EP1352172A1 - Silencer with a plurality of resonance chambers - Google Patents
Silencer with a plurality of resonance chambersInfo
- Publication number
- EP1352172A1 EP1352172A1 EP02701191A EP02701191A EP1352172A1 EP 1352172 A1 EP1352172 A1 EP 1352172A1 EP 02701191 A EP02701191 A EP 02701191A EP 02701191 A EP02701191 A EP 02701191A EP 1352172 A1 EP1352172 A1 EP 1352172A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hollow body
- silencer
- helmholtz resonators
- component
- silencer according
- 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
Links
- 230000003584 silencer Effects 0.000 title claims abstract description 47
- 238000002485 combustion reaction Methods 0.000 claims description 18
- 230000002238 attenuated effect Effects 0.000 claims description 5
- 238000009434 installation Methods 0.000 claims description 4
- 238000000605 extraction Methods 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 238000005406 washing Methods 0.000 claims description 2
- 238000010025 steaming Methods 0.000 claims 1
- 239000006096 absorbing agent Substances 0.000 abstract 1
- 230000000644 propagated effect Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 18
- 238000013016 damping Methods 0.000 description 16
- 238000004519 manufacturing process Methods 0.000 description 7
- 230000001902 propagating effect Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
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 silencer on or in a component in which a sound to be damped, in particular airborne sound, propagates.
- Silencers are used, for example, in internal combustion engines to reduce noise emissions to the environment.
- mufflers are arranged in an exhaust tract of an internal combustion engine in order to dampen the sound generated by the internal combustion engine and propagating therein.
- Mufflers are also used in motor vehicles in a fresh air tract of the internal combustion engine, for example to to dampen the sound generated by the exhaust gas turbocharger and propagating in the fresh air tract in an internal combustion engine charged with an exhaust gas turbocharger.
- shunt resonators NN or “Helmholtz resonators are known for damping sound that propagates in a line.
- a Helmholtz resonator essentially consists of a cavity, which communicates via a connection opening with the interior of the line, in which the sound to be damped propagates, the cavity being otherwise closed.
- the inserted in the cavity closed gas volume acts as a "spring” and the gas volume in the connection opening acts as a "mass”, whereby an oscillatory system is formed.
- This oscillation system can be excited to vibrate by sound waves, whereby energy is extracted from the sound waves, that is to say the sound is damped.
- the damping effect of such a Helmholtz resonator is limited to a certain frequency or to a certain frequency band.
- the frequency or the frequency band at which the Helmholtz resonator develops its damping effect depends, for example, on the geometry, the cross section, the length and thus on the volume of the cavity and the connection opening of the Helmholtz resonator.
- a Helmholtz resonator can best exert its damping effect if it is positioned on the line in such a way that its connecting opening communicates with the inside of the line exactly where an antinode of a standing sound wave of the frequency that has developed from the Helmholtz resonator has formed in the line should be dampened.
- the geometry of the line in which the sound propagates defines the positions in which a standing sound wave can form.
- the exact position of an antinode can be calculated at a given frequency.
- the Helmholtz resonator must then be connected to the line as precisely as possible at the calculated point.
- it is possible to precisely maintain a desired assembly position can only be ensured with a relatively high effort.
- the range of frequencies that can be damped with a conventional muffler equipped with a Helmholtz resonator is very narrow, so that only level peaks of certain frequencies can be damped regularly.
- the present invention is concerned with the problem of specifying an embodiment for a muffler of the type mentioned at the outset which is relatively easy to assemble and / or integrate and which thereby ensures a high damping effect.
- a silencer is to be specified which has an improved damping effect and in particular an enlarged broadband effect.
- the silencer should be particularly inexpensive to manufacture.
- the invention is based on the general idea of equipping a muffler with a plurality, in particular with a plurality, of Helmholtz resonators which are arranged with one another and develop their sound-absorbing effect in parallel with one another.
- the arrangement of the Helmholtz resonators one behind the other in the direction of sound propagation does not depend on the exact positioning of the muffler on or in the component, for example a line in which the sound to be damped propagates, since at least one of the several Helmholtz resonators is necessarily close or direct is positioned on an antinode. Since no particularly precise assembly tolerances have to be observed, series production or the standard equipment of a component with the silencer according to the invention is made easier.
- the muffler equipped with a plurality of Helmholtz resonators acting in parallel develops a relatively broadband damping effect, so that the muffler according to the invention has an overall improved damping effect.
- This broadband effect results in particular from a desired or tolerated non-uniformity of the individual Helmholtz resonators, which results from their manufacture.
- An embodiment is particularly advantageous in which, in an axial section of a hollow body of the silencer, in a zone extending in the axial direction and in the circumferential direction of the hollow body, a plurality of Helmholtz resonators acting in parallel are arranged one behind the other in the axial direction and next to one another in the circumferential direction. This results in a flat arrangement of a large number of Helmholtz resonators on the hollow body, as a result of which the damping effect or the broadband capability is additionally increased.
- a compact design results when adjacent Helmholtz resonators are adjacent to one another.
- An embodiment is advantageous in which the mutually adjoining Helmholtz resonators have common walls or common own wall sections. This simplifies the manufacture of the Helmholtz resonators.
- An embodiment is particularly advantageous in which the cross sections of the Helmholtz resonators are small compared to the cross section of the hollow body. This forms an embodiment which is distinguished by its compactness and can therefore also be used with a relatively small installation space. It has been shown that the Helmholtz resonators, due to their large number, despite their small dimensions, have a relatively large damping effect, so that the muffler according to the invention has a smaller size than a conventional muffler, and has a sufficient damping effect with a wider bandwidth. Especially for high or higher frequencies, e.g. From around 900 Hz, large attenuation values can be achieved with a small-sized silencer.
- At least some of the Helmholtz resonators can differ from one another in that their cavities and / or their connecting openings have different lengths and / or cross sections and / or geometries and / or orientations.
- the silencer according to the invention can always be used when airborne sound is generated or transmitted in a device.
- the muffler according to the invention is particularly suitable ⁇ because of its compact structure for use in or on smaller devices for damping high or higher frequencies, for example from 900 Hz.
- the muffler according to the invention can be used in household appliances, for example washing machine, dishwasher , Tumble dryer, hair dryer, vacuum cleaner, extractor hood.
- the silencer according to the invention can be used, for example, in exhaust air fans, cooling fans, air extraction systems, air conditioning systems, computers, in order to specifically dampen specific frequencies there.
- FIG. 1 is a circuit diagram-like schematic representation of an internal combustion engine which is equipped with a silencer according to the invention
- Fig. 3 shows a cross section through a silencer according to the invention
- Fig. 4 is a cross section as in Fig. 3, but in another embodiment.
- a muffler 1 can be used in an internal combustion engine 2 in order to dampen sound there, which is essentially generated by an exhaust gas turbocharger 3 of the internal combustion engine 2.
- the silencer 1 is arranged in a fresh air tract 4 downstream of an air filter 5 and upstream of a compressor 6 of the exhaust gas turbocharger 3.
- the silencer 1 is installed in a component, namely in a line 7 of the fresh air tract 4. tract 4 flows through transported air and forms part of the line 7.
- the sound generated by the exhaust gas turbocharger 3 propagates through the line 7, against the direction of flow and would - without silencer 1 - reach the air filter 5 relatively undamped and finally into the The environment.
- the sound propagating in the line 7 can be damped with regard to certain frequencies or frequency bands, as a result of which the sound emission of the entire arrangement can be reduced.
- the muffler 1 is preferably positioned as close as possible to the sound source whose sound is to be damped, ie here, close to the exhaust gas turbocharger 3.
- the muffler 1 is arranged on the clean air side, that is to say downstream of the air filter 5; an arrangement on the raw air side is also possible.
- FIG. 1 The arrangement shown in FIG. 1 is preferably found in a motor vehicle which contains the internal combustion engine 2 as the drive motor.
- the invention can also be applied to stationary internal combustion engines 2.
- the higher-frequency sound generated by the exhaust gas turbocharger 3 is essentially to be damped, at least in certain frequencies.
- the silencer according to the invention has
- the hollow body 8 can, as here, be cylindrical. Other embodiments, e.g. with a conical hollow body are also possible.
- a plurality of Helmholtz resonators 10 are arranged one behind the other in the axial direction and next to one another in the circumferential direction on an outer side of the hollow body 8.
- Each of these Helmholtz resonators 10 has a cavity 11, and each of these cavities
- the silencer according to the invention can 1, especially at higher frequencies, e.g. from 900 Hz, develop a relatively strong damping effect, which is attributed to the large number of individual Helmholtz resonators 10 acting in parallel.
- two zones 14 can be formed in the axial section 9 of the hollow body 8, in each of which Helmholtz resonators 10 arranged side by side and one behind the other are formed. 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 also be formed, which extends along the entire circumference of the hollow body 8 and thus completely surrounds it in the circumferential direction.
- the Helmholtz resonators 10 are also arranged next to one another on the hollow body 8 along the entire circumference.
- Other embodiments can also have more than two such zones 14.
- FIG. 4 shows an embodiment in which the Helmholtz resonators 10 or their cavities 11 and their connecting openings 12 radially to a longitudinal axis 15 of the hollow body 8 are aligned.
- adjacent Helmholtz resonators 10 adjoin one another.
- the adjacent Helmholtz resonators 10 have common walls or wall sections 16, which simplifies their manufacture.
- the cavities 11 of the Helmholtz resonators 10 can in principle have any cross sections. 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 cavities 11 and / or their connecting openings 12 have different lengths and / or cross sections and / or geometries and / or orientations. As a result, the damping behavior, in particular the broadband effect, of the silencer 1 can be influenced.
- the hollow body 8 has a circular cross section. It is clear that the hollow body 8 can basically have any cross-section, in particular in the area of its axial section 9, in particular a rectangular or polygonal cross-section.
- an embodiment is preferred in which, at least in the axial direction of the hollow body 8, a distance 17 between the connection openings 12 of two adjacent Helmholtz resonators 10 is smaller than a whole or half a wavelength of a frequency to be attenuated or smaller than a whole or a half average wavelength of a frequency band to be attenuated.
- This design ensures that the muffler 1 according to the invention is not positioned precisely Muffler 1 arrives at or in line 7. Because as long as the axial section 9 equipped with the Helmholtz resonators 10 is positioned in the region of an antinode, at least one of the Helmholtz resonators 10 is located relatively close to or exactly at the maximum of the antinode. In this way, an optimal damping effect for the silencer 1 can always be guaranteed.
- the silencer 1 according to the invention can be constructed such that the cavities
- Helmholtz resonators 10 are formed in a common block, which has, for example, a honeycomb structure or "honeycomb structure". This block then forms a separately producible component that can be attached to a wall section of the hollow body 8. This wall section is with the connection openings
- a suitable connection opening 12 is assigned to each cavity 11 by a suitable placement of the said block on the wall section provided for this purpose.
- the wall section thus delimits the block radially on the inside.
- the block is delimited radially on the outside, for example, by a common cover which closes the cavities 11 radially on the outside.
- the two zones 14 provided in the embodiment according to FIG. 3 can each be formed in this way.
- a type of housing can be formed on the hollow body 8, in which the separately produced block containing the cavities 11 can be inserted. By closing this housing with a suitable cover, the cavities 11 are simultaneously radially closed.
- the block can be connected to 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 propagates is formed by line 7 in the exemplary embodiment described.
- the component in which the sound to be attenuated is formed by another component of the fresh air track, for example by the air filter 5 or by a fresh air collector 18, from which the fresh air supplied is directed to the individual cylinders of the internal combustion engine 2 distributed (see. Fig. 1).
- the hollow body of the muffler then preferably forms a housing or a component, e.g. a housing wall, the component.
- the silencer according to the invention can be formed on or in the cover of the air filter 5.
- the muffler can be designed as an attachment or as an installation part which is mounted on or in the respective component. It is also possible to design the silencer as an integral part of the respective component.
- the muffler is integrated in the housing of the air filter 5 or air collector 8.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Multimedia (AREA)
- Exhaust Silencers (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10102040A DE10102040A1 (en) | 2001-01-18 | 2001-01-18 | Silencer, for a motor exhaust or turbo charger air intake, has a hollow body at the component to be suppressed containing a number of parallel Helmholtz resonators |
DE10102040 | 2001-01-18 | ||
PCT/DE2002/000094 WO2002057616A1 (en) | 2001-01-18 | 2002-01-15 | Silencer with a plurality of resonance chambers |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1352172A1 true EP1352172A1 (en) | 2003-10-15 |
EP1352172B1 EP1352172B1 (en) | 2004-12-01 |
Family
ID=7670911
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02701191A Revoked EP1352172B1 (en) | 2001-01-18 | 2002-01-15 | Silencer with a plurality of resonance chambers |
Country Status (4)
Country | Link |
---|---|
US (1) | US20040069563A1 (en) |
EP (1) | EP1352172B1 (en) |
DE (2) | DE10102040A1 (en) |
WO (1) | WO2002057616A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2005085622A1 (en) * | 2004-03-02 | 2005-09-15 | Daimlerchrysler Ag | Exhaust-gas turbocharger for internal combustion engine |
EP2101057A1 (en) | 2008-03-12 | 2009-09-16 | Hutchinson | Sound attenuation device for the intake line of a heat engine and intake line including same |
Families Citing this family (27)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10243884A1 (en) * | 2002-09-21 | 2004-04-01 | Mann + Hummel Gmbh | Resonatorschalldämpfer |
DE102004029221A1 (en) * | 2004-06-16 | 2006-01-12 | Geiger Technik Gmbh | Acoustic damping device and device for conducting a fluid |
US20070045042A1 (en) * | 2005-08-25 | 2007-03-01 | L&L Products, Inc. | Sound reduction system with sound reduction chamber |
US7870930B2 (en) * | 2005-09-02 | 2011-01-18 | Emcon Technologies Llc | Exhaust system with external helmholtz resonator and associated method |
ITMI20052297A1 (en) * | 2005-11-30 | 2007-06-01 | De Nora Elettrodi Spa | ELECTROCHEMICAL TREATMENT OF SOLUTIONS WITH HEXAVALENT CHROME |
DE102008015353A1 (en) | 2008-03-22 | 2009-09-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Loading device i.e. exhaust gas turbo charger, for motor vehicle, has sound absorber including chamber, where external wall is partially extended in axial direction and formed by housing of device |
US7934581B2 (en) * | 2009-01-30 | 2011-05-03 | Eaton Corporation | Broadband noise resonator |
FR2945839B1 (en) * | 2009-05-20 | 2012-10-26 | Mann & Hummel Gmbh | ACOUSTIC DEVICE FOR THE SOUNDPROOFING OF INTERNAL COMBUSTION ENGINES. |
KR101033601B1 (en) | 2009-06-03 | 2011-05-11 | 엘지전자 주식회사 | hot air supplying apparatus and cloth treating apparatus |
FR2950112B1 (en) * | 2009-09-11 | 2011-10-07 | Hutchinson | ACOUSTICAL ATTENUATION DEVICE FOR THE INTAKE LINE OF A THERMAL MOTOR, AND ADMISSION LINE INCORPORATING IT |
EP2357330B1 (en) | 2009-10-16 | 2015-08-19 | TI Automotive Engineering Centre (Heidelberg) GmbH | Cooling circuit with acoustic baffler for a tubular body forming a cavity |
DE202009014112U1 (en) | 2009-10-16 | 2010-01-07 | Ti Automotive Engineering Centre (Heidelberg) Gmbh | Silencer for a tubular body forming a cavity |
EP2327327A1 (en) * | 2009-11-26 | 2011-06-01 | Babyliss Faco S.A. | Add-on silencer for hairdryer |
JP5620690B2 (en) * | 2010-02-15 | 2014-11-05 | 株式会社マキタ | Blower |
DE102012024512A1 (en) | 2012-12-14 | 2014-06-18 | Daimler Ag | Silencer device for internal combustion engine of a motor vehicle, has acoustic resonator that is separately formed into suction duct, where construction element is integrated in internal combustion engine in partially opaque manner |
DE102013215636A1 (en) * | 2013-08-08 | 2015-02-12 | Mahle International Gmbh | Silencer |
DE202014007986U1 (en) * | 2014-10-01 | 2016-01-05 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | silencer |
US9650149B2 (en) * | 2014-12-08 | 2017-05-16 | Honeywell International Inc. | Fire containment apparatuses for aircraft duct assemblies |
JP6587521B2 (en) * | 2015-11-19 | 2019-10-09 | 小島プレス工業株式会社 | Vehicle silencer |
JP2018128153A (en) * | 2017-02-06 | 2018-08-16 | 三菱重工サーマルシステムズ株式会社 | Refrigeration machine |
JP6514727B2 (en) * | 2017-03-08 | 2019-05-15 | 株式会社Subaru | Silencer |
JP7014584B2 (en) * | 2017-12-12 | 2022-02-01 | 三菱重工サーマルシステムズ株式会社 | A sound absorbing element for the refrigeration cycle system, a decompression unit with it, and a refrigeration cycle system. |
DE102018116681A1 (en) * | 2018-07-10 | 2020-01-16 | Vorwerk & Co. Interholding Gesellschaft mit beschränkter Haftung | Device and method for reducing the sound power of a sound source |
CN110748410A (en) * | 2019-11-11 | 2020-02-04 | 河北亚大汽车塑料制品有限公司 | Vehicle silencer |
JP7281556B2 (en) * | 2019-11-20 | 2023-05-25 | 本田技研工業株式会社 | Vehicle air intake structure |
US20220016561A1 (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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US4314621A (en) * | 1979-03-07 | 1982-02-09 | Caterpillar Tractor Co. | Fluidborne noise attenuator |
DE2947256C2 (en) * | 1979-11-23 | 1984-09-13 | Messerschmitt-Bölkow-Blohm GmbH, 8000 München | Device for reducing exhaust or exhaust noise |
US4360075A (en) * | 1981-05-11 | 1982-11-23 | General Motors Corporation | Low back pressure exhaust silencer for diesel locomotives |
US4645032A (en) * | 1985-09-05 | 1987-02-24 | The Garrett Corporation | Compact muffler apparatus and associated methods |
JPH088305Y2 (en) * | 1987-09-07 | 1996-03-06 | 小島プレス工業株式会社 | Silencer |
US4979587A (en) * | 1989-08-01 | 1990-12-25 | The Boeing Company | Jet engine noise suppressor |
FI95747B (en) * | 1991-01-17 | 1995-11-30 | Valmet Paper Machinery Inc | Mufflers for low frequencies for air ducts in paper mills |
DE59209528D1 (en) * | 1992-08-22 | 1998-11-19 | Porsche Ag | INTERNAL COMBUSTION ENGINE WITH AN INTAKE SYSTEM |
DE19504223A1 (en) * | 1995-02-09 | 1996-08-14 | Volkswagen Ag | Intake silencer for internal combustion engine |
DE19615917A1 (en) * | 1996-04-22 | 1997-10-30 | Wolf Woco & Co Franz J | Intake silencer and motor vehicle |
DE19725003A1 (en) * | 1997-06-13 | 1998-12-17 | Philippron Jean Claude | Muffler and soundproofing material |
DE19818873C2 (en) * | 1998-04-28 | 2001-07-05 | Man B & W Diesel Ag | Reciprocating internal combustion engine |
US6231710B1 (en) * | 1999-06-04 | 2001-05-15 | The United States Of America As Represented By The Secretary Of The Air Force | Method of making composite chambercore sandwich-type structure with inherent acoustic attenuation |
US6695094B2 (en) * | 2001-02-02 | 2004-02-24 | The Boeing Company | Acoustic muffler for turbine engine |
US6752240B1 (en) * | 2002-11-05 | 2004-06-22 | Brunswick Corporation | Sound attenuator for a supercharged marine propulsion device |
-
2001
- 2001-01-18 DE DE10102040A patent/DE10102040A1/en not_active Withdrawn
-
2002
- 2002-01-15 EP EP02701191A patent/EP1352172B1/en not_active Revoked
- 2002-01-15 US US10/466,722 patent/US20040069563A1/en not_active Abandoned
- 2002-01-15 WO PCT/DE2002/000094 patent/WO2002057616A1/en not_active Application Discontinuation
- 2002-01-15 DE DE50201672T patent/DE50201672D1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO02057616A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2005085622A1 (en) * | 2004-03-02 | 2005-09-15 | Daimlerchrysler Ag | Exhaust-gas turbocharger for internal combustion engine |
EP2101057A1 (en) | 2008-03-12 | 2009-09-16 | Hutchinson | Sound attenuation device for the intake line of a heat engine and intake line including same |
Also Published As
Publication number | Publication date |
---|---|
DE50201672D1 (en) | 2005-01-05 |
DE10102040A1 (en) | 2002-07-25 |
WO2002057616A1 (en) | 2002-07-25 |
US20040069563A1 (en) | 2004-04-15 |
EP1352172B1 (en) | 2004-12-01 |
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