, the side resonator includes very low or even less flow resistance to the process gas discharge or suction flow. Hence, a side resonator does not cause any significant pressure loss in the process gas discharge or suction flow.
  • the process gas discharge or suction flow is noise attenuated by the side resonator(s). Consequently, the centrifugal compressor comprising the side resonator has a high energy efficiency.
  • the side resonator(s) is (are) integrated in the pipe section piece, such that advantageously the centrifugal compressor can be equipped with the side resonator(s) subsequent to its assembly.
  • different types of side resonators can be provided for the centrifugal compressor in replacing the pipe section piece provided with different side resonators, and the pipe section piece can be designed as an universal section which can be mounted on any centrifugal compressor.
  • various rings can be stacked in between the nozzle piping connection forming one or more resonators that can be fitted to any compressor.
  • the centrifugal compressor Since the side resonator is integrally formed in the discharge or suction nozzle and in the pipe section piece, respectively, the centrifugal compressor has a compact design, which is easy and cost saving to be manufactured.
  • the compressor discharge or suction nozzle comprises a plurality of side resonators located after each other. This enlarges the frequency band in which the noise is attenuated and makes the solution most robust.
  • Each side resonator is capable to reduce a specific frequency. Therefore, by providing a plurality of side resonators after each other, wherein each side resonator can be adapted to reduce another specific frequency, the frequency band in which the plurality of side resonators is effective to reduce the tonal noise, is broadened. This is the reason why the inventive centrifugal compressor is silenced in an effective way by means of the plurality of side resonators.
  • the pipe section piece comprises a plurality of ring elements having different inner diameters and concentrically adjoining each other, and at least one flange element facing the plurality of ring elements, wherein the plurality of ring elements form the side resonator(s).
  • the ring elements preferably can be formed by universal rings. Further, preferably standard flange elements can be used, such that manufacturing costs of the pipe section piece are low.
  • the side resonator consists of a single tube resonator.
  • the side resonator comprises an array of single tube resonators circumferentially distributed.
  • the side resonator comprises a circular resonator.
  • the side resonator comprises a cylindrical resonator.
  • the side resonator comprises an eccentrically formed cylindrical resonator.
  • the side resonator is a Helmholtz resonator.
  • the side resonator consists of a single Helmholtz resonator.
  • the side resonator comprises an array of single Helmholtz resonators circumferentially distributed.
  • the side resonator comprises a circular Helmholtz resonator.
  • the side resonator is adapted to have self cleaning properties.
  • the self cleaning properties can be generated either by using gravity or by having a secondary vortex flow.
  • the centrifugal compressor arrangement comprises the centrifugal compressor, wherein the side resonator comprises a liquid injection device for liquid injection into the side resonator for cleaning thereof.
  • the centrifugal compressor arrangement comprises a gas scrubber provided upstream of the centrifugal compressor and a bypass line from the side resonator to the gas scrubber for bypassing the process gas or the liquid from the side resonator to the gas scrubber.
  • bypass line comprises a bypass valve
  • each centrifugal compressor nozzle comprises a side resonator 2 to 9 which is integrally formed in the centrifugal compressor nozzle 1.
  • the side resonator according to Fig. 1, 2 consists of a single tube resonator 2.
  • the single tube resonator 2 is comprised by a cylindrical cavity.
  • the cavity is formed by a hollow cylinder body perpendicularly protruding from the compressor nozzle 1 and being delimited by a bottom of the cylinder body at its end opposing the centrifugal compressor nozzle, wherein the cavity is in communication with the interior of the compressor nozzle 1.
  • the side resonator according to Fig. 3 is an array 3 of the single tube resonators 2 which are circumferentially distributed at the centrifugal compressor nozzle 1.
  • the single tube resonators 2 forming the array side resonator 3 are arranged equally spaced such that the acoustic effect of the array side resonator 3 is circumferentially uniform.
  • the side resonator according to Fig. 4 comprises a circular resonator 4.
  • the circular resonator 4 is a disc-shaped cavity encompassing the centrifugal compressor nozzle 1.
  • the side resonator according to Fig. 5, 6 comprises a cylindrical resonator 5.
  • the cylindrical resonator 5 is formed like the circular resonator 4, but with an L-shaped cross section in longitudinal direction of the centrifugal compressor nozzle 1.
  • the side resonator do not need to be rotation symmetric but can comprise an eccentrically formed cylindrical resonator 6.
  • Examples of the eccentrically formed cylindrical resonator 6 are shown in Fig. 7 to 14 .
  • the eccentrically formed cylindrical resonator 6 according to Fig. 7, 8 is formed like the circular resonator 4, but with a varying inner diameter over the circumference of the centrifugal compressor nozzle 1.
  • the eccentrically formed cylindrical resonator 6 according to Fig. 1 , 10 has a square cross section.
  • the eccentrically formed cylindrical resonator 6 according to Fig. 11, 12 has a cross section formed as an equilateral triangle.
  • the eccentrically formed cylindrical resonator 6 according to Fig. 13, 14 has a cross section elliptically formed.
  • the side resonators 7 to 9 are of Helmholtz side resonator type.
  • the side resonator according to Fig. 15 consists of a single Helmholtz resonator 7.
  • the single Helmholtz resonator 7 is comprised by a cylindrical cavity.
  • the cavity is in communication with the interior of the compressor nozzle 1 and comprises an enlargement opposing the centrifugal compressor nozzle 1.
  • the side resonator according to Fig. 16 comprises an array 8 of the single Helmholtz resonators 7 provided circumferentially distributed.
  • the single Helmholtz resonators 7 are arranged equally spaced such that the acoustic effect of the array Helmholtz resonator 8 is circumferentially uniform.
  • the side resonator according to Fig. 17 comprises a circular Helmholtz resonator 9.
  • the circular Helmholtz resonator 9 is a disc-shaped cavity encompassing the centrifugal compressor nozzle 1, wherein the cavity comprises an enlargement opposing the centrifugal compressor nozzle 1.
  • Fig. 18 to 20 show a pipe section piece 10.
  • the pipe section piece 10 is adapted to be mounted on a centrifugal compressor nozzle. Therefore, when the pipe section piece is mounted on the centrifugal compressor nozzle, process gas entering or discharging the centrifugal compressor passes through the pipe section piece 10.
  • Fig. 18 to 20 show one of many possible variants of the pipe section piece 10.
  • the pipe piece section 10 is integrally formed and comprises a pipe 11 and two flanges 12 provided on the longitudinal ends of the pipe 11.
  • the flanges 12 are adapted to be fitted to the centrifugal compressor nozzle.
  • the pipe 11 has an inner diameter 15.
  • each circular resonator 4 to 4 4" has an inner diameter 13 to 13'', respectively, being greater than the inner diameter 15 of the pipe 11, wherein the inner diameter 13 is smaller than the inner diameter 13', and the inner diameter 13' is smaller than the inner diameter 13".
  • the circular resonators 4 to 4'' are arranged side by side such that the pipe piece section is acoustically effective for a broad frequency band.
  • the body of the pipe section piece 10 according to Fig. 18 is formed as a hollow cylinder.
  • the pipe section piece 10 according to Fig. 20 is flexible and formed like a bellow or a diaphragm coupling. Therefore, the pipe section piece 10 can reduce compressor casing / piping forces and moments. Hence, allowable nozzle movements are larger.
  • the number and shape of the resonators 4 to 4'' can be varied depending on the desired acoustic characteristic of the pipe section piece 10.
  • Fig. 18 and 19 i designates the number of resonators
  • 0 designates the diameter of the resonator i
  • t i designates the width of the resonator i
  • L i designates the distance between the resonator i and the resonator i+1.
  • the pipe piece section 10 according to Fig. 19 is similar to the pipe piece section 10 according to Fig. 18 and 20 , but comprises seven individual ring elements 14, 14', 14'', 14''', 14 IV , 14 V , 14 VI .
  • the inner diameter of the ring elements 14, 14'' 14 IV , 14 VI equals the inner diameter 15 of the pipe 11.
  • the ring elements 14', 14''', 14 V have different inner diameters 13 to 13'' and are concentrically adjoined together.
  • the pipe piece section 10 according to Fig. 19 comprises two flange elements 12 facing the ring elements 14, 14', 14'', 14''', 14 IV , 14 V , 14 VI for being adapted to be mountable to a centrifugal compressor nozzle.
  • the seven ring elements 14, 14', 14'', 14''', 14 IV , 14 V , 14 VI are stacked and form the circular resonators 4, 4', 4''. Any other number of ring elements 14, 14', 14'', 14''', 14 IV , 14 V , 14 VI is possible.
  • Fig. 20 shows a centrifugal compressor arrangement comprising a centrifugal compressor 21 comprising the centrifugal compressor nozzle 1.
  • the centrifugal compressor nozzle 1 comprises the circular resonators 4 and 4'.
  • the centrifugal compressor nozzle 1 comprises a wash water injection device 28 for wash water injection into the side resonators 4 and 4' for cleaning thereof.
  • the centrifugal compressor arrangement 20 comprises a gas scrubber 24 provided upstream of the centrifugal compressor 21 and a bypass line 29 from the centrifugal compressor nozzle 1 to the gas scrubber 24.
  • the bypass line 29 comprises a bypass valve 30 for controlling the bypassed gas flow. Additionally, wash water is fed back to the scrubber 24 via the bypass line 29.
  • Fig.22, 23 show views of the first embodiment according to Fig. 1, 2 having self cleaning properties.
  • the single tube resonator 2 is thread-like arranged on the compressor nozzle

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP07022502A 2007-11-20 2007-11-20 Dispositif d'atténuation de bruit pour un compresseur centrifuge Withdrawn EP2063130A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP07022502A EP2063130A1 (fr) 2007-11-20 2007-11-20 Dispositif d'atténuation de bruit pour un compresseur centrifuge
PCT/EP2008/065934 WO2009065904A1 (fr) 2007-11-20 2008-11-20 Dispositif d'atténuation de bruit pour une buse de décharge ou d'aspiration de compresseur centrifuge
EP08851643A EP2209997A1 (fr) 2007-11-20 2008-11-20 Dispositif d'atténuation de bruit pour une buse de décharge ou d'aspiration de compresseur centrifuge
US12/743,578 US20100278635A1 (en) 2007-11-20 2008-11-20 Noise attenuation device for a centrifugal compressor discharge or suction nozzle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07022502A EP2063130A1 (fr) 2007-11-20 2007-11-20 Dispositif d'atténuation de bruit pour un compresseur centrifuge

Publications (1)

Publication Number Publication Date
EP2063130A1 true EP2063130A1 (fr) 2009-05-27

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP07022502A Withdrawn EP2063130A1 (fr) 2007-11-20 2007-11-20 Dispositif d'atténuation de bruit pour un compresseur centrifuge
EP08851643A Withdrawn EP2209997A1 (fr) 2007-11-20 2008-11-20 Dispositif d'atténuation de bruit pour une buse de décharge ou d'aspiration de compresseur centrifuge

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP08851643A Withdrawn EP2209997A1 (fr) 2007-11-20 2008-11-20 Dispositif d'atténuation de bruit pour une buse de décharge ou d'aspiration de compresseur centrifuge

Country Status (3)

Country Link
US (1) US20100278635A1 (fr)
EP (2) EP2063130A1 (fr)
WO (1) WO2009065904A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011005025A1 (de) * 2011-03-03 2012-09-06 Siemens Aktiengesellschaft Resonatorschalldämpfer für eine radiale Strömungsmaschine, insbesondere für einen Radialverdichter
JP2013527382A (ja) * 2010-06-04 2013-06-27 ボーグワーナー インコーポレーテッド 排気ガスターボチャージャのコンプレッサ
GB2546538A (en) * 2016-01-21 2017-07-26 Gm Global Tech Operations Llc A compressor housing
WO2017134125A1 (fr) * 2016-02-05 2017-08-10 Universite De Bourgogne Resonateur acoustique de faible epaisseur de type mille-feuille perfore pour l'absorption ou le rayonnement acoustique tres basses frequences
CN107035484A (zh) * 2017-06-22 2017-08-11 广西壮族自治区环境保护科学研究院 一种汽车尾气净化装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9169750B2 (en) * 2013-08-17 2015-10-27 ESI Energy Solutions, LLC. Fluid flow noise mitigation structure and method

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB489114A (en) * 1937-01-22 1938-07-20 Francois Cementation Co Ltd Improvements in or relating to silencers for flowing gases
US2514998A (en) * 1948-02-16 1950-07-11 Fundom Earl Henry Silencer
DE1814146A1 (de) 1967-12-13 1969-07-10 Teem Inc Ab Schalldaempfer
US3472001A (en) * 1967-11-01 1969-10-14 American Air Filter Co Gas intake device
GB2259327A (en) * 1991-09-06 1993-03-10 Bosch Gmbh Robert Sound damper for a blower air intake
EP0573895A1 (fr) * 1992-06-12 1993-12-15 A.G. Kühnle, Kopp & Kausch Turbocompresseur avec un compresseur radial
DE29715710U1 (de) * 1997-09-02 1997-10-23 Intensiv-Filter Gmbh & Co Kg, 42555 Velbert Reinigungsvorrichtung für einen Industrieschalldämpfer
FR2780454A1 (fr) * 1998-06-29 1999-12-31 Valeo Climatisation Dispositif d'absorption de bruit pour groupe moto-ventilateur centrifuge
DE19956172A1 (de) * 1999-11-23 2001-05-31 Umfotec Umformtechnik Gmbh Doppelkammerdämpfer
US20020144683A1 (en) * 2001-02-28 2002-10-10 Hyperbaric Technology, Inc. Hyperbaric oxygen therapy system controls
EP1291570A2 (fr) * 2001-09-07 2003-03-12 Avon Polymer Products Limited Amortisseur de bruit et de vibrations
US6575696B1 (en) 2000-09-21 2003-06-10 Fasco Industries, Inc. Method of sound attenuation in centrifugal blowers
WO2005124159A1 (fr) * 2004-06-15 2005-12-29 Honeywell International Inc. Element insonorisant integre a un carter de compresseur
DE102004057413A1 (de) * 2004-11-26 2006-06-29 Mahle Filtersysteme Gmbh Schalldämpfer für eine Brennkraftmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5088886A (en) * 1990-08-28 1992-02-18 Sinko Kogyo Co., Ltd. Inlet air flow conditioning for centrifugal fans
AU635867B2 (en) * 1990-10-22 1993-04-01 Hitachi Automotive Engineering Co., Ltd. Centrifugal fan with noise suppressing arrangement
US6039532A (en) * 1996-07-18 2000-03-21 Iowa State University Research Foundation, Inc. Blower fan blade passage rate noise control scheme
ITVI20020145A1 (it) * 2002-07-02 2004-01-02 Comefri Spa Ripartitore antirumore e antivortice
US7883312B2 (en) * 2005-03-31 2011-02-08 Mitsubishi Heavy Industries, Ltd. Centrifugal blower

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB489114A (en) * 1937-01-22 1938-07-20 Francois Cementation Co Ltd Improvements in or relating to silencers for flowing gases
US2514998A (en) * 1948-02-16 1950-07-11 Fundom Earl Henry Silencer
US3472001A (en) * 1967-11-01 1969-10-14 American Air Filter Co Gas intake device
DE1814146A1 (de) 1967-12-13 1969-07-10 Teem Inc Ab Schalldaempfer
GB2259327A (en) * 1991-09-06 1993-03-10 Bosch Gmbh Robert Sound damper for a blower air intake
EP0573895A1 (fr) * 1992-06-12 1993-12-15 A.G. Kühnle, Kopp & Kausch Turbocompresseur avec un compresseur radial
DE29715710U1 (de) * 1997-09-02 1997-10-23 Intensiv-Filter Gmbh & Co Kg, 42555 Velbert Reinigungsvorrichtung für einen Industrieschalldämpfer
FR2780454A1 (fr) * 1998-06-29 1999-12-31 Valeo Climatisation Dispositif d'absorption de bruit pour groupe moto-ventilateur centrifuge
DE19956172A1 (de) * 1999-11-23 2001-05-31 Umfotec Umformtechnik Gmbh Doppelkammerdämpfer
US6575696B1 (en) 2000-09-21 2003-06-10 Fasco Industries, Inc. Method of sound attenuation in centrifugal blowers
US20020144683A1 (en) * 2001-02-28 2002-10-10 Hyperbaric Technology, Inc. Hyperbaric oxygen therapy system controls
EP1291570A2 (fr) * 2001-09-07 2003-03-12 Avon Polymer Products Limited Amortisseur de bruit et de vibrations
WO2005124159A1 (fr) * 2004-06-15 2005-12-29 Honeywell International Inc. Element insonorisant integre a un carter de compresseur
DE102004057413A1 (de) * 2004-11-26 2006-06-29 Mahle Filtersysteme Gmbh Schalldämpfer für eine Brennkraftmaschine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013527382A (ja) * 2010-06-04 2013-06-27 ボーグワーナー インコーポレーテッド 排気ガスターボチャージャのコンプレッサ
DE102011005025A1 (de) * 2011-03-03 2012-09-06 Siemens Aktiengesellschaft Resonatorschalldämpfer für eine radiale Strömungsmaschine, insbesondere für einen Radialverdichter
CN103403359A (zh) * 2011-03-03 2013-11-20 西门子公司 用于径流式流体机械特别是用于径流式压缩机的谐振消音器
US9086002B2 (en) 2011-03-03 2015-07-21 Siemens Aktiengesellschaft Resonator silencer for a radial flow machine, in particular for a radial compressor
CN103403359B (zh) * 2011-03-03 2016-12-14 西门子公司 用于径流式压缩机的谐振消音器
GB2546538A (en) * 2016-01-21 2017-07-26 Gm Global Tech Operations Llc A compressor housing
CN106988998A (zh) * 2016-01-21 2017-07-28 通用汽车环球科技运作有限责任公司 压缩机壳体
US10443614B2 (en) 2016-01-21 2019-10-15 GM Global Technology Operations LLC Compressor housing
WO2017134125A1 (fr) * 2016-02-05 2017-08-10 Universite De Bourgogne Resonateur acoustique de faible epaisseur de type mille-feuille perfore pour l'absorption ou le rayonnement acoustique tres basses frequences
CN108885863A (zh) * 2016-02-05 2018-11-23 勃艮第大学 用于吸收或辐射非常低的声波频率的小厚度穿孔多层结构式声学谐振器
CN107035484A (zh) * 2017-06-22 2017-08-11 广西壮族自治区环境保护科学研究院 一种汽车尾气净化装置
CN107035484B (zh) * 2017-06-22 2023-04-25 广西壮族自治区环境保护科学研究院 一种汽车尾气净化装置

Also Published As

Publication number Publication date
US20100278635A1 (en) 2010-11-04
EP2209997A1 (fr) 2010-07-28
WO2009065904A1 (fr) 2009-05-28

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