EP1400662B1 - Silencieux à résonateur - Google Patents

Silencieux à résonateur Download PDF

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Publication number
EP1400662B1
EP1400662B1 EP03103301A EP03103301A EP1400662B1 EP 1400662 B1 EP1400662 B1 EP 1400662B1 EP 03103301 A EP03103301 A EP 03103301A EP 03103301 A EP03103301 A EP 03103301A EP 1400662 B1 EP1400662 B1 EP 1400662B1
Authority
EP
European Patent Office
Prior art keywords
perforated plate
silencer
wall thickness
silencer according
combustion engine
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.)
Expired - Lifetime
Application number
EP03103301A
Other languages
German (de)
English (en)
Other versions
EP1400662A1 (fr
Inventor
Helmut Spannbauer
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.)
Mann and Hummel GmbH
Original Assignee
Mann and Hummel 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
Application filed by Mann and Hummel GmbH filed Critical Mann and Hummel GmbH
Publication of EP1400662A1 publication Critical patent/EP1400662A1/fr
Application granted granted Critical
Publication of EP1400662B1 publication Critical patent/EP1400662B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01N1/023—Helmholtz resonators
    • 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
    • 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
    • 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
    • F01N2450/00—Methods or apparatus for fitting, inserting or repairing different elements
    • F01N2450/18—Methods or apparatus for fitting, inserting or repairing different elements by using quick-active type locking mechanisms, e.g. clips
    • 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
    • F01N2450/00—Methods or apparatus for fitting, inserting or repairing different elements
    • F01N2450/22—Methods or apparatus for fitting, inserting or repairing different elements by welding or brazing
    • 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
    • F01N2450/00—Methods or apparatus for fitting, inserting or repairing different elements
    • F01N2450/28—Methods or apparatus for fitting, inserting or repairing different elements by using adhesive material, e.g. cement
    • 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
    • F01N2450/00—Methods or apparatus for fitting, inserting or repairing different elements
    • F01N2450/40—Retrofitting exhaust apparatus
    • 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
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/02—Tubes being perforated
    • F01N2470/04—Tubes being perforated characterised by shape, disposition or dimensions of apertures
    • 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
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/24—Concentric tubes or tubes being concentric to housing, e.g. telescopically assembled
    • 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
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/15—Plurality of resonance or dead chambers
    • F01N2490/155—Plurality of resonance or dead chambers being disposed one after the other in flow direction
    • 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
    • F01N2530/00—Selection of materials for tubes, chambers or housings
    • 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
    • F01N2530/00—Selection of materials for tubes, chambers or housings
    • F01N2530/18—Plastics material, e.g. polyester resin
    • 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

Definitions

  • the invention relates to a silencer according to the preamble of patent claim 1.
  • the object of the invention is to avoid the disadvantages listed above and to provide a muffler which is easy to manufacture, occupies a small space and has a very large variability in the frequency range to be attenuated. This object is solved by the features of claim 1.
  • the silencer according to the invention operates on the principle of a Helmholtz resonator, wherein at least one sound-conducting element of this silencer contains at least one resonator chamber, which is separated by a perforated plate from the corresponding flow channel.
  • the perforated plate may in this case be designed in the form of a tube or another self-contained element or else only as a fragment suitable for the separation of the resonator chamber and the flow-conducting channel.
  • the perforated plate in the direct area of the holes arranged therein around at least one hole around a changed wall thickness compared to the remaining wall thickness of the perforated plate on the wall thickness is reduced.
  • the frequency range to be damped can be better controlled, without the duration and fatigue strength of the perforated plate appreciably influence.
  • many different silencers with corresponding damping characteristics can be realized with only one perforated plate.
  • the perforated plate can be made of metal for this purpose; However, it is also conceivable that it consists of an injection-moldable material and the changed wall thicknesses in the region of at least one hole is produced by appropriate design of the injection mold.
  • the cross-sectional shape of the holes arranged in the perforated plate can be selected and executed independently of the changed wall thickness.
  • this muffler can be used in an internal combustion engine, especially a supercharged internal combustion engine. But it is quite conceivable to arrange this silencer in further known in the art sound conducting lines or devices. Here are to call as an example compressed air lines.
  • An embodiment of the silencer according to the invention is characterized in that the changed wall thickness is realized by a conical depression with a defined angle between the sinking surfaces.
  • the damped frequency depends on the angle between the sinking surfaces. The larger the angle included between the sinkers, the higher the frequency to be damped.
  • the counterbore can be arranged on the side leading to the chamber or on the side of the perforated plate leading to the flow channel. It is preferably designed in the direction of the resonator chamber.
  • the change in the wall thickness in the direct region of the holes arranged therein can be realized by a stepwise reduction of the wall thickness comprising at least one step.
  • the number of stages here can be chosen arbitrarily and depends on the desired frequency range to be damped and the wall thickness present in the perforated plate.
  • a reduction of the wall thickness can be realized in a further embodiment by a substantially hemispherical lowering.
  • Another possibility for changing the wall thickness in the hole region of interest is a hole-congruent sheathing or incorporation of at least one further perforated sheet.
  • the further perforated plate must have a shape corresponding to the first perforated plate and is directly connected to the first perforated plate with exact hole coverage by means of an adhesive method, welding method, clip method or other types of connection known in the prior art. It proves to be advantageous here the associated retrofitting or retrofit option of an existing silencer.
  • the silencer according to the invention is arranged in a flow line of an internal combustion engine between an exhaust gas turbocharger and a charge air cooling.
  • the muffler is preferably arranged close to the largest sound-emitting source, namely the exhaust gas turbocharger.
  • the muffler here has the same cross-section as the flow line and is used between exhaust gas turbocharger and flow line to the intercooler.
  • the silencer according to the invention represents the flow line between exhaust gas turbocharger and intercooler itself.
  • the silencer according to the invention is arranged in a sound-conducting element in the interior of an exhaust gas turbocharger of an internal combustion engine.
  • a sound-conducting element in the interior of an exhaust gas turbocharger of an internal combustion engine.
  • the silencer can be used individually or in combination with other silencers in different positions.
  • the silencer according to the invention is arranged in a sound-conducting element in an exhaust gas line of the internal combustion engine. Since exhaust-side sound waves in certain frequency ranges are to be damped, it is also possible to arrange this silencer at one or more points in the exhaust pipe system. In this case, the muffler can serve as a flange connection between two line parts or be integrated into the line. Furthermore, the silencer according to the invention can be combined in combination with other known in the art silencers.
  • a further embodiment of the invention is characterized in that the muffler is provided with a combination of rows of holes with different wall thicknesses of the perforated plate for broadband sound attenuation. Due to the different wall thicknesses in the area of individual holes or even rows of holes, a particularly wide spectrum of frequencies can be damped. The different wall thicknesses can be achieved as described above by subsequent processing or even in the production process of the perforated plate.
  • the muffler will have combinations of rows of holes, each with different wall thicknesses of the perforated plate in the rows of holes.
  • a silencer in particular for an internal combustion engine with turbocharger wherein at least one sound-conducting element includes at least one chamber which is separated by a perforated plate from the corresponding flow channel and thereby constructed according to the principle of a Helmholtz resonator provided.
  • the perforated plate in the direct region of the holes arranged therein at each hole a conical depression, wherein the angle between the lowering surfaces is between 60 and 150 °.
  • the reductions take place from the direction of the resonator chamber.
  • the resonator tube is made of metal and the subsidence are introduced mechanically from the outside.
  • the wall thickness of the perforated plate in the non-counterbored areas is between 0.5 and 5 mm and the hole diameter between 1 and 20 mm.
  • the silencer according to the invention is advantageously used in an internal combustion engine with at least one exhaust gas turbocharger, where it can be used there on the intake side and / or on the exhaust side.
  • FIG. 1 shows a schematic view of an embodiment of the invention. Shown is a muffler 10, consisting of a perforated plate 11 and a Resonatorhuntwand 14.
  • the perforated plate 11 has a substantially cylindrical shape and separates the running inside the perforated plate 11 flow channel of two resonator chambers 13a, 13b. These are formed by the, the perforated plate 11 at a radial distance surrounding the resonator chamber wall 14, wherein the chambers 13a, 13b are separated by a partition wall 15 from each other.
  • the perforated plate 11 has recesses 12, which serve to generate the Helmholtz effect and are distributed over the entire circumference.
  • the recesses 12 are countersunk in the perforated plate 11 in the direction of the resonator chamber wall 14, wherein the two rows of holes each have a different countersink angle. This results in a broadband attenuation of the emitted sound, since different resonator neck lengths are achieved by the different countersinking angles.
  • the perforated metal sheet 11 is to be connected with possibilities at the respective ends with continuing line parts or an exhaust gas turbocharger.
  • the resonator chamber wall is made of a plastic, e.g. Polyamide 6.6 (PA 6.6) and is sealed to the perforated plate by bonding or other joining methods known in the art.
  • the subsidence of the recesses 12 are mechanically introduced, with defined Senkwinkeln before connecting the perforated plate 11 and the resonator chamber wall 14. Due to the subsidence, the effective resonator neck length deviates from the original resonator neck length, namely the perforated plate wall thickness s.
  • FIG. 2 shows the relationship between countersink angle ⁇ and resonator neck length s.
  • the Figure 1 corresponding components are provided with the same reference numerals.
  • FIG. 2 shows sections of the perforated plate 11 in the region of the recesses 12, each with different reductions and different angles of sinking ⁇ i can be seen.
  • the lower section according to Figure 2c shows a perforated plate 11 in the region of a recess 12 which has no reduction, which corresponds to the prior art, and wherein the effective resonator neck length s i of the wall thickness s of the perforated plate 11 corresponds.
  • One way to increase the frequency to be damped is to reduce the effective resonator neck length s i .
  • the middle section of Figure 2b shows again a perforated plate 11 in the area a recess 12 with a countersink at the countersink angle ⁇ 2 .
  • the countersinking angle ⁇ i relative to the middle segment has been increased even at a countersinking angle ⁇ . 1 Because of the increased countersinking angle ⁇ 1, a veringerte Resonatorhalsus s 1 is again obtained.
  • the effect of reducing the effective resonator neck length s i to the frequency F to be damped is shown in FIG.
  • the fundamental effect of Helmholtz resonators with an attenuation of more than 20 dB compared to a cable of the same diameter without a silencer according to curve X can clearly be seen.
  • the muffler tested has a full-scale row of holes with an equally comprehensive, concentric resonator chamber. With a countersinking of the recesses with respect to the not countersunk recesses, the attenuated frequency shifts in the direction of the higher frequencies.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Exhaust Silencers (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)

Claims (15)

  1. Silencieux, en particulier d'un moteur à combustion interne, de préférence d'un moteur à combustion interne suralimenté, dans lequel au moins un élément conducteur du son contient au moins une chambre de résonateur séparée du canal d'écoulement correspondant par une tôle perforée et de ce fait construite selon le principe d'un résonateur de Helmholtz, caractérisé en ce que la tôle perforée présente une épaisseur de paroi modifiée autour d'au moins un trou dans la zone directe des trous pratiqués dans celle-ci, réduisant ainsi l'épaisseur de paroi.
  2. Silencieux selon la revendication 1, caractérisé en ce que l'épaisseur de paroi modifiée est réalisée par un fraisage conique avec un angle défini entre les faces fraisées.
  3. Silencieux selon la revendication 1, caractérisé en ce que l'épaisseur de paroi modifiée est réalisée par une diminution étagée, comportant au moins un étage, de l'épaisseur de paroi.
  4. Silencieux selon la revendication 1, caractérisé en ce que l'épaisseur de paroi modifiée est réalisée par un fraisage essentiellement hémisphérique.
  5. Silencieux selon la revendication 1, caractérisé en ce que l'épaisseur de paroi modifiée est réalisée par un assemblage avec au moins une autre tôle perforée en correspondance avec les trous.
  6. Silencieux selon l'une quelconque des revendications précédentes, caractérisé en ce que le silencieux est disposé dans une conduite d'écoulement d'un moteur à combustion interne entre un turbocompresseur de gaz d'échappement et un refroidissement de l'air d'admission.
  7. Silencieux selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le silencieux est disposé dans un élément conduisant le son à l'intérieur d'un turbocompresseur de gaz d'échappement du moteur à combustion interne.
  8. Silencieux selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le silencieux selon l'invention est disposé dans un élément conduisant le son dans une conduite côté gaz d'échappement du moteur à combustion interne.
  9. Silencieux selon l'une quelconque des revendications précédentes, caractérisé en ce que le silencieux est pourvu d'une combinaison de rangées de trous avec des épaisseurs de paroi différentes de la tôle perforée pour une insonorisation à plus large bande.
  10. Silencieux selon la revendication 2, caractérisé en ce que la tôle perforée présente, dans la zone directe des trous pratiqués dans celle-ci, un fraisage conique à chaque trou, où l'angle entre les faces fraisées vaut entre 60 et 150°.
  11. Silencieux selon la revendication 10, caractérisé en ce que l'épaisseur de paroi de la tôle perforée dans les zones non fraisées est de 0,5 à 5 mm et le diamètre des trous mesure entre 1 et 20 mm.
  12. Silencieux selon l'une quelconque des revendications 10 ou 11, caractérisé en ce que la distance radiale entre la tôle perforée et une paroi de limitation extérieure mesure entre 1 et 40 mm.
  13. Silencieux selon une ou plusieurs des revendications 10 à 12, caractérisé en ce que le rapport entre le volume de la chambre et la somme des surfaces des trous vaut entre 4 et 40 cm3 par cm2.
  14. Silencieux selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une modification de l'épaisseur de paroi de la tôle perforée produit une variation de la longueur utile du col de résonateur.
  15. Moteur à combustion interne comportant au moins un turbocompresseur de gaz d'échappement, caractérisé en ce qu'il est équipé d'un silencieux selon l'une quelconque des revendications précédentes.
EP03103301A 2002-09-21 2003-09-05 Silencieux à résonateur Expired - Lifetime EP1400662B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10243884A DE10243884A1 (de) 2002-09-21 2002-09-21 Resonatorschalldämpfer
DE10243884 2002-09-21

Publications (2)

Publication Number Publication Date
EP1400662A1 EP1400662A1 (fr) 2004-03-24
EP1400662B1 true EP1400662B1 (fr) 2007-08-08

Family

ID=31896264

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03103301A Expired - Lifetime EP1400662B1 (fr) 2002-09-21 2003-09-05 Silencieux à résonateur

Country Status (3)

Country Link
EP (1) EP1400662B1 (fr)
AT (1) ATE369485T1 (fr)
DE (2) DE10243884A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
US11808187B2 (en) 2021-03-01 2023-11-07 Caterpillar Inc. Noise attenuation components

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CN102753792B (zh) * 2010-02-11 2014-08-20 佛吉亚排放控制技术美国有限公司 具有赫姆霍尔兹腔室的塑料消声器
DE102010020064B4 (de) 2010-05-11 2019-10-02 Bayerische Motoren Werke Aktiengesellschaft Schalldämpferanordnung für eine insbesondere aufgeladene Kraftfahrzeug-Brennkraftmaschine
US20140196977A1 (en) 2013-01-16 2014-07-17 Henn Gmbh & Co Kg. Silencer and method for manufacturing the same
ES2717778T3 (es) 2014-10-21 2019-06-25 Henn Gmbh & Co Kg Silenciador de vehículo para una tubería de aire de sobrealimentación de un motor de combustión interna
JP6579834B2 (ja) * 2015-07-08 2019-09-25 三菱日立パワーシステムズ株式会社 燃焼器及びガスタービン
DE102019002157B4 (de) * 2019-03-26 2023-03-02 Stefanie Gernert Wand zur tieffrequenten und breit-frequenzbandingen, massiven schalldämpfung flächig einfallenden schalls

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FR2540912A2 (fr) * 1982-06-02 1984-08-17 Uzan Daniel Dispositif absorbeur acoustique passif absorbant aussi les basses frequences
FR2743848B1 (fr) * 1996-01-24 1998-04-10 Peugeot Dispositif d'attenuation reglable des bruits emis par des gaz en circulation d'un moteur de vehicule automobile
DE19629368A1 (de) * 1996-07-20 1998-01-22 Gillet Heinrich Gmbh Vorrichtung zum Unterdrücken des Entstehens von harmonischen Tönen in perforierten Rohren
US5930371A (en) * 1997-01-07 1999-07-27 Nelson Industries, Inc. Tunable acoustic system
BR9810148A (pt) * 1997-06-20 2001-12-26 Mann & Hummel Filter Sistema de admissão
DE19818873C2 (de) * 1998-04-28 2001-07-05 Man B & W Diesel Ag Hubkolbenbrennkraftmaschine
DE10102040A1 (de) * 2001-01-18 2002-07-25 Mahle Filtersysteme Gmbh Schalldämpfer

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11808187B2 (en) 2021-03-01 2023-11-07 Caterpillar Inc. Noise attenuation components

Also Published As

Publication number Publication date
ATE369485T1 (de) 2007-08-15
EP1400662A1 (fr) 2004-03-24
DE10243884A1 (de) 2004-04-01
DE50307856D1 (de) 2007-09-20

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