US20040069563A1 - Silencer with a plurality of resonance chambers - Google Patents

Silencer with a plurality of resonance chambers Download PDF

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Publication number
US20040069563A1
US20040069563A1 US10/466,722 US46672203A US2004069563A1 US 20040069563 A1 US20040069563 A1 US 20040069563A1 US 46672203 A US46672203 A US 46672203A US 2004069563 A1 US2004069563 A1 US 2004069563A1
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United States
Prior art keywords
sound absorber
hollow body
absorber according
helmholtz resonators
sound
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.)
Abandoned
Application number
US10/466,722
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English (en)
Inventor
Thomas Zirkelbach
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.)
Mahle Filtersysteme GmbH
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Mahle Filtersysteme GmbH
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7670911&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US20040069563(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Mahle Filtersysteme GmbH filed Critical Mahle Filtersysteme GmbH
Assigned to MAHLE FILTERSYSTEME GMBH reassignment MAHLE FILTERSYSTEME GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZIRKELBACK, THOMAS
Publication of US20040069563A1 publication Critical patent/US20040069563A1/en
Assigned to MAHLE FILTERSYSTEME GMBH reassignment MAHLE FILTERSYSTEME GMBH CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNOR'S NAME PREVIOUSLY RECORDED ON REEL 014721, FRMAE 0478. ASSIGNOR HEREBY CONFIRMS THE ASSIGNMENT OF THE ENTIRE INTEREST. Assignors: ZIRKELBACH, THOMAS
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/026—Annular resonance chambers arranged concentrically to an exhaust passage and communicating with it, e.g. via at least one opening in the exhaust passage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/009—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more separate purifying devices arranged in series
    • F01N13/0097—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more separate purifying devices arranged in series the purifying devices are arranged in a single housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/011—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more purifying devices arranged in parallel
    • F01N13/017—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more purifying devices arranged in parallel the purifying devices are arranged in a single housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1205—Flow throttling or guiding
    • F02M35/1216—Flow throttling or guiding by using a plurality of holes, slits, protrusions, perforations, ribs or the like; Surface structures; Turbulence generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1261—Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1266—Intake silencers ; Sound modulation, transmission or amplification using resonance comprising multiple chambers or compartments
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/14—Combined air cleaners and silencers

Definitions

  • the invention relates to a sound absorber on or in a component, in which sound to be absorbed, in particular, airborne sound, is dispersed.
  • Sound absorbers are used in internal combustion engines, for example, for reducing noise emissions into the surrounding environment.
  • mufflers are arranged in an exhaust tract of an internal combustion engine, in order to lessen the sound produced and dispersed from the internal combustion engine.
  • sound absorbers are used in the fresh air tract of the internal combustion engine, in order, for example, to lessen the sound produced by an exhaust turbocharger in an engine utilizing such a turbocharger and to lessen the sound dispersed in the fresh air tract.
  • shunt resonators For damping sound which is dispersed in a line, so-called “shunt resonators” or “Helmholtz resonators” are known.
  • Helmholtz resonator essentially comprises a hollow chamber, which communicates with the interior of a line via a connection opening, in which the sound to be damped disperses, whereby the remainder of hollow chamber is closed.
  • the gas volume enclosed in the hollow chamber operates thereby as a “spring” and the gas volume in the connection opening operates as a “mass”, whereby a vibratory system is formed.
  • This vibration system can be stimulated into vibration by means of sound waves, whereby the sound wave energy is canceled, that is, the sound is damped.
  • the damping effect of such a Helmholtz resonator is limited to a predetermined frequency or to a predetermined frequency band.
  • the frequency or frequency band with which the Helmholtz resonator utilizes its damping effect depends, for example, on the geometry, the cross section, the length, and therefore, the volume of the hollow chamber, as well as the connection opening of the Helmholtz resonator.
  • a Helmholtz resonator can best utilize its damping action if it is positioned on the line, such that its connection opening communicates accurately with the interior of the line there, where an antinode of a vertical sound wave of that frequency has formed, which is to be damped by the Helmholtz resonator.
  • any positions are provided in which a vertical sound wave can form.
  • the exact position of an antinode can be calculated with predetermined frequency.
  • the Helmholtz resonator must be connected as precisely as possible to the calculated position on the line.
  • the band width of the frequency to be damped by the sound absorber equipped with a common Helmholtz resonator is very narrow, so that only peaks of a level of a predetermined frequency can be absorbed.
  • the present invention is concerned with the problem of providing an embodiment for a sound absorber of the above-described type, which can be relatively easily mounted and/or can be integrated, and thereby enables a high quenching action.
  • a sound absorber should be provided, which has an improved quenching action and, in particular, has an increased broad-band action.
  • the sound absorber should be able to be manufactured in a particularly cost-effective manner.
  • the invention relates to the general idea of equipping a sound absorber with multiple, in particular, with a plurality of Helmholtz resonators, which are arranged side by side and operate their sound-absorbing action parallel to one another.
  • the precise positioning of the sound absorber on or in the component does not occur, since of the multiple Helmholtz resonators, at least one is positioned near or directly on an antinode. Therefore, since no particularly precise mounting tolerances must be complied with, serial manufacturing or serial fitting of a component with the sound absorber of the present invention is facilitated.
  • the sound absorber equipped with multiple, parallel acting Helmholtz resonators utilizes a relatively broad-banded damping action, so that the sound absorber of the present invention offers altogether an improved damping action.
  • This broad-band action provides, in particular, a wanted or tolerated irregularity of the individual Helmholtz resonators, which is provided with their manufacture.
  • a compact structure is provided, then, when adjacent Helmholtz resonators border one another.
  • the Helmholtz resonators are smaller compared to the cross section of the hollow body.
  • one embodiment is formed, which can be used also with relatively minimal structural space because of its compactness.
  • the Helmholtz resonators based on their large number and in spite of their minimal dimensions, affect a relatively large damping action, so that the sound absorber of the present invention, compared to a common sound absorber, is built to be smaller, thereby using a sufficient damping action with greater band widths.
  • a large damping value can be achieved with a small sound absorber.
  • At least some of the Helmholtz resonators can differ from one another in different lengths and/or cross sections and/or geometries and/or orientations of their hollow chambers and/or in their connection openings.
  • the sound absorber of the present invention can be used always when airborne sound is produced or transmitted in an apparatus.
  • the sound absorber of the present invention is suited in particular for use in or on small apparatuses for damping high or higher frequencies, in particular, from 900 Hz, based on its compact structure.
  • the sound absorber of the present invention can be used with household apparatuses, for example, washing machines, dish washers, hair dryers, vacuum cleaners, or extractor hoods.
  • the sound absorber of the present invention can be used with exhaust air blowers, cooling blowers, air intake assemblies, air conditioners, and computers, in order to damp the frequencies determined there.
  • FIG. 1 shows a schematic diagram-type principle illustration of an internal combustion engine, which is equipped with a sound absorber of the present invention
  • FIG. 2 shows a longitudinal section through a sound absorber of the present invention
  • FIG. 3 shows a cross section through a sound absorber of the present invention
  • FIG. 4 shows a cross section as in FIG. 3, however, with a different embodiment.
  • a sound absorber 1 can be used with an internal combustion engine 2 , in order to dampen sound there, which is produced essentially from an exhaust turbocharger 3 of the combustion engine 2 .
  • the sound absorber, or muffler, 1 is arranged for this purpose in a fresh air tract 4 downstream of an air filter 5 and upstream of a compressor 6 of the exhaust turbocharger 3 .
  • the sound absorber 1 is built into a component, namely, a line 7 of the fresh air tract 4 , is flowed-through by the air transported through the fresh air tract 4 and in this respect, forms an element of the line 7 .
  • the sound produced from the exhaust turbocharger 3 spreads through the line 7 , against the flow direction and—without a sound absorber 1 —would be moved relatively undamped to the air filter 5 and finally dispersed into the surrounding environment.
  • the sound absorber 1 is positioned as close as possible to the sound source whose sounds are to be damped, that is, here, near the exhaust turbocharger 3 .
  • the sound absorber 1 is arranged on the clean air side, that is, downstream of the air filter 5 ; likewise, an arrangement on the crude-air side is also possible.
  • the arrangement shown in FIG. 1 is located in a motor vehicle again, which contains an internal combustion engine as a driving engine.
  • the invention can be used on stationary internal combustion engines 2 .
  • essentially the higher-frequency sound at least in selected frequencies produced from the exhaust turbocharger 3 can be damped.
  • an internal combustion engine without an exhaust turbocharger it is also possible with an internal combustion engine without an exhaust turbocharger to dampen sound produced by the internal combustion engine or elements thereof, for example, from valves of the combustion engine 2 .
  • the sound absorber of the present invention 1 has a tube-shaped hollow body 8 , which forms a component of the line 7 , in which the sound absorber 1 is installed or integrated.
  • the hollow body 8 can be cylindrically formed, as shown here. Other forms, for example, with a cone-shaped hollow body, are likewise possible.
  • a plurality of Helmholtz resonators 10 are arranged in an outer side of the hollow body 8 one after another in the axial direction and side by side in the circumferential direction.
  • Each of these Helmholtz resonators 10 has a hollow chamber 11 , and each of these hollow chambers 11 communicates via an individual connection opening 12 with an interior 13 of the hollow body 8 .
  • the hollow chambers 11 of the Helmholtz resonators 10 are closed.
  • the individual Helmholtz resonators 10 are dimensioned relatively small compared with the line 7 , since the cross sections of the Helmholtz resonators 10 or the hollow chambers 11 are small in comparison to the cross section of the line 7 or the hollow body 8 . Nevertheless, the sound absorber 1 of the present invention can display a relatively strong damping action, in particular, with higher frequencies, for example, from 900 Hz, which is attributed to the large number of the individual, parallel-acting Helmholtz resonators 10 .
  • two zones 14 can be formed in the axial section 9 of the hollow body 8 , in which, respectively, Helmholtz resonators 10 are formed one after another and side by side.
  • these zones 14 extend only partially along the circumference of the hollow body 8 and are arranged opposite one another on the hollow body 8 , according to FIG. 3.
  • a single zone 14 can be formed, which extends along the entire circumference of the hollow body 8 and completely encloses this in the circumferential direction.
  • the Helmholtz resonators 10 are arranged along the entire circumference side by side on the hollow body 8 .
  • Other embodiments also can have more than two such zones 14 .
  • FIG. 4 shows an embodiment, in which the Helmholtz resonators 10 or their hollow chambers 11 and connection openings 12 are oriented radial to a longitudinal axis 15 of the hollow body 8 .
  • adjacent Helmholtz resonators 10 border one another.
  • the bordering Helmholtz resonators 10 have common walls or wall sections 16 , whereby their manufacture is simplified.
  • the hollow chambers 11 of the Helmholtz resonators 10 basically can have any cross section. However, circular, rectangular, or hexagonal cross sections are preferred.
  • At least some of the Helmholtz resonators 10 can differ from one another, in that their hollow chambers 11 and/or their connection openings 12 have different lengths and/or cross sections and/or geometries and/or orientations.
  • the damping performance, in particular, the broad band action, of the sound absorber 1 can be affected.
  • the hollow body 8 has a circular cross section. It is clear that the hollow body 8 can have basically any cross section, at least in the area of its axial section 9 , in particular, a rectangular or polygonal cross section.
  • a distance 17 between the connection openings 12 of two adjacent Helmholtz resonators 10 is smaller than an entire or half wavelength of a frequency to be damped or smaller than a whole or half middle wavelength of a frequency band to be damped.
  • the sound absorber 1 of the present invention can be constructed, such that the hollow chambers 11 of at least some of the Helmholtz resonators 10 are formed in a common block, which, for example, has a “honeycomb structure”.
  • This block forms a separately manufacturable component, which can be attached to a wall section of the hollow body 8 .
  • This wall section includes the connection openings 12 .
  • each hollow chamber 11 is associated with a separate connection opening 12 .
  • the wall section therefore defines the block radially inward. Radially outward, the block is defined, for example, by a common cover, which closes the hollow chambers 11 radially outward.
  • the two zones 14 in the embodiment of FIG. 3 each can be formed in this manner.
  • a type of housing can be formed on the hollow body 8 , in which the separately manufactured block containing the hollow chamber 11 can be inserted.
  • the hollow chambers 1 are closed radially outward.
  • the block can be connected with the wall section of the hollow body 8 and/or with the cover in a suitable manner, in particular, welded.
  • the component, in which the sound to be damped disperses is formed in the described embodiment by the line 7 .
  • the component, in which the sound to be damped disperses is formed by another element of the fresh air tract, for example, by the air filter 5 of by a fresh air accumulator 18 , from which the fresh air is distributed to the individual cylinders of the internal combustion engine (compare FIG. 1).
  • the hollow body of the sound absorber forms a housing or an element, for example, a housing wall, of the component.
  • the sound absorber of the present invention can be formed on or in the cover of an air filter 5 .
  • the sound absorber can be formed as an attachment part or as a mounting part. Likewise, it is possible to form the sound absorber as an integral element of the respective component. For example, the sound absorber is integrated in the housing of the air filter 5 of the air accumulator 8 .
US10/466,722 2001-01-18 2002-01-15 Silencer with a plurality of resonance chambers Abandoned US20040069563A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10102040.6 2001-01-18
DE10102040A DE10102040A1 (de) 2001-01-18 2001-01-18 Schalldämpfer
PCT/DE2002/000094 WO2002057616A1 (de) 2001-01-18 2002-01-15 Schalldämpfer mit einer mehrzahl an resonanzkammern

Publications (1)

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US20040069563A1 true US20040069563A1 (en) 2004-04-15

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US10/466,722 Abandoned US20040069563A1 (en) 2001-01-18 2002-01-15 Silencer with a plurality of resonance chambers

Country Status (4)

Country Link
US (1) US20040069563A1 (de)
EP (1) EP1352172B1 (de)
DE (2) DE10102040A1 (de)
WO (1) WO2002057616A1 (de)

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WO2006018336A1 (de) * 2004-06-16 2006-02-23 Geiger Technik Gmbh Vorrichtung zur schalldämpfung und vorrichtung zur leitung eines fluids
US20070045042A1 (en) * 2005-08-25 2007-03-01 L&L Products, Inc. Sound reduction system with sound reduction chamber
US20070051556A1 (en) * 2005-09-02 2007-03-08 Arvin Technologies, Inc. Exhaust system with external Helmholtz resonator and associated method
US20080223730A1 (en) * 2005-11-30 2008-09-18 Industrie De Nora S. P.A. Electrochemical treatment of solutions containing hexavalent chromium
US20110088968A1 (en) * 2009-10-16 2011-04-21 Ti Automotive Engineering Centre (Heidelberg) Gmbh Sound absorber for a pipe-shaped, cavity-forming body
KR101033601B1 (ko) 2009-06-03 2011-05-11 엘지전자 주식회사 열풍 공급장치 및 의류 처리장치
US20110200426A1 (en) * 2010-02-15 2011-08-18 Makita Corporation Noise reduction devices for blowers
US20160097315A1 (en) * 2014-10-01 2016-04-07 GM Global Technology Operations LLC Silencer
US20160159489A1 (en) * 2014-12-08 2016-06-09 Honeywell International Inc. Fire containment apparatuses for aircraft duct assemblies
US20160195049A1 (en) * 2013-08-08 2016-07-07 Mahle International Gmbh Silencer
JP2017096114A (ja) * 2015-11-19 2017-06-01 小島プレス工業株式会社 車両用消音器
JP2018128153A (ja) * 2017-02-06 2018-08-16 三菱重工サーマルシステムズ株式会社 冷凍機
US20180258891A1 (en) * 2017-03-08 2018-09-13 Subaru Corporation Silencing device
JP2019105391A (ja) * 2017-12-12 2019-06-27 三菱重工サーマルシステムズ株式会社 冷凍サイクルシステム用の吸音要素、それを備えた減圧部、および冷凍サイクルシステム
CN110706684A (zh) * 2018-07-10 2020-01-17 沃维克股份有限公司 用于降低声源的声功率的装置以及方法
JPWO2021100478A1 (de) * 2019-11-20 2021-05-27
WO2022015826A1 (en) * 2020-07-14 2022-01-20 Toledo Molding & Die, Llc Vehicle air filter housing with integrated broad band tuner
GB2616608A (en) * 2022-03-14 2023-09-20 Dyson Technology Ltd Noise attenuator

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DE10243884A1 (de) * 2002-09-21 2004-04-01 Mann + Hummel Gmbh Resonatorschalldämpfer
DE102004010037A1 (de) * 2004-03-02 2005-08-04 Daimlerchrysler Ag Abgasturbolader für eine Brennkraftmaschine
FR2928705A1 (fr) 2008-03-12 2009-09-18 Hutchinson Sa Dispositif d'attenuation acoustique pour ligne d'admission d'un moteur thermique,et ligne d'admission l'incorporant.
DE102008015353A1 (de) 2008-03-22 2009-09-24 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung
US7934581B2 (en) * 2009-01-30 2011-05-03 Eaton Corporation Broadband noise resonator
FR2945839B1 (fr) * 2009-05-20 2012-10-26 Mann & Hummel Gmbh Dispositif acoustique pour l'insonorisation de moteurs a combustion interne.
FR2950112B1 (fr) * 2009-09-11 2011-10-07 Hutchinson Dispositif d'attenuation acoustique pour ligne d'admission d'un moteur thermique, et ligne d'admission l'incorporant
DE202009014112U1 (de) 2009-10-16 2010-01-07 Ti Automotive Engineering Centre (Heidelberg) Gmbh Schalldämpfer für einen rohrförmigen, einen Hohlraum bildenden Körper
EP2327327A1 (de) * 2009-11-26 2011-06-01 Babyliss Faco S.A. Zusätzlicher Geräuschdämpfer für Haartrockner
DE102012024512A1 (de) 2012-12-14 2014-06-18 Daimler Ag Schalldämpfungseinrichtung für eine Verbrennungskraftmaschine

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DE50201672D1 (de) 2005-01-05

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