EP0649982B1 - Side branch resonator - Google Patents

Side branch resonator Download PDF

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Publication number
EP0649982B1
EP0649982B1 EP94114289A EP94114289A EP0649982B1 EP 0649982 B1 EP0649982 B1 EP 0649982B1 EP 94114289 A EP94114289 A EP 94114289A EP 94114289 A EP94114289 A EP 94114289A EP 0649982 B1 EP0649982 B1 EP 0649982B1
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EP
European Patent Office
Prior art keywords
resonator
volume
frequency
side branch
intake section
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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
EP94114289A
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German (de)
French (fr)
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EP0649982A1 (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.
  • Such a resonator is known from JP-A-04246221.
  • There is a conventional rigid resonance chamber which is only connected to the main power line via a deformable connecting pipe. Changes in resonance can only be achieved there by deformation of the elastic connecting piece, as a result of which the overall frequency range to be influenced remains relatively small, since the elastic connecting tube cannot be made as large as desired.
  • 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, the volume of which depends on the speed of the engine with the aid of a servomotor that moves a piston that delimits 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 not yet become established in practice.
  • the invention in particular based on JP-A-04246221, deals with the problem of providing a shunt resonator whose damping behavior is adapted to different excitation frequencies due to the relatively large volume variability and which is inexpensive to produce. Furthermore, the device should be as small as possible, that is to say only require a small installation space.
  • the natural frequency of the resonator 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 automatically adjusted in that the resonator consists of an elastic bellows, the volume of which decreases with increasing speed as a result of the rising suction pressure - with the build-up of a restoring force - and whose spring core line runs in such a way that the volume change due to the increase in speed leads to an adaptation the natural frequency of the resonator leads to the increased excitation frequency.
  • the natural frequency of an intake silencer depends on the length 1 of the intake pipe, the volume V of the resonator and the cross section A of the intake pipe.
  • the Helmholtz resonator equation does not exactly describe the natural frequency.
  • the equation exactly describes the natural frequency.
  • 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 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 vacuum drops 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)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Characterised By The Charging Evacuation (AREA)

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.

Ein solcher Resonator ist aus JP-A-04246221 bekannt. Dort ist eine an sich übliche starr ausgebildete Resonanzkammer vorgesehen, die lediglich über ein verformbares Verbindungsrohr mit der Hauptstromleitung verbunden ist. Resonanzveränderungen können dort lediglich durch eine Verformung des elastischen Verbindungsstückes erreicht werden, wodurch der zu beeinflussende Gesamtfrequenzbereich relativ gering bleibt, da das elastische Verbindungsrohr nicht beliebig groß ausgebildet werden kann.Such a resonator is known from JP-A-04246221. There is a conventional rigid resonance chamber which is only connected to the main power line via a deformable connecting pipe. Changes in resonance can only be achieved there by deformation of the elastic connecting piece, as a result of which the overall frequency range to be influenced remains relatively small, since the elastic connecting tube cannot be made as large as desired.

Ferner ist aus AT-PS 216292 ein Ansaugschalldämpfer für Brennkraftmaschinen bekannt, der im Bereich der Zuleitung zum Vergaser einen Nebenschluß-Resonator aufweist.Furthermore, 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, the volume of which depends on the speed of the engine with the aid of a servomotor that moves a piston that delimits 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 not yet become established in practice.

Die Erfindung beschäftigt sich, insbesondere ausgehend von JP-A-04246221, mit dem Problem, einen Nebenschluß-Resonator bereitzustellen, dessen Dämpfungsverhalten durch relativ große Volumenveränderbarkeit an unterschiedliche Anregungsfrequenzen angepaßt ist und der kostengünstig zu produzieren ist. Des weiteren soll die Einrichtung möglichst klein bauen, das heißt nur geringen Einbauraum erfordern.The invention, in particular based on JP-A-04246221, deals with the problem of providing a shunt resonator whose damping behavior is adapted to different excitation frequencies due to the relatively large volume variability and which is inexpensive to produce. Furthermore, the device should be as small as possible, that is to say only require a small installation space.

Dieses Problem wird durch die Merkmale des Hauptanspruchs gelöst. Vorteilhafte Weiterbildungen sind Gegenstand der Unteransprüche.This problem is solved by the features 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. Die selbsttätige Anpassung der Eigenfrequenz erfolgt dadurch, daß der Resonator aus einem elastischen Faltenbalg besteht, dessen Volumen sich bei steigender Drehzahl infolge des ebenfalls steigenden Ansaugunterdrucks - unter Aufbau einer Rückstellkraft - verringert und dessen Federkernlinie so verläuft, daß die Volumenveränderung infolge der Drehzahlerhöhung zu einer Anpassung der Eigenfrequenz des Resonators an die gestiegene Anregungsfrequenz führt.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 automatically adjusted in that the resonator consists of an elastic bellows, the volume of which decreases with increasing speed as a result of the rising suction pressure - with the build-up of a restoring force - and whose spring core line runs in such a way that the volume change due to the increase in speed leads to an adaptation the natural frequency of the resonator leads to the increased excitation frequency.

Nach der Helmholz'schen Resonator-Gleichung ist die Eigenfrequenz eines Ansaugschalldämpfers abhängig von der Länge 1 des Ansaugrohres, dem Volumen V des Resonators und dem Querschnitt A des Ansaugrohres.According to the Helmholz resonator equation, the natural frequency of an intake silencer depends on the length 1 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 : (1 x V)) 1/2

Figure imgb0001
The equation is: f O = (c / 2k) x (A: (1 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
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 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.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.

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

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

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 Resonator-volumens.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 vacuum drops 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 (2)

  1. Side branch resonator for sound damping in the air intake section of an internal combustion engine or a compressor, with an excitation frequency determined by the oscillation frequency of the air mass in the intake section, in which the natural frequency adapts automatically during the operation of the engine to the respective excitation frequency, without the interposition of a control system, in order to achieve optimum damping in all operating states, characterized in that the resonator comprises overall a bellows (4) which has a defined volume or a defined length at an internal pressure corresponding to the atmospheric pressure and contracts with a reduction in volume and length when a vacuum is applied in the intake section (3), building up a restoring force in the process.
  2. Side branch resonator according to Claim 1, characterized in that the spring characteristic of the bellows (4) or of the travel-dependent build-up of the restoring force varies in such a way that, when the excitation frequency changes by a certain factor, the volume of the resonator (4) changes in inverse proportion to the square of this 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

Publications (2)

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

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DE (2) DE4336112A1 (en)
ES (1) ES2096389T3 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101211301B1 (en) 2011-01-13 2012-12-11 엘에스엠트론 주식회사 Resonator
US10302052B2 (en) 2016-11-16 2019-05-28 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
DE19641715A1 (en) * 1996-10-10 1998-04-16 Mann & Hummel Filter Intake system for an internal combustion engine
DE19743482A1 (en) * 1997-10-01 1999-04-08 Mann & Hummel Filter Silencer with a shunt resonator
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
GB2357141A (en) * 1999-12-09 2001-06-13 Draftex Ind Ltd Combined resonator and coolant store for an IC engine
DE10002984C1 (en) * 2000-01-24 2001-08-09 Daimler Chrysler Ag Acoustic absorber and method for sound absorption
DE10026121A1 (en) * 2000-05-26 2001-11-29 Alstom Power Nv Device for damping acoustic vibrations in a combustion chamber
SE0004624D0 (en) * 2000-12-14 2000-12-14 Flaekt Ab Fluid transport system
FR2840652B1 (en) * 2002-06-07 2006-09-01 Trelleborg Automotive France DEVICE FOR ATTENUATING NOISE FROM THE OPERATION OF THE INTERNAL COMBUSTION ENGINE AND / OR THE AIR CONDITIONING SYSTEM OF A VEHICLE
KR100569901B1 (en) * 2003-10-07 2006-04-10 현대자동차주식회사 Noise control type intake hose structure
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
JP6504844B2 (en) * 2015-02-10 2019-04-24 株式会社マーレ フィルターシステムズ Intake noise reduction device for internal combustion engine
JP6791724B2 (en) * 2016-11-10 2020-11-25 株式会社マーレ フィルターシステムズ Internal combustion engine air cleaner

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JPS599751B2 (en) * 1976-09-06 1984-03-05 川崎重工業株式会社 Internal combustion engine intake silencer
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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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101211301B1 (en) 2011-01-13 2012-12-11 엘에스엠트론 주식회사 Resonator
US10302052B2 (en) 2016-11-16 2019-05-28 Ford Global Technologies, Llc Vacuum actuated multi-frequency quarter-wave resonator for an internal combustion engine

Also Published As

Publication number Publication date
DE59401202D1 (en) 1997-01-16
DE4336112A1 (en) 1995-04-27
EP0649982A1 (en) 1995-04-26
ES2096389T3 (en) 1997-03-01

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