EP0649982A1 - Side branch resonator - Google Patents

Side branch resonator Download PDF

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Publication number
EP0649982A1
EP0649982A1 EP94114289A EP94114289A EP0649982A1 EP 0649982 A1 EP0649982 A1 EP 0649982A1 EP 94114289 A EP94114289 A EP 94114289A EP 94114289 A EP94114289 A EP 94114289A EP 0649982 A1 EP0649982 A1 EP 0649982A1
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EP
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Prior art keywords
resonator
volume
frequency
bellows
excitation frequency
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Application number
EP94114289A
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German (de)
French (fr)
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EP0649982B1 (en
Inventor
Jiri Fiedler
Manfred Helget
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Knecht Filterwerk GmbH
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Knecht Filterwerk GmbH
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    • 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
    • F02M35/1222—Flow throttling or guiding by using adjustable or movable elements, e.g. valves, membranes, bellows, expanding or shrinking elements
    • 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
    • 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

Definitions

  • the invention relates to a shunt resonator according to the preamble of claim 1.
  • an intake silencer for internal combustion engines which has a shunt resonator in the area of the feed line to the carburetor.
  • JP-OS 58-93955 discloses a resonator which is still located in front of the air filter and whose volume is changed as a function of the speed of the motor with the aid of an actuating motor which moves a piston delimiting the resonator chamber.
  • the natural frequency of the resonator can be adapted to the respective excitation frequency in order to obtain optimal damping.
  • the disadvantage of this solution is that costly measurement and control technology has to be installed. For this reason, the proposed solution has been put into practice not yet implemented.
  • the invention is therefore concerned with the problem of providing a shunt resonator, the damping behavior of which can be adapted to different excitation frequencies and which can be produced particularly inexpensively, that is to say that it does not require any complex measurement and control technology.
  • the natural frequency is preferably adjusted automatically in that the resonator consists at least in part of an elastic bellows, the volume of which decreases with increasing speed as a result of the also increasing suction vacuum - with the build-up of a restoring force - and the spring characteristic of which runs such that the volume change as a result of the Increasing the speed leads to an adaptation of the natural frequency of the resonator to the increased excitation frequency.
  • the bellows can also represent only part of the resonator, e.g. B. the connecting pipe. Then the natural frequency of the resonator is adjusted by changing the length of the connecting tube.
  • the natural frequency of an intake silencer depends on the length l of the intake pipe, the volume V of the resonator and the cross section A of the intake pipe.
  • the natural frequency of the resonator can be adapted to the excitation frequency by targeted variation of one or more of the quantities mentioned, so that optimum damping is achieved in a broad frequency band.
  • the change in the resonator volume or in the other variables mentioned which influence the natural frequency takes place automatically without the interposition of a controller.
  • a particularly inexpensive embodiment of the invention is to use the negative pressure prevailing in the intake manifold to influence the parameters V, I and A mentioned.
  • a possible and inexpensive embodiment is the design of the resonator from an elastically deformable material in the form of a bellows, the volume of which changes depending on the negative pressure present.
  • a shunt resonator in the form of an elastic bellows 4 is connected to the intake pipe 3 between a reciprocating piston engine 1 and an air filter 2.
  • the changes in the resonator volume required for adapting the natural frequency to the excitation frequency are brought about by the negative pressure which arises in the intake manifold 3 as a function of the respective speed.
  • a higher negative pressure is created, so that the bellows 4 is built up by a contracting its spring characteristic dependent restoring force.
  • the negative pressure decreases and the restoring force increases the resonator volume.
  • the components of the travel limiter 5 and stop 6 are optionally provided only in the event that only two frequencies have to be particularly attenuated. It is then sufficient to design the resonator volume and the spring characteristic to the lower frequency to be damped and at the same time to select the spring characteristic so that the resonator reaches its smallest volume defined by path limiter 5 and stop 6 at the latest at the higher frequency to be damped.
  • This design therefore has the advantage that the spring characteristic only has to run through a certain point and may have a certain maximum slope, that is, it does not have to be defined exactly.

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  • 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)
  • Characterised By The Charging Evacuation (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)

Abstract

In order in the case of side branch resonator to achieve good damping (attenuation) of the suction noise cost effectively in a wide frequency range, the natural frequency of the resonator is adapted (matched) to the respective excitation frequency by automatically changing the geometry of its vibrating space (treadmill). For this purpose, the resonator is preferably designed as a bellows (4) having a defined spring characteristic. <IMAGE>

Description

Die Erfindung betrifft einen Nebenschluß-Resonator nach dem Oberbegriff des Anspruchs 1.The invention relates to a shunt resonator according to the preamble of claim 1.

Aus der AT-PS 216292 ist ein Ansaugschalldämpfer für Brennkraftmaschinen bekannt, der im Bereich der Zuleitung zum Vergaser einen Nebenschluß-Resonator aufweist.From AT-PS 216292 an intake silencer for internal combustion engines is known which has a shunt resonator in the area of the feed line to the carburetor.

Die Dämpfungswirkung dieses Nebenschluß-Resonators ist am höchsten im Bereich seiner Eigenfrequenz und nimmt bei Über- bzw. Unterschreitung der Eigenfrequenz ab. Nachteil dieses Standes der Technik ist es also, daß eine optimale Dämpfung nur bei einem bestimmten Motorbetriebszustand bzw. bei einer bestimmten Anregungsfrequenz, die der Eigenfrequenz des Nebenschluß-Resonators entspricht, erreicht wird.The damping effect of this shunt resonator is highest in the range of its natural frequency and decreases when the natural frequency is exceeded or fallen below. It is therefore a disadvantage of this prior art that optimum damping is only achieved with a specific engine operating state or with a specific excitation frequency that corresponds to the natural frequency of the shunt resonator.

Weiterhin ist aus JP-OS 58-93955 ein noch vor dem Luftfilter sitzender Resonator bekannt, dessen Volumen in Abhängigkeit von der Drehzahl des Motors unter Zuhilfenahme eines Stellmotors, der einen den Resonatorraum begrenzenden Kolben verfährt, verändert wird. Hierdurch kann die Eigenfrequenz des Resonators der jeweiligen Anregungsfrequenz angepaßt werden, um eine optimale Dämpfung zu erhalten. Nachteil dieser Lösung ist es jedoch, daß eine kostenintensive Meß- und Steuertechnik installiert werden muß. Aus diesem Grund hat sich die vorgeschlagene Lösung in der Praxis bisher nicht durchgesetzt.Furthermore, JP-OS 58-93955 discloses a resonator which is still located in front of the air filter and whose volume is changed as a function of the speed of the motor with the aid of an actuating motor which moves a piston delimiting the resonator chamber. As a result, the natural frequency of the resonator can be adapted to the respective excitation frequency in order to obtain optimal damping. The disadvantage of this solution, however, is that costly measurement and control technology has to be installed. For this reason, the proposed solution has been put into practice not yet implemented.

Die Erfindung beschäftigt sich daher mit dem Problem, einen Nebenschlußresonator bereitzustellen, dessen Dämpfungsverhalten an unterschiedliche Anregungsfrequenzen angepaßt werden kann und der insbesondere kostengünstig produziert werden kann, also keine aufwendige Meß- und Steuertechnik benötigt.The invention is therefore concerned with the problem of providing a shunt resonator, the damping behavior of which can be adapted to different excitation frequencies and which can be produced particularly inexpensively, that is to say that it does not require any complex measurement and control technology.

Dieses Problem wird durch den kennzeichnenden Teil des Hauptanspruchs gelöst. Vorteilhafte Weiterbildungen sind Gegenstand der Unteransprüche.This problem is solved by the characterizing part of the main claim. Advantageous further developments are the subject of the subclaims.

Durch die selbsttätige Anpassung der Eigenfrequenz des Resonators an die Anregungsfrequenz kann auf teure Meß- und Steuereinrichtungen verzichtet werden. Vorzugweise erfolgt die selbsttätige Anpassung der Eigenfrequenz dadurch, daß der Resonator zumindest zum Teil aus einem elastischen Faltenbalg besteht, dessen Volumen sich bei steigender Drehzahl infolge des ebenfalls steigenden Ansaugunterdrucks - unter Aufbau einer Rückstellkraft - verringert und dessen Federkennlinie so verläuft, daß die Volumenveränderung infolge der Drehzahlerhöhung zu einer Anpassung der Eigenfrequenz des Resonators an die gestiegene Anregungsfrequenz führt. Selbstverständlich kann der Faltenbalg auch nur einen Teil des Resonators darstellen, z. B. das Verbindungsrohr. Dann erfolgt die Anpassung der Eigenfrequenz des Resonators über eine Längenänderung des Verbindungsrohres.By automatically adapting the natural frequency of the resonator to the excitation frequency, expensive measuring and control devices can be dispensed with. The natural frequency is preferably adjusted automatically in that the resonator consists at least in part of an elastic bellows, the volume of which decreases with increasing speed as a result of the also increasing suction vacuum - with the build-up of a restoring force - and the spring characteristic of which runs such that the volume change as a result of the Increasing the speed leads to an adaptation of the natural frequency of the resonator to the increased excitation frequency. Of course, the bellows can also represent only part of the resonator, e.g. B. the connecting pipe. Then the natural frequency of the resonator is adjusted by changing the length of the connecting tube.

Nach der Helmholtz'schen Resonator-Gleichung ist die Eigenfrequenz eines Ansaugschalldämpfers abhängig von der Länge l des Ansaugrohres, dem Volumen V des Resonators und dem Querschnitt A des Ansaugrohres.According to the Helmholtz resonator equation, the natural frequency of an intake silencer depends on the length l of the intake pipe, the volume V of the resonator and the cross section A of the intake pipe.

Die Gleichung lautet:

f o = (c/2k) x (A : (l x V)) 1/2

Figure imgb0001


Es bedeuten:

fo
= Eigenfrequenz
c
= Schallgeschwindigkeit
k
= konstanter Faktor, ca. 3,1416
A
= Querschnitt des Verbindungsrohres
l
= Länge des Verbindungsrohres
V
= Volumen des Resonators
In der Praxis beschreibt die Helmholtz'sche Resonator-Gleichung nicht exakt die Eigenfrequenz. Durch Hinzufügen von Anpassungsfaktoren zur Länge des Verbindungsrohres, die vom Rohrquerschnitt und von der Länge des Verbindungsrohres abhängen, beschreibt die Gleichung exakt die Eigenfrequenz.The equation is:

f O = (c / 2k) x (A: (lx V)) 1/2
Figure imgb0001

It means:
f o
= Natural frequency
c
= Speed of sound
k
= constant factor, approx.3.1416
A
= Cross section of the connecting pipe
l
= Length of the connecting pipe
V
= Volume of the resonator
In practice, the Helmholtz resonator equation does not exactly describe the natural frequency. By adding adjustment factors to the length of the connecting pipe, which depend on the pipe cross section and the length of the connecting pipe, the equation exactly describes the natural frequency.

Durch gezielte Variation einer oder mehrerer der genannten Größen läßt sich die Eigenfrequenz des Resonators so an die Anregungsfrequenz anpassen, daß in einem breiten Frequenzband eine optimale Dämpfung erreicht wird.The natural frequency of the resonator can be adapted to the excitation frequency by targeted variation of one or more of the quantities mentioned, so that optimum damping is achieved in a broad frequency band.

Häufig genügt es in der Praxis auch, die Ansauggeräuschkennlinie nur bei bestimmten, hohe Geräuschpegel erzeugenden Frequenzen zu glätten. Bisher wurden z.B. im Falle von zwei besonders zu dämpfenden Frequenzen zwei Nebenschluß-Resonatoren mit entsprechenden Eigenfrequenzen vorgesehen. Erfindungsgemäß genügt in Zukunft ein Nebenschluß-Resonator, dessen Eigenfrequenz zumindest an die beiden störenden Frequenzen durch kontinuierliche oder auch diskontinuierliche Änderung des Resonator-Volumens angepaßt wird.In practice, it is often sufficient to smooth the intake noise characteristic only at certain frequencies that generate high noise levels. So far, two shunt resonators with corresponding natural frequencies have been provided, for example, in the case of two frequencies to be particularly damped. According to the invention, a shunt resonator, the natural frequency of which is at least at the two interfering frequencies by continuous or discontinuous frequencies, will suffice in the future Change in the resonator volume is adjusted.

Die Änderung des Resonator-Volumens bzw. der weiteren obengenannten, die Eigenfrequenz beeinflussenden Größen erfolgt erfindungsgemäß selbsttätig ohne Zwischenschaltung einer Steuerung.According to the invention, the change in the resonator volume or in the other variables mentioned which influence the natural frequency takes place automatically without the interposition of a controller.

Eine besonders kostengünstige Ausführungsform der Erfindung besteht darin, den im Saugrohr herrschenden Unterdruck zur Beeinflussung der genannten Parameter V, l und A zu verwenden. Eine mögliche und günstige Ausführungsform ist die Ausführung des Resonators aus einem elastisch verformbaren Material in Form eines Faltenbalgs, dessen Volumen sich abhängig vom anliegenden Unterdruck ändert.A particularly inexpensive embodiment of the invention is to use the negative pressure prevailing in the intake manifold to influence the parameters V, I and A mentioned. A possible and inexpensive embodiment is the design of the resonator from an elastically deformable material in the form of a bellows, the volume of which changes depending on the negative pressure present.

Die Erfindung wird im folgenden anhand eines Ausführungsbeispiels beschrieben. Es zeigt

Fig. 1
einen als einseitig geschlossener Faltenbalg ausgeführten Nebenschlußresonator.
The invention is described below using an exemplary embodiment. It shows
Fig. 1
a shunt resonator designed as a bellows closed on one side.

Zwischen einem Hubkolbenmotor 1 und einem Luftfilter 2 ist an die Saugrohrleitung 3 ein Nebenschluß-Resonator in Form eines elastischen Faltenbalges 4 angeschlossen.A shunt resonator in the form of an elastic bellows 4 is connected to the intake pipe 3 between a reciprocating piston engine 1 and an air filter 2.

Die für die Anpassung der Eigenfrequenz an die Anregungsfrequenz erforderlichen Änderungen des Resonatorvolumens werden durch den im Saugrohr 3 abhängig von der jeweiligen Drehzahl entstehenden Unterdruck herbeigeführt. Bei einer Drehzahlerhöhung des Motors entsteht ein höherer Unterdruck, so daß sich der Faltenbalg 4 unter Aufbau einer von seiner Federkennlinie abhängigen Rückstellkraft zusammenzieht. Bei nachlassender Drehzahl sinkt der Unterdruck und die Rückstellkraft bewirkt eine Vergrößerung des Resonatorvolumens.The changes in the resonator volume required for adapting the natural frequency to the excitation frequency are brought about by the negative pressure which arises in the intake manifold 3 as a function of the respective speed. When the speed of the engine increases, a higher negative pressure is created, so that the bellows 4 is built up by a contracting its spring characteristic dependent restoring force. As the speed decreases, the negative pressure decreases and the restoring force increases the resonator volume.

Die Bauteile Wegbegrenzer 5 und Anschlag 6 sind optional nur für den Fall vorgesehen, daß nur zwei Frequenzen besonders gedämpft werden müssen. Dann genügt es, das Resonatorvolumen und die Federkennlinie auf die niedrigere zu dämpfende Frequenz auszulegen und gleichzeitig die Federkennlinie so auszuwählen, daß spätestens bei der höheren zu dämpfenden Frequenz der Resonator sein durch Wegbegrenzer 5 und Anschlag 6 definiertes kleinstes Volumen erreicht.The components of the travel limiter 5 and stop 6 are optionally provided only in the event that only two frequencies have to be particularly attenuated. It is then sufficient to design the resonator volume and the spring characteristic to the lower frequency to be damped and at the same time to select the spring characteristic so that the resonator reaches its smallest volume defined by path limiter 5 and stop 6 at the latest at the higher frequency to be damped.

Diese Bauweise hat also den Vorteil, daß die Federkennlinie nur durch einen bestimmten Punkt verlaufen muß und eine bestimmte Maximalsteigung haben darf, also nicht exakt definiert werden muß.This design therefore has the advantage that the spring characteristic only has to run through a certain point and may have a certain maximum slope, that is, it does not have to be defined exactly.

Claims (3)

Nebenschluß-Resonator zur Schalldämpfung im Luftansaugtrakt eines Verbrennungsmotors oder eines Verdichters mit einer von der Schwingungsfrequenz der Luftmasse im Ansaugtrakt bestimmten Anregungsfrequenz,
dadurch gekennzeichnet,
daß sich die Eigenfrequenz des Resonators (4) während des Motorbetriebs der jeweiligen Anregungsfrequenz selbsttätig und ohne Zwischenschaltung einer Steuerung anpaßt, um bei allen Betriebszuständen eine optimale Dämpfung zu erzielen.Shunt resonator for sound absorption in the air intake tract of an internal combustion engine or a compressor with an excitation frequency determined by the oscillation frequency of the air mass in the intake tract,
characterized by
that the natural frequency of the resonator (4) adjusts itself automatically during motor operation to the respective excitation frequency and without the interposition of a controller in order to achieve optimal damping in all operating states. Nebenschluß-Resonator nach Anspruch 1
dadurch gekennzeichnet,
daß der Resonator zumindest zum Teil aus einem Faltenbalg (4) besteht, der bei einem dem Atmosphärendruck entsprechenden Innendruck ein definiertes Volumen oder eine definierte Länge aufweist und der sich bei Anliegen eines Unterdrucks im Ansaugtrakt (3) unter Aufbau einer Rückstellkraft volumenverkleinernd bzw. längenverkürzend zusammenzieht.Shunt resonator according to claim 1
characterized,
that the resonator consists at least in part of a bellows (4) which, at an internal pressure corresponding to the atmospheric pressure, has a defined volume or a defined length and which contracts when a negative pressure is present in the intake tract (3) to reduce the volume or reduce the length by building up a restoring force . Nebenschluß-Resonator nach Anspruch 2,
dadurch gekennzeichnet,
daß die Federkennlinie des Faltenbalges (4) bzw. der wegabhängige Aufbau der Rückstellkraft so verläuft, daß sich das Volumen des Resonators (4) bei Änderung der Anregungsfrequenz um einen bestimmten Faktor umgekehrt proportional zum Quadrat dieses Faktors verändert.Shunt resonator according to claim 2,
characterized by
that the spring characteristic of the bellows (4) or the path-dependent structure of the restoring force is such that the volume of the resonator (4) changes inversely proportional to the square of this factor when the excitation frequency changes by a certain factor.
EP94114289A 1993-10-22 1994-09-07 Side branch resonator Expired - Lifetime EP0649982B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4336112 1993-10-22
DE4336112A DE4336112A1 (en) 1993-10-22 1993-10-22 Shunt resonator

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EP0649982A1 true EP0649982A1 (en) 1995-04-26
EP0649982B1 EP0649982B1 (en) 1996-12-04

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Cited By (11)

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DE19641715A1 (en) * 1996-10-10 1998-04-16 Mann & Hummel Filter Intake system for an internal combustion engine
WO1999017012A1 (en) * 1997-10-01 1999-04-08 Filterwerk Mann+Hummel Gmbh Silencer with a bypass resonator
GB2357141A (en) * 1999-12-09 2001-06-13 Draftex Ind Ltd Combined resonator and coolant store for an IC engine
EP1158247A3 (en) * 2000-05-26 2002-01-02 ALSTOM Power N.V. Apparatus to reduce acoustic vibrations in a combustion chamber
WO2002048998A1 (en) * 2000-12-14 2002-06-20 ABB Fläkt AB Fluid-transporting system
FR2840652A1 (en) * 2002-06-07 2003-12-12 Trelleborg Automotive France Attenuation device for noises coming form i.c. engine operation and vehicle air conditioning system comprises membrane responding to predetermined vibration frequency and is positioned on hole in air inlet pipe
EP1120774A3 (en) * 2000-01-24 2004-11-03 EADS Deutschland Gmbh Acoustic absorber and method for sound absorption
CN102472264A (en) * 2009-08-03 2012-05-23 皇家飞利浦电子股份有限公司 Low restriction resonator with adjustable frequency characteristics for use in compressor nebulizer systems
EP3056723A1 (en) * 2015-02-10 2016-08-17 MAHLE Filter Systems Japan Corporation Intake noise reducing apparatus for internal combustion engine
EP3324033A1 (en) * 2016-11-10 2018-05-23 MAHLE Filter Systems Japan Corporation Air cleaner for internal combustion engine
US10738744B2 (en) 2016-11-16 2020-08-11 Ford Global Technologies, Llc Vacuum actuated multi-frequency quarter-wave resonator for an internal combustion engine

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DE19521025A1 (en) * 1995-06-13 1996-12-19 Mann & Hummel Filter Tube module
DE19543967B4 (en) * 1995-11-25 2006-10-12 Mahle Filtersysteme Gmbh Device for damping intake noise and method for sizing the device
DE19640980B4 (en) * 1996-10-04 2008-06-19 Alstom Device for damping thermoacoustic oscillations in a combustion chamber
DE19747245C1 (en) 1997-10-25 1999-04-29 Bayerische Motoren Werke Ag Internal combustion engine with an exhaust gas recirculation device, in particular a diesel internal combustion engine
KR100569901B1 (en) * 2003-10-07 2006-04-10 현대자동차주식회사 Noise control type intake hose structure
KR101211301B1 (en) 2011-01-13 2012-12-11 엘에스엠트론 주식회사 Resonator

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DE1052169B (en) * 1954-04-20 1959-03-05 Sigismond Wilman Intake silencer
FR1308738A (en) * 1961-09-29 1962-11-09 Polycarbure Self-adjusting resonance expansion chamber according to the frequency of the pulsations, arranged on the pulsating flow path of fluids, and its industrial applications
JPS5332222A (en) * 1976-09-06 1978-03-27 Kawasaki Heavy Ind Ltd Intake air nozzle silencer for internal combustion engine
FR2394676A1 (en) * 1977-06-17 1979-01-12 Lepape Roger Attachment for internal combustion engine - reduces atmospheric pollution by means of damping membrane in engine suction
EP0065076A2 (en) * 1981-05-15 1982-11-24 Klöckner-Humboldt-Deutz Aktiengesellschaft Resonance charging with variable intake system
DE3300499A1 (en) * 1983-01-08 1984-07-12 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V., 8000 München Sound absorber for passages through which liquids flow
JPH0219644A (en) * 1988-07-06 1990-01-23 Toyoda Spinning & Weaving Co Ltd Resonator type air cleaner
JPH04246221A (en) * 1991-01-31 1992-09-02 Toyoda Gosei Co Ltd Noise suppressing device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1052169B (en) * 1954-04-20 1959-03-05 Sigismond Wilman Intake silencer
FR1308738A (en) * 1961-09-29 1962-11-09 Polycarbure Self-adjusting resonance expansion chamber according to the frequency of the pulsations, arranged on the pulsating flow path of fluids, and its industrial applications
JPS5332222A (en) * 1976-09-06 1978-03-27 Kawasaki Heavy Ind Ltd Intake air nozzle silencer for internal combustion engine
FR2394676A1 (en) * 1977-06-17 1979-01-12 Lepape Roger Attachment for internal combustion engine - reduces atmospheric pollution by means of damping membrane in engine suction
EP0065076A2 (en) * 1981-05-15 1982-11-24 Klöckner-Humboldt-Deutz Aktiengesellschaft Resonance charging with variable intake system
DE3300499A1 (en) * 1983-01-08 1984-07-12 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V., 8000 München Sound absorber for passages through which liquids flow
JPH0219644A (en) * 1988-07-06 1990-01-23 Toyoda Spinning & Weaving Co Ltd Resonator type air cleaner
JPH04246221A (en) * 1991-01-31 1992-09-02 Toyoda Gosei Co Ltd Noise suppressing device

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DE19641715A1 (en) * 1996-10-10 1998-04-16 Mann & Hummel Filter Intake system for an internal combustion engine
WO1999017012A1 (en) * 1997-10-01 1999-04-08 Filterwerk Mann+Hummel Gmbh Silencer with a bypass resonator
US6494290B1 (en) * 1997-10-01 2002-12-17 Filterwerk Mann & Hummel Gmbh Noise suppressor with a bypass resonator
GB2357141A (en) * 1999-12-09 2001-06-13 Draftex Ind Ltd Combined resonator and coolant store for an IC engine
EP1120774A3 (en) * 2000-01-24 2004-11-03 EADS Deutschland Gmbh Acoustic absorber and method for sound absorption
EP1158247A3 (en) * 2000-05-26 2002-01-02 ALSTOM Power N.V. Apparatus to reduce acoustic vibrations in a combustion chamber
US6634457B2 (en) 2000-05-26 2003-10-21 Alstom (Switzerland) Ltd Apparatus for damping acoustic vibrations in a combustor
WO2002048998A1 (en) * 2000-12-14 2002-06-20 ABB Fläkt AB Fluid-transporting system
FR2840652A1 (en) * 2002-06-07 2003-12-12 Trelleborg Automotive France Attenuation device for noises coming form i.c. engine operation and vehicle air conditioning system comprises membrane responding to predetermined vibration frequency and is positioned on hole in air inlet pipe
CN102472264A (en) * 2009-08-03 2012-05-23 皇家飞利浦电子股份有限公司 Low restriction resonator with adjustable frequency characteristics for use in compressor nebulizer systems
EP2462347A1 (en) * 2009-08-03 2012-06-13 Koninklijke Philips Electronics N.V. Low restriction resonator with adjustable frequency characteristics for use in compressor nebulizer systems
CN102472264B (en) * 2009-08-03 2016-01-20 皇家飞利浦电子股份有限公司 For the low constraint resonator with characteristic of adjustable frequency in compressor atomiser system
US9790937B2 (en) 2009-08-03 2017-10-17 Koninklijke Philips N.V. Low restriction resonator with adjustable frequency characteristics for use in compressor nebulizer systems
EP3056723A1 (en) * 2015-02-10 2016-08-17 MAHLE Filter Systems Japan Corporation Intake noise reducing apparatus for internal combustion engine
CN105863906A (en) * 2015-02-10 2016-08-17 株式会社马勒滤清系统 Intake noise reducing apparatus for internal combustion engine
EP3324033A1 (en) * 2016-11-10 2018-05-23 MAHLE Filter Systems Japan Corporation Air cleaner for internal combustion engine
US10364779B2 (en) 2016-11-10 2019-07-30 Mahle Filter Systems Japan Corporation Air cleaner for internal combustion engine
US10738744B2 (en) 2016-11-16 2020-08-11 Ford Global Technologies, Llc Vacuum actuated multi-frequency quarter-wave resonator for an internal combustion engine

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DE4336112A1 (en) 1995-04-27
ES2096389T3 (en) 1997-03-01
EP0649982B1 (en) 1996-12-04
DE59401202D1 (en) 1997-01-16

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