EP1051562B1 - Silencer with a shunt resonator - Google Patents

Silencer with a shunt resonator Download PDF

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Publication number
EP1051562B1
EP1051562B1 EP98963457A EP98963457A EP1051562B1 EP 1051562 B1 EP1051562 B1 EP 1051562B1 EP 98963457 A EP98963457 A EP 98963457A EP 98963457 A EP98963457 A EP 98963457A EP 1051562 B1 EP1051562 B1 EP 1051562B1
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EP
European Patent Office
Prior art keywords
sound
tubular elements
duct
silencer
resonator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98963457A
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German (de)
French (fr)
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EP1051562A1 (en
Inventor
Matthias Alex
Rolf Füsser
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Mann and Hummel GmbH
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Filterwerk Mann and Hummel GmbH
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Publication of EP1051562A1 publication Critical patent/EP1051562A1/en
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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 genus of the main claim.
  • a resonator is known from DE 1 147 769 which is used for damping Sound frequencies are provided in flowing gases.
  • the resonator a resonator chamber arranged in a shunt around a gas-carrying line on.
  • Pipe elements originate from this gas-carrying line, which protrude into the cavity and the line with the cavity connect.
  • the dimensions of the pipe elements and their number will be determined by the desired resonance frequency.
  • the arrangement of several Pipe elements can be made in a plane perpendicular to the direction of flow. With further training, several rows lying next to each other can also be used be arranged by tubular elements.
  • the invention has for its object a silencer of the beginning mentioned type so that it is easy and inexpensive to manufacture can be.
  • the muffler according to the invention is advantageously suitable starting from of the generic type, the task with the characteristic Features to solve the main claim. Because the acoustically effective openings in the intake duct consist of tubular elements, that extend from the intake duct into the housing volume of the shunt resonator can extend through a suitable dimensioning and arrangement of these Pipe elements have a positive influence on the damping behavior.
  • the silencer according to the invention can be manufactured in that the area with the pipe elements in the sound-conducting duct as an injection molded part is insertable between two ends in the intake duct and that the enclosing Housing volume of the shunt resonator with one each Half of the housing are attached to one end of the channel and the two The halves of the housing, including the injection molded part, can be firmly joined together are.
  • the position of the tubular elements can be used advantageously to the resonance frequency in relation to the center of the shunt resonator in the longitudinal direction so be postponed that damping losses occurring through interaction with other components surrounding the silencer in frequency ranges are relocated, in which this does not interfere; in the best case can in turn lead to a gain in damping.
  • the sound-conducting channel the intake duct for the intake air of an internal combustion engine and the damping sound emissions are caused by the intake impulses of the individual
  • Cylinder especially a diesel engine.
  • the pipe elements are also manufactured separately and individually at the Manufacture of the injection molded part added and overmolded.
  • 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 mainly contributes to damping in its resonance range and the high sound energies occur in the intake duct at relatively low frequencies.
  • the length L of the individual tube elements 6 makes them acoustic overall effective length set. With a given housing volume V, one fixed diameter D of the tubular elements 6 and with a corresponding The selected length L of the tubular elements 6 can thus provide an optimal damping range for the silencer.
  • 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 larger because of the thus increased acoustically effective area A. However, if the position of the area of the tubular elements 6 is changed from the central position in the shunt resonator 10, then there is no influence to be considered on the resonance frequency f res , but it does affect 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.

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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)

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Schalldämpfer mit einem Nebenschlussresonator nach der Gattung des Hauptanspruches.The invention relates to a silencer with a shunt resonator according to the genus of the main claim.

Es ist aus der DE 1 147 769 ein Resonator bekannt, welcher zur Dämpfung von Schallfrequenzen in strömenden Gasen vorgesehen ist. Hierzu weist der Resonator einen, um eine gasführende Leitung im Nebenschluss angeordneten Resonatorraum auf. Von dieser gasführenden Leitung gehen Rohrelemente aus, welche in den Resonatorraum hineinragen und die Leitung mit dem Resonatorraum verbinden. Die Abmessungen der Rohrelemente und deren Anzahl wird durch die gewünschte Resonanzfrequenz bestimmt. Die Anordnung mehrerer Rohrelemente kann in einer Ebene senkrecht zur Strömungsrichtung erfolgen. Bei weiteren Ausbildungen können auch mehrere nebeneinanderliegende Reihen von Rohrelementen angeordnet sein.A resonator is known from DE 1 147 769 which is used for damping Sound frequencies are provided in flowing gases. For this purpose, the resonator a resonator chamber arranged in a shunt around a gas-carrying line on. Pipe elements originate from this gas-carrying line, which protrude into the cavity and the line with the cavity connect. The dimensions of the pipe elements and their number will be determined by the desired resonance frequency. The arrangement of several Pipe elements can be made in a plane perpendicular to the direction of flow. With further training, several rows lying next to each other can also be used be arranged by tubular elements.

Diese Rohrelemente sind einzeln mit der Leitung verbunden, was in der Herstellung des Resonators aufwendig und teuer ist.These pipe elements are individually connected to the pipe, which is in the making of the resonator is complex and expensive.

Aufgabenstellungtask

Der Erfindung liegt die Aufgabe zugrunde, einen Schallddämpfer der eingangs genannten Art so auszubilden, dass dieser einfach und kostengünstig hergestellt werden kann.The invention has for its object a silencer of the beginning mentioned type so that it is easy and inexpensive to manufacture can be.

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 den 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 of the generic type, the task with the characteristic Features to solve the main claim. Because the acoustically effective openings in the intake duct consist of tubular elements, that extend from the intake duct into the housing volume of the shunt resonator can extend through a suitable dimensioning and arrangement of these Pipe elements have a positive influence on the damping behavior.

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 pipe elements as openings in the intake duct are above all advantageous because it is the shunt resonator, also the Helmholtz resonator called in the bypass, in a simple way for damping too lower frequencies can be tuned.

Hergestellt werden kann der erfindungsgemäße Schalldämpfer 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 zusammerifügbar sind.The silencer according to the invention can be manufactured in that the area with the pipe elements in the sound-conducting duct as an injection molded part is insertable between two ends in the intake duct and that the enclosing Housing volume of the shunt resonator with one each Half of the housing are attached to one end of the channel and the two The halves of the housing, including the injection molded part, can be firmly joined together are.

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 between by the annulus the intake duct and the outer housing defined, the design of the acoustic neck through the pipe elements takes a priority position. The number and position of the pipe elements as well as their length and their Diameters are advantageously chosen so that their acoustic Form attenuation gains 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. At so-called break-in frequencies with loss of attenuation on both sides The position of the tubular elements can be used advantageously to the resonance frequency in relation to the center of the shunt resonator in the longitudinal direction so be postponed that damping losses occurring through interaction with other components surrounding the silencer in frequency ranges are relocated, in which this does not interfere; in the best case 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 einzelnenIn a particularly advantageous embodiment, the sound-conducting channel the intake duct for the intake air of an internal combustion engine and the damping sound emissions are caused by the intake impulses of the individual

Zylinder, insbesondere eines Dieselmotors, hervorgerufen.Cylinder, especially a diesel engine.

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.To be able to achieve a simple design option for the tubular elements the pipe elements are also manufactured separately and individually at the Manufacture of the injection molded part added and overmolded.

Zeichnungdrawing

Ein Ausführungsbeispiel des erfindungsgemäßen Schalldämpfers mit einem Nebenschlussresonator wird anhand der Figur der Zeichnung erläutert. Es zeigen:

  • Figur 1 einen Schnitt durch einen Ansaugkanal für die Ansaugluft eines Verbrennungsmotors mit Rohrelementen im Nebenschlussresonator;
  • Figur 2 einen Detailschnitt durch den Ansaugkanal im Bereich der Rohrelemente und
  • Figur 3 ein Diagramm des Dämpfungsverlaufs in Abhängigkeit von der Frequenz bei verschiedenen Anordnungen der Rohrelemente.
    • 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:
  • 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 and
  • 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 Gehäuseteilen 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 Figure 1 of the drawing, an intake duct 1 is shown as a sound duct for the supply of intake air 2 of an internal combustion engine (not explained in more detail here) provides. The intake duct 1 is interrupted at one end 3 and 4 and includes an injection molded part 5, which with pipe elements 6th is provided as sound-conducting openings. The injection molded part 5 is with housing parts Surround 7 and 8, which are firmly attached to the pipe ends 3 and 4 are and are tightly connected at a seam 9. The middle of the The area in which the tubular elements 6 are arranged is not located here centrally within the housing parts 7 and 8; as a reference value here is dimension a, as the distance from the excitation 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 a shunt resonator for the sound vibrations of the pulsating intake air 10. The operation of the muffler according to the invention should in the following also with reference to FIG. 2, which shows the molded part 5 in section and with reference to Figure 3, which shows a damping diagram of the sound vibrations, explained become.

    Das Dämpfungsverhalten der aus der Figur 1 ersichtlichen Anordnung kann durch die Anzahl, die Lage und die Abmessungen der Rohrelemente 6 beeinflusst werden. Die hier zugrundeliegende Formel zur Berechnung der Resonanzfrequenz fres des Schalldämpfers lautet: fres = 340/2π * √A/ L*V,    wobei

  • A die Summe der akustisch wirksamen Fläche der Rohrelemente 6,
  • L die Länge der Rohrelemente 6 und
  • V das Gehäusevolumen den Nebenschlussresonators 10 darstellt.
    • 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: f res = 340 / 2π * √A / L * V, in which
  • A the sum of the acoustically effective area of the tubular elements 6,
  • L the length of the tubular elements 6 and
  • 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 Resonanzbereich 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 mainly contributes to damping in its resonance range and the high sound energies occur in the intake duct 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.From the number of pipe elements 6 and thus the openings Sum of all opening areas and thus the acoustically effective area A. The length L of the individual tube elements 6 makes them acoustic overall effective length set. With a given housing volume V, one fixed diameter D of the tubular elements 6 and with a corresponding The selected length L of the tubular elements 6 can thus provide an optimal damping range for the silencer.

    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 are exemplary the arrangement with the tubular elements 6 shown. Sound absorption in (dB) is plotted against frequency f. in a curve 11 is the damping curve for an arrangement with a series of tubular elements 6, in one Curve 12 is an arrangement with two rows of tubular elements 6 and in one 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 Pipe elements 6 the area of damping, corresponding to that specified above Formula almost directly proportional to the number of rows, to higher frequencies walks and gets wider.

    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 larger because of the thus increased acoustically effective area A. However, if the position of the area of the tubular elements 6 is changed from the central position in the shunt resonator 10, then there is no influence to be considered on the resonance frequency f res , but it does affect 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 The type described above are used in intake systems that have a variety of other components and their components mutually influence. A shunt resonator can be used in such complex systems 10 even with certain frequency situations with loss losses the surprising Effect of a desired damping instead of a sound reinforcement to have. If, as in the exemplary embodiment according to the invention, this Effect can be calculated and thus influenced, this can be done in an advantageous manner be exploited.

    BezugszeichenlisteLIST OF REFERENCE NUMBERS

    1 =1 =
    schallführender Kanal (Ansaugkanal)sound-conducting duct (intake duct)
    2 =2 =
    Ansaugluftintake
    3 =3 =
    Ende des Ansaugkanals 1End of the intake duct 1
    4 =4 =
    Ende des Ansaugkanals 1End of the intake duct 1
    5 =5 =
    SpritzgussformteilInjection molding
    6 =6 =
    Rohrelementetubular elements
    7 =7 =
    Gehäusehälftehousing half
    8 =8 =
    Gehäusehälftehousing half
    9 =9 =
    ..........
    10 =10 =
    Nebenschlussresonatorshunt resonator
    11 =11 =
    Kurve eines DämpfungsverlaufsCurve of an attenuation curve
    12 =12 =
    Kurve eines DämpfungsverlaufsCurve of an attenuation curve
    13 =13 =
    Kurve eines DämpfungsverlaufsCurve of an attenuation curve

    Claims (5)

    1. Silencer, having a bypass resonator, wherein
      the bypass resonator (10) is formed by an external housing chamber, which surrounds the sound-conducting duct (1) in a prescribed region, and wherein
      the sound-conducting duct (1) is connected to the bypass resonator (10) via openings (6), and
      the openings comprise tubular elements (6) which extend from the sound-conducting duct (1) into the housing chamber of the bypass resonator (10),
      characterised in that
      the region provided with the tubular elements (6) in the sound conducting duct (1) is insertable as a shaped injection-moulded component part (5) between two ends (3,4) of the duct (1), and in that
      the surrounding housing chamber of the bypass resonator (10) is mounted with one respective housing half (7,8) on each respective end (3,4) of the duct (1), and the two housing halves (7,8) are securedly interconnectable with the incorporation of the shaped injection-moulded component part (5).
    2. Silencer according to claim 1, characterised in that
      the number and position of the tubular elements (6) as well as their length (L) and their diameter (D) are so selected that their acoustic damping gains are achieved in a prescribed frequency range.
    3. Silencer according to claim 1 or 2, characterised in that
      the position of the tubular elements (6) relative to the centre of the bypass resonator (10), when viewed with respect to the longitudinal direction, is so selected that any damping losses which occur are displaced into frequency ranges which, in turn, lead to a damping gain in co-operation with the component parts surrounding the silencer.
    4. Silencer according to one of the preceding claims, characterised in that
      the sound-conducting duct is the intake duct (1) for the intake air of an internal combustion engine, and the sound emissions to be damped are caused by the intake pulses of the individual cylinders, more especially of a diesel engine.
    5. Silencer according to one of the preceding claims, characterised in that
      the tubular elements (6) are produced separately and are added individually during the production of the shaped injection-moulded component part (5) and extrusion-coated.
    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 1997-11-27
    PCT/EP1998/007296 WO1999027237A1 (en) 1997-11-24 1998-11-14 Silencer with a shunt resonator

    Publications (2)

    Publication Number Publication Date
    EP1051562A1 EP1051562A1 (en) 2000-11-15
    EP1051562B1 true 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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    CN101466949B (en) * 2006-05-03 2012-01-25 惠而浦股份有限公司 Resonator arrangement in an acoustic muffler for a refrigeration compressor

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    DE19902951A1 (en) * 1999-01-26 2000-07-27 Mann & Hummel Filter Induction device for internal combustion engine, in which resonance tube has common wall sector with line sector
    AU7772600A (en) * 1999-10-11 2001-04-23 Silentor Holding A/S A silencer
    US8820325B2 (en) * 2002-10-11 2014-09-02 The Regents Of The University Of California Bymixer apparatus and method for fast-response, adjustable measurement of mixed gas fractions in ventilation circuits
    DE202005007714U1 (en) * 2005-05-11 2006-09-21 Mann + Hummel Gmbh silencer
    KR100710342B1 (en) * 2006-02-07 2007-04-23 엘지전자 주식회사 Silencer
    KR101807783B1 (en) * 2012-06-18 2018-01-18 목포해양대학교 산학협력단 Soundproof duct for ship propellors using resonators
    KR101823215B1 (en) * 2013-02-12 2018-03-08 포레시아 이미션스 컨트롤 테크놀로지스, 유에스에이, 엘엘씨 Vehicle exhaust system with resonance damping
    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
    JP7005866B2 (en) * 2016-03-14 2022-01-24 株式会社竹中工務店 Exhaust noise reduction device
    KR101943607B1 (en) * 2017-05-18 2019-01-29 성균관대학교산학협력단 Acoustic resonator
    DE102017130661A1 (en) * 2017-12-20 2019-06-27 Montaplast Gmbh Broadband damper for a motor vehicle engine
    DE102022001220A1 (en) * 2022-04-09 2023-10-12 Hydac Technology Gmbh Damping device

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    CN101466949B (en) * 2006-05-03 2012-01-25 惠而浦股份有限公司 Resonator arrangement in an acoustic muffler for a refrigeration compressor

    Also Published As

    Publication number Publication date
    DE59803310D1 (en) 2002-04-11
    JP2001524635A (en) 2001-12-04
    CA2311383A1 (en) 1999-06-03
    CA2311383C (en) 2007-05-15
    DE19751940C1 (en) 1999-03-25
    BR9815023A (en) 2002-04-30
    WO1999027237A1 (en) 1999-06-03
    EP1051562A1 (en) 2000-11-15
    US6341663B1 (en) 2002-01-29
    ES2174526T3 (en) 2002-11-01

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