EP1051562A1 - Silencer with a shunt resonator - Google Patents

Silencer with a shunt resonator

Info

Publication number
EP1051562A1
EP1051562A1 EP98963457A EP98963457A EP1051562A1 EP 1051562 A1 EP1051562 A1 EP 1051562A1 EP 98963457 A EP98963457 A EP 98963457A EP 98963457 A EP98963457 A EP 98963457A EP 1051562 A1 EP1051562 A1 EP 1051562A1
Authority
EP
European Patent Office
Prior art keywords
sound
shunt resonator
tubular elements
silencer
channel
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
Application number
EP98963457A
Other languages
German (de)
French (fr)
Other versions
EP1051562B1 (en
Inventor
Matthias Alex
Rolf Füsser
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
Filterwerk 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 Filterwerk Mann and Hummel GmbH filed Critical Filterwerk Mann and Hummel GmbH
Publication of EP1051562A1 publication Critical patent/EP1051562A1/en
Application granted granted Critical
Publication of EP1051562B1 publication Critical patent/EP1051562B1/en
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
    • F01N1/003—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages
    • F01N1/006—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages comprising at least one perforated tube extending from inlet to outlet of the silencer
    • 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
    • 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
    • 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
    • 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
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/20—Chambers being formed inside the exhaust pipe without enlargement of the cross section of the pipe, e.g. resonance chambers

Definitions

  • the invention relates to a silencer with a shunt resonator according to the preamble of the main claim.
  • the invention has for its object to design a muffler of the type mentioned in such a way that the damping behavior of the muffler can be calculated and influenced in a simple manner as a function of the sound frequency.
  • the muffler according to the invention is advantageously suitable, starting from the generic type, to solve the task with the characterizing features of the main claim. Because the acoustically active openings in the intake duct consist of tubular elements that extend from the intake duct into the housing volume of the shunt resonator, the damping behavior can be positively influenced by suitable dimensioning and arrangement of these tubular elements.
  • the changeable tubular elements as openings in the intake duct are particularly advantageous because they allow the shunt resonator, also called the Helmholtz resonator in the shunt, to be easily tuned for damping even low frequencies.
  • the volume of the shunt resonator is defined by the annular space between the intake duct and the outer housing, the design of the acoustic neck through the pipe elements taking a primary position.
  • the number and position of the tubular elements as well as their length and their diameter are advantageously chosen so that their acoustic damping gains are formed in a predetermined frequency range.
  • the position of the pipe elements in relation to the center of the shunt resonator can be shifted in the longitudinal direction so that occurring damping losses due to interaction with other components surrounding the silencer are shifted to frequency ranges in which this is not disturbing; in the best case, this can in turn lead to a gain in damping.
  • the sound-guiding duct is the intake duct for the intake air of an internal combustion engine, and the sound emissions to be damped are caused by the intake impulses of the individual cylinders, in particular of a diesel engine.
  • the muffler according to the invention can advantageously be manufactured in that the area with the pipe elements in the sound-conducting channel can be inserted as an injection molded part between two ends in the suction channel and that the enclosing housing volume of the shunt resonator, each with a housing half, is attached to one end of the channel and the two housing halves can be firmly joined together, including the injection molded part.
  • the tubular elements can also be produced separately and individually added and extrusion-coated during the production of the injection molded part.
  • FIG. 1 shows a section through an intake duct for the intake air of an internal combustion engine with tubular elements in the shunt resonator
  • Figure 2 shows a detail section through the intake duct in the area of the tubular elements
  • Figure 3 is a diagram of the damping curve as a function of frequency with different arrangements of the tubular elements.
  • an intake duct 1 is shown as a sound duct, which ensures the intake of intake air 2 of an internal combustion engine, which is not explained in more detail here.
  • the intake duct 1 is interrupted at one end 3 and 4 and includes an injection molded part 5, which is provided with pipe elements 6 as sound-conducting openings.
  • the injection molded part 5 is house parts 7 and 8 surrounded, which are fixedly attached to the pipe ends 3 and 4 and are tightly connected at a seam 9.
  • the middle of the area in which the tubular elements 6 are arranged is not in the center within the housing parts 7 and 8; dimension a is given here as the reference quantity, as the distance from the exciter side.
  • the housing volume between the housing parts 7 and 8 and the injection molded part 5 and the adjoining areas of the intake duct 1 forms a shunt resonator 10 for the acoustic vibrations of the pulsating intake air.
  • the operation of the silencer according to the invention is also described below with reference to FIG. 2, which shows the molded part 5 in section and will be explained with reference to FIG. 3, which shows a damping diagram of the sound vibrations.
  • the damping behavior of the arrangement shown in FIG. 1 can be influenced by the number, the position and the dimensions of the tubular elements 6.
  • the formula used here to calculate the resonance frequency f res of the silencer is:
  • V represents the housing volume of the shunt resonator 10.
  • a growing length L of the tubular elements 6 can thus bring about a reduction in the resonance frequency f res .
  • This has advantages for use in internal combustion engines because the shunt resonator 10 is primarily in its resonance contributes to damping and the high sound energies in the intake duct occur at relatively low frequencies.
  • the sum of all opening areas and thus the acoustically effective area A results from the number of tubular elements 6 and thus the openings.
  • the length L of the individual tubular elements 6 determines the overall acoustically effective length.
  • damping losses also occur with this arrangement.
  • the position of the so-called break-in frequencies f A and f B , at which these damping losses occur, can be influenced by the width and position of the area in which the tubular elements 6 are located in the intake duct 1 and thus also within the shunt resonator 10.
  • the dimension a shown in FIG. 1 and the number z of the tubular elements 6 can be changed here in such a way that the undesired damping losses are shifted into frequency ranges in which this is less disturbing. If, for example, the number z of the rows or the diameter D of the tubular elements 6 is increased, the resonance frequency f res becomes greater because of the thus increased acoustically effective area A. However, if you change the position of the area of the tubular elements 6 from the center position in the shunt resonator 10, it does not have an influence on the resonance frequency f res that has to be taken into account, but it does have an influence on the position of the break-in frequencies f A and f B. The decisive factor here is dimension a, which indicates the position of the area of the tubular elements 6 relative to the exciter side in the intake duct 1.
  • a shunt resonator 10 can have the surprising effect of a desired damping instead of a sound amplification even at certain frequency positions with damping losses. If, as in the exemplary embodiment according to the invention, this effect can be calculated and thus influenced, this can be used in an advantageous manner.

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)

Abstract

The invention relates to a silencer with a shunt resonator. Said shunt resonator (10) is formed by an outer housing volume which encompasses the sound-conducting channel (1) in a predetermined area. The sound-conducting channel (1) is connected to the shunt resonator (10) by openings (6). The openings in the sound-conducting channel (1) consist of tubular elements (6), preferably in a moulded part (5), extending from the sound-conducting channel (1) into the housing volume of the shunt resonator (10).

Description

Beschreibung description
Schalldämpfer mit einem NebenschlussresonatorSilencer with a shunt resonator
Stand der TechnikState of the art
Die Erfindung betrifft einen Schalldämpfer mit einem Nebenschlussresonator nach der Gattung des Hauptanspruchs.The invention relates to a silencer with a shunt resonator according to the preamble of the main claim.
Es ist bereits aus der Druckschrift „Ansauggeräuschdämpfung an Nutzfahrzeugen", Lothar Bending, ATZ, 4.4.78 bekannt, dass an einem Schalldämpfer im Ansaugkanal eines Verbrennungsmotors ein bestimmtes Längsstück mit einem äußeren Gehäuse umgeben ist. Im Bereich dieser Gehäuseüberdeckung ist der Ansaugkanal teilweise perforiert, wodurch das zwischen dem Ansaugkanal und dem äußeren Gehäuse gebildete Volumen akustisch angekoppelt wird.It is already known from the publication “Intake Noise Damping on Commercial Vehicles”, Lothar Bending, ATZ, April 4, 1978, that on a muffler in the intake duct of an internal combustion engine, a certain longitudinal piece is surrounded by an outer housing. In the area of this housing cover, the intake duct is partially perforated, whereby the volume formed between the intake duct and the outer housing is acoustically coupled.
AufgabenstellungTask
Der Erfindung liegt die Aufgabe zugrunde, einen Schalldämpfer der eingangs genannten Art so auszubilden, dass das Dämpfungsverhalten des Schalldämpfers in Abhängigkeit von der Schallfrequenz auf einfache Weise berechen- und beeinflussbar ist.The invention has for its object to design a muffler of the type mentioned in such a way that the damping behavior of the muffler can be calculated and influenced in a simple manner as a function of the sound frequency.
Vorteile der ErfindungAdvantages of the invention
Der erfindungsgemäße Schalldämpfer ist in vorteilhafter Weise geeignet, ausgehend von der gattungsgemäßen Art, die gestellte Aufgabe mit den kennzeichnenden Merkmalen des Hauptanspruchs zu lösen. Dadurch, dass die akustisch wirksamen Öffnungen im Ansaugkanal aus Rohrelementen bestehen, die sich vom Ansaugkanal in das Gehäusevolumen des Nebenschlussresonators erstrecken, kann durch eine geeignete Bemessung und Anordnung dieser Rohrelemente das Dämpfungsverhalten positiv beeinflusst werden.The muffler according to the invention is advantageously suitable, starting from the generic type, to solve the task with the characterizing features of the main claim. Because the acoustically active openings in the intake duct consist of tubular elements that extend from the intake duct into the housing volume of the shunt resonator, the damping behavior can be positively influenced by suitable dimensioning and arrangement of these tubular elements.
Die veränderbaren Rohrelemente als Öffnungen im Ansaugkanal sind vor allem deswegen vorteilhaft, weil damit der Nebenschlussresonator, auch Helmholtz- Resonator im Nebenschluß genannt, auf einfache Weise zur Dämpfung auch niederer Frequenzen abgestimmt werden kann.The changeable tubular elements as openings in the intake duct are particularly advantageous because they allow the shunt resonator, also called the Helmholtz resonator in the shunt, to be easily tuned for damping even low frequencies.
Das Volumen des Nebenschlussresonators ist durch den Ringraum zwischen dem Ansaugkanal und dem äußeren Gehäuse definiert, wobei die Gestaltung des akustischen Halses durch die Rohrelemente eine vorrangige Stellung einnimmt. Die Anzahl und Lage der Rohrelemente sowie ihre Länge und ihr Durchmesser sind dabei in vorteilhafter Weise so gewählt, dass sich ihre akustischen Dämpfungsgewinne in einem vorgegebenen Frequenzbereich ausbilden.The volume of the shunt resonator is defined by the annular space between the intake duct and the outer housing, the design of the acoustic neck through the pipe elements taking a primary position. The number and position of the tubular elements as well as their length and their diameter are advantageously chosen so that their acoustic damping gains are formed in a predetermined frequency range.
Um auch sogenannte Einbruchfrequenzen mit Dämpfungsverlusten beiderseits der Resonanzfrequenz vorteilhaft auszunutzen, kann die Lage der Rohrelemente im Verhältnis zur Mitte des Nebenschlussresonators in Längsrichtung so verschoben werden, dass auftretende Dämpfungsverluste durch Zusammenwirkung mit weiteren, den Schalldämpfer umgebenden Bauteilen in Frequenzbereiche verlagert sind, in denen dies nicht störend wirkt; im günstigsten Fall kann dies wiederum zu einem Dämpfungsgewinn führen.In order to take advantage of so-called break-in frequencies with damping losses on both sides of the resonance frequency, the position of the pipe elements in relation to the center of the shunt resonator can be shifted in the longitudinal direction so that occurring damping losses due to interaction with other components surrounding the silencer are shifted to frequency ranges in which this is not disturbing; in the best case, this can in turn lead to a gain in damping.
Bei einer besonders vorteilhaften Ausführungsform ist der schallführende Kanal der Ansaugkanal für die Ansaugluft eines Verbrennungsmotors und die zu dämpfenden Schallemissionen werden durch die Ansaugimpulse der einzelnen Zylinder, insbesondere eines Dieselmotors, hervorgerufen.In a particularly advantageous embodiment, the sound-guiding duct is the intake duct for the intake air of an internal combustion engine, and the sound emissions to be damped are caused by the intake impulses of the individual cylinders, in particular of a diesel engine.
Hergestellt kann der erfindungsgemäße Schalldämpfer in vorteilhafter Weise dadurch, dass der Bereich mit den Rohrelementen im schallführenden Kanal als Spritzgussformteil zwischen zwei Enden im Ansaugkanal einfügbar ist und dass das umschließende Gehäusevolumen des Nebenschlussresonators mit jeweils einer Gehäusehälfte an jeweils einem Ende des Kanals angebracht sind und die beiden Gehäusehälften unter Einschluss des Spritzgussformteils fest zusammenfügbar sind.The muffler according to the invention can advantageously be manufactured in that the area with the pipe elements in the sound-conducting channel can be inserted as an injection molded part between two ends in the suction channel and that the enclosing housing volume of the shunt resonator, each with a housing half, is attached to one end of the channel and the two housing halves can be firmly joined together, including the injection molded part.
Um eine einfache Gestaltungsmöglichkeit der Rohrelemente zu erreichen können die Rohrelemente auch separat hergestellt werden und einzeln bei der Herstellung des Spritzgussformteils angefügt und umspritzt werden.In order to achieve a simple design option for the tubular elements, the tubular elements can also be produced separately and individually added and extrusion-coated during the production of the injection molded part.
Zeichnungdrawing
Ein Ausführungsbeispiel des erfindungsgemäßen Schalldämpfers mit einem Nebenschlussresonator wird anhand der Figur der Zeichnung erläutert. Es zeigen:An embodiment of the silencer according to the invention with a shunt resonator is explained with reference to the figure of the drawing. Show it:
Figur 1 einen Schnitt durch einen Ansaugkanal für die Ansaugluft eines Verbrennungsmotors mit Rohrelementen im Nebenschlussresonator;1 shows a section through an intake duct for the intake air of an internal combustion engine with tubular elements in the shunt resonator;
Figur 2 einen Detailschnitt durch den Ansaugkanal im Bereich der Rohrelemente undFigure 2 shows a detail section through the intake duct in the area of the tubular elements and
Figur 3 ein Diagramm des Dämpfungsverlaufs in Abhängigkeit von der Frequenz bei verschiedenen Anordnungen der Rohrelemente.Figure 3 is a diagram of the damping curve as a function of frequency with different arrangements of the tubular elements.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 der Zeichnung ist ein Ansaugkanal 1 als Schallkanal dargestellt, der für die Zuführung von Ansaugluft 2 eines hier nicht näher erläuterten Verbrennungsmotors sorgt. Der Ansaugkanal 1 ist an jeweils einem Ende 3 und 4 unterbrochen und schließt ein Spritzgussformteil 5 ein, das mit Rohrelementen 6 als schallführende Öffnungen versehen ist. Das Spritzgussformteil 5 ist mit Ge- häuseteilen 7 und 8 umgeben, die an den Rohrenden 3 und 4 fest angebracht sind und an einer Nahtstelle 9 dicht miteinander verbunden sind. Die Mitte des Bereichs in dem die Rohrelemente 6 angeordnet sind befindet sich hier nicht mittig innerhalb der Gehäuseteile 7 und 8; als Bezugsgröße ist hier das Maß a, als Abstand von der Erregerseite, angegeben.In FIG. 1 of the drawing, an intake duct 1 is shown as a sound duct, which ensures the intake of intake air 2 of an internal combustion engine, which is not explained in more detail here. The intake duct 1 is interrupted at one end 3 and 4 and includes an injection molded part 5, which is provided with pipe elements 6 as sound-conducting openings. The injection molded part 5 is house parts 7 and 8 surrounded, which are fixedly attached to the pipe ends 3 and 4 and are tightly connected at a seam 9. The middle of the area in which the tubular elements 6 are arranged is not in the center within the housing parts 7 and 8; dimension a is given here as the reference quantity, as the distance from the exciter side.
Das Gehäusevolumen zwischen den Gehäuseteilen 7 und 8 und dem Spritzgussformteil 5 sowie den anschließenden Bereichen des Ansaugkanals 1 bildet für die Schallschwingungen der pulsierenden Ansaugluft einen Nebenschlussresonator 10. Die Funktionsweise des erfindungsgemäßen Schalldämpfers soll im Folgenden auch anhand Figur 2, die das Formteil 5 im Schnitt zeigt und anhand Figur 3, die ein Dämpfungsdiagramm der Schallschwingungen zeigt, erläutert werden.The housing volume between the housing parts 7 and 8 and the injection molded part 5 and the adjoining areas of the intake duct 1 forms a shunt resonator 10 for the acoustic vibrations of the pulsating intake air. The operation of the silencer according to the invention is also described below with reference to FIG. 2, which shows the molded part 5 in section and will be explained with reference to FIG. 3, which shows a damping diagram of the sound vibrations.
Das Dämpfungsverhalten der aus der Figur 1 ersichtlichen Anordnung kann durch die Anzahl, die Lage und die Abmessungen der Rohrelemente 6 beein- flusst werden. Die hier zugrundeliegende Formel zur Berechnung der Resonanzfrequenz fres des Schalldämpfers lautet:The damping behavior of the arrangement shown in FIG. 1 can be influenced by the number, the position and the dimensions of the tubular elements 6. The formula used here to calculate the resonance frequency f res of the silencer is:
wobei in which
A die Summe der akustisch wirksamen Fläche der Rohrelemente 6,A the sum of the acoustically effective area of the tubular elements 6,
L die Länge der Rohrelemente 6 undL the length of the tubular elements 6 and
V das Gehäusevolumen den Nebenschlussresonators 10 darstellt.V represents the housing volume of the shunt resonator 10.
Zusätzlich zu einer Vergrößerung des Gehäusevolumens V kann somit eine wachsende Länge L der Rohrelemente 6 eine Absenkung der Resonanzfrequenz fres bewirken. Das hat für die Anwendung bei Verbrennungsmotoren Vorteile, weil der Nebenschlussresonator 10 vornehmlich in seinem Reso- nanzbereich zur Dämpfung beiträgt und die hohen Schallenergien im Ansaugkanal bei relativ niedrigen Frequenzen auftreten.In addition to an increase in the housing volume V, a growing length L of the tubular elements 6 can thus bring about a reduction in the resonance frequency f res . This has advantages for use in internal combustion engines because the shunt resonator 10 is primarily in its resonance contributes to damping and the high sound energies in the intake duct occur at relatively low frequencies.
Aus der Anzahl der Rohrelemente 6 und damit der Öffnungen ergibt sich die Summe aller Öffnungsflächen und damit die akustisch wirksame Fläche A. Durch die Länge L der einzelnen Rohrelemente 6 wird insgesamt die akustisch wirksame Länge festgelegt. Bei einem vorgegebenen Gehäusevolumen V, einem festem Durchmesser D der Rohrelemente 6 und mit einer entsprechend gewählten Länge L der Rohrelemente 6 kann somit ein optimaler Dämpfungsbereich für den Schalldämpfer eingestellt werden.The sum of all opening areas and thus the acoustically effective area A results from the number of tubular elements 6 and thus the openings. The length L of the individual tubular elements 6 determines the overall acoustically effective length. With a given housing volume V, a fixed diameter D of the tubular elements 6 and with a correspondingly selected length L of the tubular elements 6, an optimal damping range for the silencer can be set.
Im Diagramm nach der Figur 3 sind beispielhaft unterschiedliche Ausgestaltungen der Anordnung mit den Rohrelementen 6 gezeigt. Die Schalldämpfung in (dB) ist hier über der Frequenz f aufgetragen. In einer Kurve 11 ist der Dämpfungsverlauf für eine Anordnung mit einer Reihe von Rohrelementen 6, in einer Kurve 12 ist eine Anordnung mit zwei Reihen von Rohrelementen 6 und in einer Kurve 13 ist eine Anordnung mit sechs Reihen der Rohrelemente 6 dargestellt. Es ist hieraus ersichtlich, dass mit einer zunehmenden Anzahl von Reihen mit Rohrelementen 6 der Bereich der Dämpfung, entsprechend der oben angegebenen Formel nahezu direkt proportional zur Zahl der Reihen, zu höheren Frequenzen wandert und dabei breiter wird.In the diagram according to FIG. 3, different configurations of the arrangement with the tubular elements 6 are shown by way of example. Sound attenuation in (dB) is plotted against frequency f. Curve 11 shows the damping curve for an arrangement with a row of tubular elements 6, curve 12 shows an arrangement with two rows of tubular elements 6 and curve 13 shows an arrangement with six rows of tubular elements 6. It can be seen from this that with an increasing number of rows with tubular elements 6, the range of damping, according to the formula given above, is almost directly proportional to the number of rows and moves to higher frequencies and becomes wider in the process.
Wie das Diagramm nach der Figur 3 auch zeigt, treten neben Dämpfungsgewinnen bei dieser Anordnung auch Dämpfungsverluste auf. Die Lage der sogenannten Einbruchfrequenzen fA und fB , bei denen diese Dämpfungsverluste auftreten, kann durch die Breite und Lage des Bereichs in dem die Rohrelemente 6 im Ansaugkanal 1 und somit auch innerhalb des Nebenschlussresonators 10 liegen, beeinflusst werden.As the diagram according to FIG. 3 also shows, in addition to damping gains, damping losses also occur with this arrangement. The position of the so-called break-in frequencies f A and f B , at which these damping losses occur, can be influenced by the width and position of the area in which the tubular elements 6 are located in the intake duct 1 and thus also within the shunt resonator 10.
Vor allem das aus der Figur 1 ersichtliche Maß a und die Anzahl z der Rohrelemente 6 können hier derart verändert werden, dass die unerwünschten Dämpfungsverluste in Frequenzbereiche verschoben werden, in denen dies weniger störend ist. Erhöht man beispielsweise die Anzahl z der Reihen oder den Durchmesser D der Rohrelemente 6 wird die Resonanzfrequenz fres größer wegen der somit vergrößerten akustisch wirksamen Fläche A. Ändert man jedoch die Lage des Bereichs der Rohrelemente 6 aus der Mittenlage im Nebenschlussresonator 10 heraus, so hat es zwar keinen zu berücksichtigenden Einfluß auf die Resonanzfrequenz fres, wohl aber auf die Lage der Einbruchfrequenzen fA und fB. Entscheidend ist hier das Maß a, das die Lage des Bereichs der Rohrelemente 6 relativ zu der Erregerseite im Ansaugkanal 1 angibt.In particular, the dimension a shown in FIG. 1 and the number z of the tubular elements 6 can be changed here in such a way that the undesired damping losses are shifted into frequency ranges in which this is less disturbing. If, for example, the number z of the rows or the diameter D of the tubular elements 6 is increased, the resonance frequency f res becomes greater because of the thus increased acoustically effective area A. However, if you change the position of the area of the tubular elements 6 from the center position in the shunt resonator 10, it does not have an influence on the resonance frequency f res that has to be taken into account, but it does have an influence on the position of the break-in frequencies f A and f B. The decisive factor here is dimension a, which indicates the position of the area of the tubular elements 6 relative to the exciter side in the intake duct 1.
Anordnungen mit dem erfindungsgemäßen Nebenschlussresonator nach der oben beschriebenen Art finden Anwendung in Ansaugsystemen, die eine Vielzahl von weiteren Bauteilen aufweisen und deren Bauteile sich gegenseitig beeinflussen. In derartig komplexen Systemen kann ein Nebenschlussresonator 10 auch bei bestimmten Frequenzlagen mit Dämpfungsverlusten die überraschende Wirkung einer erwünschten Dämpfung anstatt einer Schallverstärkung haben. Wenn, wie im erfindungsgemäßen Ausführungsbeispiel, dieser Effekt berechenbar und damit beeinflussbar ist, kann dies in vorteilhafter Weise ausgenutzt werden. Arrangements with the shunt resonator according to the invention of the type described above are used in intake systems which have a large number of further components and the components of which influence one another. In such complex systems, a shunt resonator 10 can have the surprising effect of a desired damping instead of a sound amplification even at certain frequency positions with damping losses. If, as in the exemplary embodiment according to the invention, this effect can be calculated and thus influenced, this can be used in an advantageous manner.
BezugszeichenlisteReference list
= schallführender Kanal (Ansaugkanal) = Ansaugluft = Ende des Ansaugkanals 1 = Ende des Ansaugkanals 1 = Spritzgussformteil = Rohrelemente = Gehäusehälfte = Gehäusehälfte= sound-conducting duct (intake duct) = intake air = end of intake duct 1 = end of intake duct 1 = injection molded part = pipe elements = housing half = housing half
= Nebenschlussresonator = Kurve eines Dämpfungsverlaufs = Kurve eines Dämpfungsverlaufs = Kurve eines Dämpfungsverlaufs = Shunt resonator = curve of an attenuation curve = curve of an attenuation curve = curve of an attenuation curve

Claims

Patentansprücheclaims
1 ) Schalldämpfer mit einem Nebenschlussresonator, bei dem1) Silencer with a shunt resonator, in which
- der Nebenschlussresonator (10) durch ein äußeres, den schallführenden Kanal (1 ) in einem vorgegebenen Bereich umschließendes Gehäusevolumen gebildet ist und bei dem der schallführende Kanal (1 ) mit dem Nebenschlussresonator (10) über Öffnungen (6) verbunden ist, dadurch gekennzeichnet, dass- The shunt resonator (10) is formed by an outer housing volume enclosing the sound-guiding channel (1) in a predetermined area and in which the sound-guiding channel (1) is connected to the shunt resonator (10) via openings (6), characterized in that that
- die Öffnungen aus Rohrelementen (6) bestehen, die sich vom schallführenden Kanal (1 ) in das Gehäusevolumen des Nebenschlussresonators (10) erstrek- ken.- The openings consist of tubular elements (6) which extend from the sound-conducting channel (1) into the housing volume of the shunt resonator (10).
2) Schalldämpfer nach Anspruch 1 , dadurch gekennzeichnet, dass2) silencer according to claim 1, characterized in that
- die Anzahl und Lage der Rohrelemente (6) sowie ihre Länge (L) und ihr Durchmesser (D) so gewählt sind, dass sich ihre akustische Dämpfungsgewinne in einem vorgegebenen Frequenzbereich ausbildet.- The number and position of the tubular elements (6) and their length (L) and their diameter (D) are chosen so that their acoustic damping gains are formed in a predetermined frequency range.
3) Schalldämpfer nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass3) muffler according to claim 1 or 2, characterized in that
- die Lage der Rohrelemente (6) im Verhältnis zur Mitte des Nebenschlussresonators (10) in Längsrichtung so gewählt ist, dass auftretende Dämpfungsverluste in Frequenzbereichen verlagert sind, die in Zusammenwirkung mit den, den Schalldämpfer umgebenden Bauteilen wiederum zu einem Dämpfungsgewinn führen.- The position of the tubular elements (6) in relation to the center of the shunt resonator (10) is chosen in the longitudinal direction so that damping losses occurring are shifted in frequency ranges, which in turn lead to a damping gain in cooperation with the components surrounding the silencer.
4) Schalldämpfer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass4) Silencer according to one of the preceding claims, characterized in that
- der schallführende Kanal der Ansaugkanal (1 ) für die Ansaugluft eines Verbrennungsmotors ist und die zu dämpfenden Schallemissionen durch die An- saugimpulse der einzelnen Zylinder, insbesondere eines Dieselmotors hervorgerufen werden.- The sound-guiding duct is the intake duct (1) for the intake air of an internal combustion engine and the sound emissions to be damped by the intake Suction pulses of the individual cylinders, especially a diesel engine.
5) Schalldämpfer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass5) Silencer according to one of the preceding claims, characterized in that
- der Bereich mit den Rohrelementen (6) im schallführenden Kanal (1 ) als Spritzgussformteil (5) zwischen zwei Enden (3,4) des Kanals (1 ) einfügbar ist und dass- The area with the pipe elements (6) in the sound-conducting channel (1) as an injection molded part (5) between two ends (3,4) of the channel (1) can be inserted and that
- das umschließende Gehäusevolumen des Nebenschlussresonators (10) mit jeweils einer Gehäusehälfte (7,8) an jeweils einem Ende (3,4) des Kanals (1 ) angebracht sind und die beiden Gehäusehälften (7,8) unter Einschluss des Spritzgussformteils (5) fest zusammenfügbar sind.- The enclosing housing volume of the shunt resonator (10), each with a housing half (7,8) at each end (3,4) of the channel (1), and the two housing halves (7,8) including the injection molded part (5) are firmly put together.
6) Schalldämpfer nach Anspruch 5, dadurch gekennzeichnet, dass6) silencer according to claim 5, characterized in that
- die Rohrelemente (6) separat hergestellt sind und einzeln bei der Herstellung des Spritzgussformteils (5) angefügt und umspritzt werden. - The tubular elements (6) are manufactured separately and individually added and extrusion-coated during the manufacture of the injection molded part (5).
EP98963457A 1997-11-24 1998-11-14 Silencer with a shunt resonator Expired - Lifetime EP1051562B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19751940A DE19751940C1 (en) 1997-11-24 1997-11-24 Intake silencer for motor vehicle internal combustion engine
DE19751940 1997-11-24
PCT/EP1998/007296 WO1999027237A1 (en) 1997-11-24 1998-11-14 Silencer with a shunt resonator

Publications (2)

Publication Number Publication Date
EP1051562A1 true EP1051562A1 (en) 2000-11-15
EP1051562B1 EP1051562B1 (en) 2002-03-06

Family

ID=7849612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98963457A Expired - Lifetime EP1051562B1 (en) 1997-11-24 1998-11-14 Silencer with a shunt resonator

Country Status (8)

Country Link
US (1) US6341663B1 (en)
EP (1) EP1051562B1 (en)
JP (1) JP2001524635A (en)
BR (1) BR9815023A (en)
CA (1) CA2311383C (en)
DE (2) DE19751940C1 (en)
ES (1) ES2174526T3 (en)
WO (1) WO1999027237A1 (en)

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CN104500178B (en) * 2013-11-27 2016-11-09 广东西电动力科技股份有限公司 A kind of complex muffler preventing and treating diesel generating set low-frequency noise
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Also Published As

Publication number Publication date
CA2311383A1 (en) 1999-06-03
EP1051562B1 (en) 2002-03-06
WO1999027237A1 (en) 1999-06-03
DE19751940C1 (en) 1999-03-25
US6341663B1 (en) 2002-01-29
DE59803310D1 (en) 2002-04-11
BR9815023A (en) 2002-04-30
ES2174526T3 (en) 2002-11-01
CA2311383C (en) 2007-05-15
JP2001524635A (en) 2001-12-04

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