EP1959106B1 - Silencer for an exhaust system - Google Patents

Silencer for an exhaust system Download PDF

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Publication number
EP1959106B1
EP1959106B1 EP08150938A EP08150938A EP1959106B1 EP 1959106 B1 EP1959106 B1 EP 1959106B1 EP 08150938 A EP08150938 A EP 08150938A EP 08150938 A EP08150938 A EP 08150938A EP 1959106 B1 EP1959106 B1 EP 1959106B1
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EP
European Patent Office
Prior art keywords
chamber
resonator
expansion chamber
perforation
housing
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EP08150938A
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German (de)
French (fr)
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EP1959106B2 (en
EP1959106A1 (en
Inventor
Micha HÖRR
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Eberspaecher Exhaust Technology GmbH and Co KG
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J Eberspaecher GmbH and Co KG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • 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
    • F01N1/023—Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • 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
    • F01N2210/00—Combination of methods of silencing
    • F01N2210/04—Throttling-expansion and 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
    • F01N2490/00—Structure, disposition or shape of gas-chambers

Definitions

  • the present invention relates to a silencer for an exhaust system of an internal combustion engine, in particular in a motor vehicle, having the features of the preamble of claim 1.
  • a Helmholtz resonator in a silencer, which has a resonator chamber which is coupled in a sound-transmitting manner via a neck to an exhaust line arrangement of the silencer.
  • a resonator chamber which is coupled in a sound-transmitting manner via a neck to an exhaust line arrangement of the silencer.
  • branch points are disadvantageous in many ways.
  • additional noise may occur at the branch point at higher volume flows.
  • branches are comparatively expensive to produce.
  • the resonator volume can not be connected via a single branch to the exhaust pipe arrangement. At the junction comparatively large flow velocities can occur; so can it come to relatively high temperature fluctuations at the junction.
  • a muffler for an exhaust system of an internal combustion engine which has a housing and a guided through the housing exhaust line arrangement. Furthermore, an expansion chamber and a resonator chamber of a Helmholtz resonator are formed in the housing, whose respective neck is formed by at least one respective connecting tube arranged in the housing.
  • the exhaust pipe arrangement is passed through the expansion chamber without interruption and has a perforation within the expansion chamber. Furthermore, the respective connecting tube connects the expansion chamber with the resonator chamber.
  • the exhaust pipe arrangement comprises only a single inlet pipe and only a single outlet pipe.
  • the present invention is concerned with the problem of providing a muffler of the type mentioned an improved embodiment, in particular suitable for high-performance internal combustion engines, which are characterized by comparatively high volume flows. Furthermore, a solution is sought, which has a relatively low backpressure increase. In addition, a cost-effective production is desired.
  • the invention is based on the general idea of sound transmitting the exhaust pipe arrangement via a perforation with an expansion chamber, while the resonator neck connects said expansion chamber with the resonator chamber of the Helmholtz resonator.
  • This construction results in the expansion chamber very low flow velocities, which significantly reduces pressure losses in the flow through the muffler.
  • the muffler is characterized in particular for relatively high volume flows at the same time low pressure losses. Furthermore, the muffler is characterized in a special way for high-performance internal combustion engines or for large-volume internal combustion engines. Within the expansion chamber also temperature fluctuations can be reduced, which in particular has a positive effect on the fatigue strength of the muffler.
  • the exhaust pipe arrangement comprises either an inlet pipe and at least two Exhaust pipes or an outlet pipe and at least two inlet pipes, wherein the inlet pipes and outlet pipes are coupled to each other via at least one perforation having the coupling piece within the expansion chamber.
  • the exhaust pipe arrangement has a plurality of exhaust pipes, at least two of which each have a perforation within the expansion chamber, different damping characteristics can be achieved here by adapting the respective perforations accordingly.
  • the perforations may differ from each other in terms of number of holes and hole cross-section. This is particularly advantageous when the at least two exhaust pipes are traversed differently by exhaust gas as a function of load and / or speed of the internal combustion engine.
  • one of the exhaust pipes is activated only at larger exhaust gas flow rates. In this way, a different damping characteristic as a function of the exhaust gas volume flow can be realized comparatively easily.
  • a muffler 1 a housing 2, in which at least one expansion chamber 3 and a resonator 4 are formed. Furthermore, the muffler 1 has an exhaust pipe arrangement 5 and contains in its housing 2 a connecting pipe 6. In the illustrated embodiments, the muffler 1 also has an absorption chamber 7, which is also formed in the housing 2 and optionally with a sound-absorbing material or absorbent. 8 at least partially filled.
  • the muffler 1 is provided for installation in an exhaust system of an internal combustion engine, not shown here, which may be arranged in particular in a motor vehicle.
  • the resonator chamber 4 forms the resonance volume of a Helmholtz resonator 9 whose resonator neck is formed by the connecting tube 6.
  • the connecting pipe 6 is arranged in the housing 2 so as to connect the resonator chamber 4 to the expansion chamber 3 in a communicative manner.
  • the exhaust pipe assembly 5 is passed through the housing 2, thus having two ends 10 and 11, one of which - depending on the direction of flow of the exhaust pipe assembly 5 - forms an exhaust gas inlet, while the other then forms an exhaust gas outlet. Between the ends 10, 11, the exhaust pipe assembly 5 extends inside the housing 2. It is noteworthy that the exhaust pipe assembly 5 is at least passed through the expansion chamber 3 without interruption. In the examples shown, the exhaust pipe assembly 5 is passed through the entire housing 2 without interruption. This means, in particular, that the exhaust pipe arrangement 5 ensures a more or less effective flow guidance at each point between its ends 10, 11.
  • the exhaust pipe assembly 5 is passed through the expansion chamber 3 and has within the expansion chamber 3, a perforation 12, which is in particular formed by a plurality of holes 13 which break a flow-leading wall of the exhaust pipe assembly 5.
  • the perforation 12 thus creates a sound-transmitting connection between an interior 14 of the exhaust pipe assembly 5 and the expansion chamber 3. It is noteworthy that such a perforation 12 affects the flow through the exhaust pipe assembly 5 only comparatively slightly. In particular, owing to the perforation 12, only a comparatively small increase in pressure results. Furthermore, even at comparatively high mass flows, the perforation 12 does not lead to any significant additional noise formation within the muffler 1.
  • the sound to be damped by the Helmholtz resonator 9 can enter the expansion chamber 3 and activate the Helmholtz resonator 9 coupled therewith via the connecting tube 6.
  • the connecting tube 6 can effectively dampen.
  • the absorption chamber 7 can bring about a certain damping effect, in particular for high-frequency noise.
  • the absorption chamber 7 can preferably be coupled to the expansion chamber 3 via a further perforation 15, which is not visible here, in a sound-transmitting manner.
  • This perforation 15 may e.g. be provided in an intermediate wall 16 which separates the expansion chamber 3 from the absorption chamber 7.
  • the exhaust pipe arrangement 5 is passed through the resonator chamber 4.
  • the exhaust pipe assembly 5 is passed through the absorption chamber 7 in these embodiments.
  • the expansion chamber 3 and the resonator 4 and here the absorption chamber 7 are arranged axially one behind the other with respect to a longitudinal direction of the exhaust pipe assembly 5, wherein the absorption chamber 7 - if present - is arranged axially between the expansion chamber 3 and the resonator 4.
  • the exhaust pipe assembly 5 consists of a single exhaust pipe 18 here.
  • This exhaust pipe 18 is, in particular rectilinear, passed through the housing 2 and has the perforation 12 in a section passed through the expansion chamber 3.
  • This design is suitable for single-flow exhaust systems or for single-flow sections of exhaust systems.
  • Fig. 2 In the Fig. 2 embodiment shown is provided for a Hoflutige exhaust system or for a Hoflumble section of an exhaust system and is characterized in that the exhaust pipe assembly 5 has a plurality of parallel effetströmbare exhaust pipes 18, 19. In the example shown, only two such exhaust pipes 18, 19 are shown. Likewise, three and more exhaust pipes 18, 19 are conceivable.
  • the two exhaust pipes 18, 19 are each passed through the housing 2. At least one of the two exhaust pipes 18, 19 is also passed through the expansion chamber 3 and has within the expansion chamber 3 a provided with the perforation 12 section. In the embodiment shown, both exhaust pipes 18, 19 are passed through the expansion chamber 3 and each provided in a guided through the expansion chamber 3 section with such a perforation 12 or 12 '.
  • the perforations 12, 12 'of the two exhaust pipes 18, 19 are designed differently.
  • the two perforations 12, 12 ' are configured differently with respect to the sound-coupling effect.
  • the number of holes 13 in the one exhaust pipe 18 is smaller than the number of holes 13 'of the other exhaust pipe 19.
  • the holes 13 of an exhaust pipe 18 are here provided with a larger hole cross-section or hole diameter than the holes 13 'of the other exhaust pipe 19th
  • the exhaust pipe assembly 5 each have a coupling piece 20 which connects at least two individual lines 21, with a common bus 22.
  • the coupling piece 20 form a branch point, in which at least one of the two individual lines 21 branches off from the manifold 22.
  • the coupling piece 20 may form a junction, in which at least one of the individual lines 21 merges with the manifold 22.
  • the manifold 22 may form an inlet tube, while the two individual tubes 21 each form an outlet tube. In the reverse flow direction, the two individual lines 21 each form an inlet pipe, while the manifold 22 forms a common outlet pipe.
  • the individual lines 21 extend through the resonator chamber 4 and extend into the expansion chamber 3, so if necessary, through the absorption chamber 7 therethrough.
  • the manifold 22 only projects into the expansion chamber 3.
  • the arrangement of the lines is chosen such that the collecting line 22 extends through the resonator chamber 4 and extends into the expansion chamber 3, wherein the collecting line 22 can also extend through the absorption chamber 7.
  • the two individual lines 21 only extend into the expansion chamber 3.
  • the coupling piece 20 is disposed respectively within the expansion chamber 3.
  • the coupling piece 20 is preferably equipped with the perforation 12.
  • the coupling piece 20 may be manufactured in shell construction and thus in particular be assembled from two half-shells. At least one of these shells can then be provided with the perforation 12.
  • the intermediate walls 16 and 17 are used to separate the individual chambers 3, 4, 7 from each other and at the same time form a stiffening of the housing 2. Further, the intermediate walls 16, 17 are used to hold the pipes of the muffler 1, so the connecting pipe 6 and the pipes or lines 18, 19, 21, 22 of the exhaust pipe arrangement 5.
  • the respective muffler 1 each only a single Helmholtz resonator 9 on.

Abstract

The silencer (1) has an exhaust pipe arrangement (5) conducted through a housing (2), and an expansion chamber (3) formed in the housing. A resonator chamber (4) of a Helmholtz resonator (9) is formed in the housing. The exhaust pipe arrangement is conducted through the expansion chamber in an uninterruptible manner and exhibits a perforation (12) within the expansion chamber, where a connecting pipe (6) of the expansion chamber connects with the resonator chamber in a communicating manner. The connecting pipe is conducted through an absorption chamber (7).

Description

Die vorliegende Erfindung betrifft einen Schalldämpfer für eine Abgasanlage einer Brennkraftmaschine, insbesondere in einem Kraftfahrzeug, mit den Merkmalen des Oberbegriffs des Anspruchs 1.The present invention relates to a silencer for an exhaust system of an internal combustion engine, in particular in a motor vehicle, having the features of the preamble of claim 1.

Um bei Abgasanlagen vergleichsweise tiefe Frequenzen effektiv dämpfen zu können, ist es bekannt, in einem Schalldämpfer einen Helmholtz-Resonator auszubilden, der eine Resonatorkammer aufweist, die über einen Hals schallübertragend mit einer Abgasleitungsanordnung des Schalldämpfers gekoppelt ist. Für die schallübertragende Kopplung des Resonatorhalses mit der Abgasleitungsanordnung ist es grundsätzlich möglich, den Resonatorhals an einer geeigneten Stelle von der Abgasleitungsanordnung abzuzweigen. Derartige Abzweigstellen sind in vielfacher Sicht nachteilig. Zum einen können an der Abzweigstelle bei höheren Volumenströmen zusätzliche Geräusche entstehen. Des Weiteren sind Abzweigungen vergleichsweise teuer in ihrer Herstellung. Bei mehrflutigen Abgasanlagen kann das Resonatorvolumen nicht mehr über eine einzige Abzweigung an die Abgasleitungsanordnung angeschlossen werden. An der Abzweigung können vergleichsweise große Strömungsgeschwindigkeiten auftreten; ebenso kann es zu relativ hohen Temperaturschwankungen an der Abzweigung kommen.In order to be able to effectively dampen comparatively low frequencies in exhaust systems, it is known to form a Helmholtz resonator in a silencer, which has a resonator chamber which is coupled in a sound-transmitting manner via a neck to an exhaust line arrangement of the silencer. For the sound-transmitting coupling of the resonator neck to the exhaust-gas line arrangement, it is basically possible to branch off the resonator neck at a suitable point from the exhaust-gas line arrangement. Such branch points are disadvantageous in many ways. On the one hand, additional noise may occur at the branch point at higher volume flows. Furthermore, branches are comparatively expensive to produce. In mehrflutigen exhaust systems, the resonator volume can not be connected via a single branch to the exhaust pipe arrangement. At the junction comparatively large flow velocities can occur; so can it come to relatively high temperature fluctuations at the junction.

Alternativ ist es grundsätzlich möglich, den Resonatorhals mit einer Expansionskammer zu koppeln, in welcher die Abgasleitungsanordnung eine Unterbrechung aufweist. Jedoch besitzt auch eine derartige Anordnung vielfältige Nachteile. Auch hier können sich z.B. bei großen Volumenströmen Geräusche entwickeln. Zusätzlich besitzt eine derartige Anordnung einen vergleichsweise hohen Druckverlust.Alternatively, it is basically possible to couple the resonator neck with an expansion chamber in which the exhaust pipe arrangement has an interruption. However, such an arrangement has many disadvantages. Here too, e.g. develop noises at high volume flows. In addition, such an arrangement has a comparatively high pressure loss.

Aus der GB 2 285 283 A ist ein Schalldämpfer für eine Abgasanlage einer Brennkraftmaschine bekannt, der ein Gehäuse und eine durch das Gehäuse hindurchgeführte Abgasleitungsanordnung aufweist. Ferner sind im Gehäuse eine Expansionskammer sowie eine Resonatorkammer eines Helmholtz-Resonators ausgebildet, dessen jeweiliger Hals durch zumindest ein jeweiliges im Gehäuse angeordnetes Verbindungsrohr gebildet ist. Die Abgasleitungsanordnung ist durch die Expansionskammer unterbrechungsfrei hindurchgeführt und weist innerhalb der Expansionskammer eine Perforation auf. Ferner verbindet das jeweilige Verbindungsrohr die Expansionskammer mit der Resonatorkammer. Beim bekannten Schalldämpfer umfasst die Abgasleitungsanordnung nur ein einziges Einlassrohr und nur ein einziges Auslassrohr.From the GB 2 285 283 A a muffler for an exhaust system of an internal combustion engine is known, which has a housing and a guided through the housing exhaust line arrangement. Furthermore, an expansion chamber and a resonator chamber of a Helmholtz resonator are formed in the housing, whose respective neck is formed by at least one respective connecting tube arranged in the housing. The exhaust pipe arrangement is passed through the expansion chamber without interruption and has a perforation within the expansion chamber. Furthermore, the respective connecting tube connects the expansion chamber with the resonator chamber. In the known muffler, the exhaust pipe arrangement comprises only a single inlet pipe and only a single outlet pipe.

Die vorliegende Erfindung beschäftigt sich mit dem Problem, für einen Schalldämpfer der eingangs genannten Art eine verbesserte Ausführungsform anzugeben, die sich insbesondere für leistungsstarke Brennkraftmaschinen eignet, die sich durch vergleichsweise hohe Volumenströme charakterisieren. Ferner ist eine Lösung angestrebt, die einen vergleichsweise niedrigen Gegendruckanstieg aufweist. Außerdem ist eine kostengünstige Fertigung erwünscht.The present invention is concerned with the problem of providing a muffler of the type mentioned an improved embodiment, in particular suitable for high-performance internal combustion engines, which are characterized by comparatively high volume flows. Furthermore, a solution is sought, which has a relatively low backpressure increase. In addition, a cost-effective production is desired.

Dieses Problem wird erfindungsgemäß durch den Gegenstand des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.This problem is solved according to the invention by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.

Die Erfindung beruht auf dem allgemeinen Gedanken, die Abgasleitungsanordnung über eine Perforation schallübertragend mit einer Expansionskammer zu koppeln, während der Resonatorhals besagte Expansionskammer mit der Resonatorkammer des Helmholtzresonators verbindet. Durch diese Bauweise ergeben sich in der Expansionskammer sehr geringe Strömungsgeschwindigkeiten, was Druckverluste bei der Durchströmung des Schalldämpfers signifikant reduziert. Der Schalldämpfer eignet sich dadurch insbesondere für relativ hohe Volumenströme bei gleichzeitig niedrigen Druckverlusten. Ferner eignet sich der Schalldämpfer dadurch in besonderer Weise für leistungsstarke Brennkraftmaschinen beziehungsweise für großvolumige Brennkraftmaschinen. Innerhalb der Expansionskammer können außerdem Temperaturschwankungen reduziert werden, was sich insbesondere für die Dauerfestigkeit des Schalldämpfers positiv auswirkt.The invention is based on the general idea of sound transmitting the exhaust pipe arrangement via a perforation with an expansion chamber, while the resonator neck connects said expansion chamber with the resonator chamber of the Helmholtz resonator. This construction results in the expansion chamber very low flow velocities, which significantly reduces pressure losses in the flow through the muffler. The muffler is characterized in particular for relatively high volume flows at the same time low pressure losses. Furthermore, the muffler is characterized in a special way for high-performance internal combustion engines or for large-volume internal combustion engines. Within the expansion chamber also temperature fluctuations can be reduced, which in particular has a positive effect on the fatigue strength of the muffler.

Beim erfindungsgemäßen Schalldämpfer umfasst die Abgasleitungsanordnung entweder ein Einlassrohr und zumindest zwei Auslassrohre oder ein Auslassrohr und zumindest zwei Einlassrohre, wobei die Einlassrohre und Auslassrohre über wenigstens ein die Perforation aufweisendes Kupplungsstück innerhalb der Expansionskammer miteinander gekoppelt sind.In the muffler according to the invention, the exhaust pipe arrangement comprises either an inlet pipe and at least two Exhaust pipes or an outlet pipe and at least two inlet pipes, wherein the inlet pipes and outlet pipes are coupled to each other via at least one perforation having the coupling piece within the expansion chamber.

Ein weiterer wichtiger Vorteil der erfindungsgemäß vorgeschlagenen Bauweise kann darin gesehen werden, dass die Abgasleitungsanordnung durch das gesamte Gehäuse des Schalldämpfers oder zumindest durch die Expansionskammer unterbrechungsfrei hindurchgeführt werden kann, was die Abstützung der einzelnen Bestandteile der Abgasleitungsanordnung innerhalb des Gehäuses, beispielsweise mittels entsprechender Zwischenwände, extrem vereinfacht.Another important advantage of the proposed construction according to the invention can be seen in the fact that the exhaust pipe assembly can be passed through the entire housing of the muffler or at least through the expansion chamber without interruption, which is the support of the individual components of the exhaust pipe assembly within the housing, for example by means of corresponding partitions, extremely simplified.

Sofern die Abgasleitungsanordnung mehrere Abgasrohre aufweist, von denen zumindest zwei innerhalb der Expansionskammer jeweils eine Perforation aufweisen, lassen sich hier unterschiedliche Dämpfungscharakteristika erzielen, indem die jeweilige Perforation entsprechend adaptiert wird. Beispielsweise können sich die Perforationen hinsichtlich Lochzahl und Lochquerschnitt voneinander unterscheiden. Dies ist insbesondere dann von Vorteil, wenn die wenigstens zwei Abgasrohre in Abhängigkeit von Last und/oder Drehzahl der Brennkraftmaschine unterschiedlich von Abgas durchströmt werden. Beispielsweise wird eines der Abgasrohre erst bei größeren Abgasvolumenströmen aktiviert. Auf diese Weise kann vergleichsweise einfach eine unterschiedliche Dämpfungscharakteristik in Abhängigkeit des Abgasvolumenstroms realisiert werden.If the exhaust pipe arrangement has a plurality of exhaust pipes, at least two of which each have a perforation within the expansion chamber, different damping characteristics can be achieved here by adapting the respective perforations accordingly. For example, the perforations may differ from each other in terms of number of holes and hole cross-section. This is particularly advantageous when the at least two exhaust pipes are traversed differently by exhaust gas as a function of load and / or speed of the internal combustion engine. For example, one of the exhaust pipes is activated only at larger exhaust gas flow rates. In this way, a different damping characteristic as a function of the exhaust gas volume flow can be realized comparatively easily.

Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen.Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Es zeigen, jeweils schematisch,

Fig. 1 und 2
jeweils eine stark vereinfachte, prinzipielle Schnittansicht eines nicht vom Schutzumfang der Ansprüche erfassten Schalldämpfers bei verschiedenen Ausführungsformen,
Fig. 3 und 4
jeweils eine stark vereinfachte, prinzipielle Schnittansicht eines erfindungsgemäßen Schalldämpfers bei verschiedenen Ausführungs- formen.
Show, in each case schematically,
Fig. 1 and 2
in each case a greatly simplified, schematic sectional view of a silencer not covered by the scope of the claims in various embodiments,
3 and 4
in each case a greatly simplified, schematic sectional view of a silencer according to the invention in various embodiments.

Entsprechend den Fig. 1 bis 4 weist ein Schalldämpfer 1 ein Gehäuse 2 auf, in dem zumindest eine Expansionskammer 3 und eine Resonatorkammer 4 ausgebildet sind. Des weiteren weist der Schalldämpfer 1 eine Abgasleitungsanordnung 5 auf und enthält in seinem Gehäuse 2 ein Verbindungsrohr 6. Bei den gezeigten Ausführungsbeispielen weist der Schalldämpfer 1 außerdem eine Absorptionskammer 7 auf, die ebenfalls im Gehäuse 2 ausgebildet ist und die optional mit einem Schallschluckstoff oder Absorptionsmittel 8 zumindest teilweise befüllt sein kann.According to the Fig. 1 to 4 a muffler 1 a housing 2, in which at least one expansion chamber 3 and a resonator 4 are formed. Furthermore, the muffler 1 has an exhaust pipe arrangement 5 and contains in its housing 2 a connecting pipe 6. In the illustrated embodiments, the muffler 1 also has an absorption chamber 7, which is also formed in the housing 2 and optionally with a sound-absorbing material or absorbent. 8 at least partially filled.

Der Schalldämpfer 1 ist zum Einbau in eine hier nicht gezeigte Abgasanlage einer Brennkraftmaschine vorgesehen, die insbesondere in einem Kraftfahrzeug angeordnet sein kann.The muffler 1 is provided for installation in an exhaust system of an internal combustion engine, not shown here, which may be arranged in particular in a motor vehicle.

Beim Schalldämpfer 1 bildet die Resonatorkammer 4 das Resonanzvolumen eines Helmholtzresonators 9, dessen Resonatorhals durch das Verbindungsrohr 6 gebildet ist. Das Verbindungsrohr 6 ist im Gehäuse 2 so angeordnet, dass es die Resonatorkammer 4 mit der Expansionskammer 3 kommunizierend verbindet.In the case of the muffler 1, the resonator chamber 4 forms the resonance volume of a Helmholtz resonator 9 whose resonator neck is formed by the connecting tube 6. The connecting pipe 6 is arranged in the housing 2 so as to connect the resonator chamber 4 to the expansion chamber 3 in a communicative manner.

Die Abgasleitungsanordnung 5 ist durch das Gehäuse 2 hindurchgeführt, besitzt somit zwei Enden 10 und 11, von denen das eine - je nach Durchströmungsrichtung der Abgasleitungsanordnung 5 - einen Abgaseinlass bildet, während das andere dann einen Abgasauslass bildet. Zwischen den Enden 10, 11 verläuft die Abgasleitungsanordnung 5 im Inneren des Gehäuses 2. Bemerkenswert ist dabei, dass die Abgasleitungsanordnung 5 zumindest durch die Expansionskammer 3 unterbrechungsfrei hindurchgeführt ist. In den gezeigten Beispielen ist die Abgasleitungsanordnung 5 durch das ganze Gehäuse 2 unterbrechungsfrei hindurch geführt. Das bedeutet insbesondere, dass die Abgasleitungsanordnung 5 zwischen ihren Enden 10, 11 an jeder Stelle eine mehr oder weniger effektive Strömungsführung gewährleistet. Die Abgasleitungsanordnung 5 ist durch die Expansionskammer 3 hindurchgeführt und weist innerhalb der Expansionskammer 3 eine Perforation 12 auf, die insbesondere durch eine Vielzahl von Löchern 13 gebildet ist, die eine strömungsführende Wand der Abgasleitungsanordnung 5 durchbrechen. Die Perforation 12 schafft somit eine schallübertragende Verbindung zwischen einem Inneren 14 der Abgasleitungsanordnung 5 und der Expansionskammer 3. Bemerkenswert ist dabei, das eine derartige Perforation 12 die Durchströmung der Abgasleitungsanordnung 5 nur vergleichsweise geringfügig beeinträchtigt. Insbesondere ergibt sich aufgrund der Perforation 12 nur ein vergleichsweise geringer Druckanstieg. Ferner führt die Perforation 12 auch bei vergleichsweise hohen Massenströmen zu keiner signifikanten zusätzlichen Geräuschbildung innerhalb des Schalldämpfers 1. Im Betrieb kann nun der vom Helmholtzresonator 9 zu bedämpfende Schall in die Expansionskammer 3 eintreten und den damit über das Verbindungsrohr 6 gekoppelte Helmholtzresonator 9 aktivieren. Hierdurch lassen sich insbesondere tieffrequente Störgeräusche einer bestimmten Störfrequenz beziehungsweise eines bestimmten Störfrequenzbandes effektiv bedämpfen.The exhaust pipe assembly 5 is passed through the housing 2, thus having two ends 10 and 11, one of which - depending on the direction of flow of the exhaust pipe assembly 5 - forms an exhaust gas inlet, while the other then forms an exhaust gas outlet. Between the ends 10, 11, the exhaust pipe assembly 5 extends inside the housing 2. It is noteworthy that the exhaust pipe assembly 5 is at least passed through the expansion chamber 3 without interruption. In the examples shown, the exhaust pipe assembly 5 is passed through the entire housing 2 without interruption. This means, in particular, that the exhaust pipe arrangement 5 ensures a more or less effective flow guidance at each point between its ends 10, 11. The exhaust pipe assembly 5 is passed through the expansion chamber 3 and has within the expansion chamber 3, a perforation 12, which is in particular formed by a plurality of holes 13 which break a flow-leading wall of the exhaust pipe assembly 5. The perforation 12 thus creates a sound-transmitting connection between an interior 14 of the exhaust pipe assembly 5 and the expansion chamber 3. It is noteworthy that such a perforation 12 affects the flow through the exhaust pipe assembly 5 only comparatively slightly. In particular, owing to the perforation 12, only a comparatively small increase in pressure results. Furthermore, even at comparatively high mass flows, the perforation 12 does not lead to any significant additional noise formation within the muffler 1. During operation, the sound to be damped by the Helmholtz resonator 9 can enter the expansion chamber 3 and activate the Helmholtz resonator 9 coupled therewith via the connecting tube 6. As a result, in particular low-frequency noise of a certain interference frequency or a particular interference frequency band can effectively dampen.

Zusätzlich kann die Absorptionskammer 7 eine gewisse Dämpfungswirkung, insbesondere für hochfrequente Störgeräusche, bewirken. Die Absorptionskammer 7 kann dabei vorzugsweise über eine weitere Perforation 15, die hier nicht erkennbar ist, schallübertragend mit der Expansionskammer 3 gekoppelt sein. Diese Perforation 15 kann z.B. in einer Zwischenwand 16 vorgesehen sein, welche die Expansionskammer 3 von der Absorptionskammer 7 trennt. Grundsätzlich ist es ebenso möglich, die Absorptionskammer 7 schallübertragend mit der Resonatorkammer 4 oder mit der Abgasleitungsanordnung 5 oder mit dem Verbindungsrohr 6 zu koppeln, beispielsweise durch eine entsprechende Perforation, die z.B. in eine die Absorptionskammer 7 von der Resonatorkammer 4 trennende Zwischenwand 17 oder in einem innerhalb der Absorptionskammer 7 verlaufenden Abschnitt des Verbindungsrohrs 6 oder in einem innerhalb der Absorptionskammer 7 verlaufenden Abschnitt der Abgasleitungsanordnung 5 ausgebildet sein kann.In addition, the absorption chamber 7 can bring about a certain damping effect, in particular for high-frequency noise. The absorption chamber 7 can preferably be coupled to the expansion chamber 3 via a further perforation 15, which is not visible here, in a sound-transmitting manner. This perforation 15 may e.g. be provided in an intermediate wall 16 which separates the expansion chamber 3 from the absorption chamber 7. In principle, it is also possible to transmit the absorption chamber 7 sound-transmitting with the resonator chamber 4 or with the exhaust pipe arrangement 5 or with the connecting pipe 6, for example by means of a corresponding perforation, e.g. in an absorption chamber 7 of the resonator 4 separating partition 17 or in a running within the absorption chamber 7 portion of the connecting pipe 6 or in a running within the absorption chamber 7 portion of the exhaust pipe assembly 5 may be formed.

Bei den hier gezeigten Ausführungsformen ist die Abgasleitungsanordnung 5 durch die Resonatorkammer 4 hindurchgeführt. Ebenso ist die Abgasleitungsanordnung 5 bei diesen Ausführungsformen durch die Absorptionskammer 7 hindurchgeführt. Ferner sind die Expansionskammer 3 und die Resonatorkammer 4 sowie hier die Absorptionskammer 7 bezüglich einer Längsrichtung der Abgasleitungsanordnung 5 axial hintereinander angeordnet, wobei die Absorptionskammer 7 - soweit vorhanden - axial zwischen der Expansionskammer 3 und der Resonatorkammer 4 angeordnet ist.In the embodiments shown here, the exhaust pipe arrangement 5 is passed through the resonator chamber 4. Likewise, the exhaust pipe assembly 5 is passed through the absorption chamber 7 in these embodiments. Further, the expansion chamber 3 and the resonator 4 and here the absorption chamber 7 are arranged axially one behind the other with respect to a longitudinal direction of the exhaust pipe assembly 5, wherein the absorption chamber 7 - if present - is arranged axially between the expansion chamber 3 and the resonator 4.

Die in Fig. 1 gezeigte Ausführungsform charakterisiert sich dadurch, dass die Abgasleitungsanordnung 5 hier aus einem einzigen Abgasrohr 18 besteht. Dieses Abgasrohr 18 ist, insbesondere geradlinig, durch das Gehäuse 2 hindurchgeführt und weist in einem durch die Expansionskammer 3 hindurchgeführten Abschnitt die Perforation 12 auf. Diese Bauform eignet sich für einflutige Abgasanlagen beziehungsweise für einflutige Abschnitte von Abgasanlagen.In the Fig. 1 embodiment shown here is characterized in that the exhaust pipe assembly 5 consists of a single exhaust pipe 18 here. This exhaust pipe 18 is, in particular rectilinear, passed through the housing 2 and has the perforation 12 in a section passed through the expansion chamber 3. This design is suitable for single-flow exhaust systems or for single-flow sections of exhaust systems.

Die in Fig. 2 gezeigte Ausführungsform ist für eine mehrflutige Abgasanlage bzw. für einen mehrflutigen Abschnitt einer Abgasanlage vorgesehen und charakterisiert sich dadurch, dass die Abgasleitungsanordnung 5 mehrere parallel durchströmbare Abgasrohre 18, 19 aufweist. Im gezeigten Beispiel sind nur zwei derartige Abgasrohre 18, 19 gezeigt. Ebenso sind drei und mehr Abgasrohre 18, 19 denkbar. Die beiden Abgasrohre 18, 19 sind jeweils durch das Gehäuse 2 hindurchgeführt. Zumindest eines der beiden Abgasrohre 18, 19 ist auch durch die Expansionskammer 3 hindurchgeführt und weist innerhalb der Expansionskammer 3 einen mit der Perforation 12 versehenen Abschnitt auf. Im gezeigten Ausführungsbeispiel sind beide Abgasrohre 18, 19 durch die Expansionskammer 3 hindurchgeführt und jeweils in einem durch die Expansionskammer 3 hindurchgeführten Abschnitt mit einer solchen Perforation 12 beziehungsweise 12' versehen. Die Ausführungsform gemäß Fig. 2 zeigt eine optionale Besonderheit, bei der die Perforationen 12, 12' der beiden Abgasrohre 18, 19 unterschiedlich ausgestaltet sind. Die beiden Perforationen 12, 12' sind dabei hinsichtlich der schallkoppelnden Wirkung unterschiedlich ausgestaltet. Beispielsweise ist die Anzahl an Löchern 13 bei dem einen Abgasrohr 18 kleiner als die Anzahl an Löchern 13' des anderen Abgasrohrs 19. Des weiteren können sich die Perforationen 12, 12' hinsichtlich der Lochquerschnitte, insbesondere hinsichtlich der Lochdurchmesser, voneinander unterscheiden. Beispielsweise sind die Löcher 13 der einen Abgasleitung 18 hier mit einem größeren Lochquerschnitt oder Lochdurchmesser versehen als die Löcher 13' der anderen Abgasleitung 19.In the Fig. 2 embodiment shown is provided for a mehrflutige exhaust system or for a mehrflutigen section of an exhaust system and is characterized in that the exhaust pipe assembly 5 has a plurality of parallel durchströmbare exhaust pipes 18, 19. In the example shown, only two such exhaust pipes 18, 19 are shown. Likewise, three and more exhaust pipes 18, 19 are conceivable. The two exhaust pipes 18, 19 are each passed through the housing 2. At least one of the two exhaust pipes 18, 19 is also passed through the expansion chamber 3 and has within the expansion chamber 3 a provided with the perforation 12 section. In the embodiment shown, both exhaust pipes 18, 19 are passed through the expansion chamber 3 and each provided in a guided through the expansion chamber 3 section with such a perforation 12 or 12 '. The embodiment according to Fig. 2 shows an optional feature in which the perforations 12, 12 'of the two exhaust pipes 18, 19 are designed differently. The two perforations 12, 12 'are configured differently with respect to the sound-coupling effect. For example, the number of holes 13 in the one exhaust pipe 18 is smaller than the number of holes 13 'of the other exhaust pipe 19. Furthermore, the perforations 12, 12' with respect to the hole cross sections, in particular with respect to the hole diameter, from each other. For example, the holes 13 of an exhaust pipe 18 are here provided with a larger hole cross-section or hole diameter than the holes 13 'of the other exhaust pipe 19th

Bei den Ausführungsformen der Fig. 3 und 4 weist die Abgasleitungsanordnung 5 jeweils ein Kopplungsstück 20 auf, das zumindest zwei Einzelleitungen 21, mit einer gemeinsamen Sammelleitung 22 verbindet. Dabei kann das Kopplungsstück 20 eine Abzweigstelle bilden, bei der zumindest eine der beiden Einzelleitungen 21 von der Sammelleitung 22 abzweigt. Ebenso kann das Kopplungsstück 20 eine Vereinigungsstelle bilden, bei der sich zumindest eine der Einzelleitungen 21 mit der Sammelleitung 22 vereinigt. Je nach Strömungsrichtung kann die Sammelleitung 22 ein Einlassrohr bilden, während die beiden Einzelrohre 21 jeweils ein Auslassrohr bilden. Bei umgekehrter Strömungsrichtung bilden die beiden Einzelleitungen 21 jeweils ein Einlassrohr, während das Sammelleitung 22 ein gemeinsames Auslassrohr bildet.In the embodiments of the 3 and 4 the exhaust pipe assembly 5 each have a coupling piece 20 which connects at least two individual lines 21, with a common bus 22. In this case, the coupling piece 20 form a branch point, in which at least one of the two individual lines 21 branches off from the manifold 22. Likewise, the coupling piece 20 may form a junction, in which at least one of the individual lines 21 merges with the manifold 22. Depending on the direction of flow, the manifold 22 may form an inlet tube, while the two individual tubes 21 each form an outlet tube. In the reverse flow direction, the two individual lines 21 each form an inlet pipe, while the manifold 22 forms a common outlet pipe.

Bei der in Fig. 3 gezeigten Ausführungsform erstrecken sich die Einzelleitungen 21 durch die Resonatorkammer 4 hindurch und erstrecken sich bis in die Expansionskammer 3 hinein, also gegebenenfalls auch durch die Absorptionskammer 7 hindurch. Im Unterschied dazu ragt die Sammelleitung 22 nur in die Expansionskammer 3 hinein. Bei der in Fig. 4 gezeigten Ausführungsform ist die Anordnung der Leitungen so gewählt, dass sich die Sammelleitung 22 durch die Resonatorkammer 4 hindurch erstreckt und sich bis in die Expansionskammer 3 hinein erstreckt, wobei sich die Sammelleitung 22 außerdem durch die Absorptionskammer 7 hindurch erstrecken kann. Im Unterschied dazu erstrecken sich die beiden Einzelleitungen 21 nur bis in die Expansionskammer 3 hinein.At the in Fig. 3 In the embodiment shown, the individual lines 21 extend through the resonator chamber 4 and extend into the expansion chamber 3, so if necessary, through the absorption chamber 7 therethrough. In contrast, the manifold 22 only projects into the expansion chamber 3. At the in Fig. 4 In the embodiment shown, the arrangement of the lines is chosen such that the collecting line 22 extends through the resonator chamber 4 and extends into the expansion chamber 3, wherein the collecting line 22 can also extend through the absorption chamber 7. In contrast, the two individual lines 21 only extend into the expansion chamber 3.

Bei beiden Ausführungsformen ist das Kopplungsstück 20 jeweils innerhalb der Expansionskammer 3 angeordnet. Außerdem ist bevorzugt das Kopplungsstück 20 mit der Perforation 12 ausgestattet. Zur Realisierung einer besonders preiswerten Bauweise kann das Kopplungsstück 20 in Schalenbauweise hergestellt sein und somit insbesondere aus zwei Halbschalen zusammengebaut sein. Zumindest eine dieser Schalen kann dann mit der Perforation 12 versehen sein.In both embodiments, the coupling piece 20 is disposed respectively within the expansion chamber 3. In addition, the coupling piece 20 is preferably equipped with the perforation 12. To realize a particularly inexpensive construction, the coupling piece 20 may be manufactured in shell construction and thus in particular be assembled from two half-shells. At least one of these shells can then be provided with the perforation 12.

Die Zwischenwände 16 und 17 dienen zur Trennung der einzelnen Kammern 3, 4, 7 voneinander und bilden gleichzeitig eine Aussteifung des Gehäuses 2. Ferner dienen die Zwischenwände 16, 17 zur Halterung der Rohre des Schalldämpfers 1, also des Verbindungsrohrs 6 sowie der Rohre oder Leitungen 18, 19, 21, 22 der Abgasleitungsanordnung 5.The intermediate walls 16 and 17 are used to separate the individual chambers 3, 4, 7 from each other and at the same time form a stiffening of the housing 2. Further, the intermediate walls 16, 17 are used to hold the pipes of the muffler 1, so the connecting pipe 6 and the pipes or lines 18, 19, 21, 22 of the exhaust pipe arrangement 5.

Bei den hier gezeigten Ausführungsbeispielen weist der jeweilige Schalldämpfer 1 jeweils nur einen einzigen Helmholtzresonator 9 auf. Bei anderen Ausführungsformen können auch zwei oder mehr Helmholtzresonatoren 9 vorgesehen sein, die parallel und/oder in Reihe wirksam geschaltet und insbesondere hinsichtlich unterschiedlicher Frequenzen abgestimmt sein können.In the embodiments shown here, the respective muffler 1 each only a single Helmholtz resonator 9 on. In other embodiments, it is also possible to provide two or more Helmholtz resonators 9, which can be switched in parallel and / or in series effectively and, in particular, tuned to different frequencies.

Claims (5)

  1. A silencer for an exhaust system of a combustion engine, more preferably in a motor vehicle,
    - with a housing (2),
    - with an exhaust line arrangement (5) passed through the housing (2),
    - with an expansion chamber (3) formed in the housing (2),
    - with at least one resonator chamber (4) of a Helmholtz resonator (9) formed in the housing (2), whose respective neck is formed by at least one respective connecting pipe (6) arranged in the housing (2),
    - wherein the exhaust line arrangement (5) is passed through the expansion chamber (3) without interruption and within the expansion chamber (3) comprises a perforation (12),
    - wherein the respective connecting pipe (6) connects the expansion chamber (3) with the resonator chamber (4) in a communicating manner,
    characterized in that
    the exhaust line arrangement (5) comprises an inlet pipe (22) and at least two outlet pipes (21) or an outlet pipe (22) and at least two inlet pipes (21) which are coupled to one another via at least one coupling piece (20) within the expansion chamber (3) comprising the perforation (12).
  2. The silencer according to Claim 1,
    characterized in that
    the exhaust line arrangement (5) is passed through the resonator chamber (4).
  3. The silencer according to Claim 1 or 2,
    Characterized in that
    - in the housing (2) an absorption chamber (7) is arranged,
    - the connecting pipe (6) is passed through the absorption chamber (7) and within the absorption chamber (7) comprises a perforation or
    - the exhaust line arrangement (5) is passed through the absorption chamber (7) and within the absorption chamber (7) comprises a perforation or
    - in that the exhaust line arrangement (5) is passed through the absorption chamber (7) and within the absorption chamber (7) comprises a perforation or in that a separating wall (16) separating the absorption chamber (7) from the expansion chamber (3) comprises a perforation (15) or
    - in that a separating wall (17) separating the absorption chamber (7) from the resonator chamber (4) comprises a perforation.
  4. The silencer according to Claim 3,
    characterized in that
    the exhaust line arrangement (5) is passed through the absorption chamber (7).
  5. The silencer according to any one of the Claims 1 to 4,
    characterized in that
    the expansion chamber (3) and the resonator chamber (4) or in that the expansion chamber (3) the absorption chamber (7) and the resonator chamber (4) with respect to a longitudinal direction of the exhaust line arrangement (5) are arranged axially behind one another.
EP08150938.2A 2007-02-13 2008-02-01 Silencer for an exhaust system Active EP1959106B2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007007600A DE102007007600A1 (en) 2007-02-13 2007-02-13 Silencer for exhaust system of internal-combustion engine in motor vehicle, has exhaust pipe arrangement conducted through expansion chamber in interruptible manner and exhibiting perforation within expansion chamber

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EP1959106A1 EP1959106A1 (en) 2008-08-20
EP1959106B1 true EP1959106B1 (en) 2010-12-08
EP1959106B2 EP1959106B2 (en) 2016-01-06

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DE102009049462A1 (en) * 2009-10-15 2011-05-05 J. Eberspächer GmbH & Co. KG Exhaust system and Y-distributor
RU2504667C1 (en) * 2012-07-05 2014-01-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования Поволжский государственный технологический университет Silencer
CN102966411A (en) * 2012-11-18 2013-03-13 无锡明珠增压器制造有限公司 Improved muffler structure
DE102014114254A1 (en) * 2014-09-30 2016-03-31 Eberspächer Exhaust Technology GmbH & Co. KG Passive silencer with Helmholtz resonator for multi-flow exhaust systems
CN107882712B (en) * 2017-09-06 2023-12-26 西安交通大学 But quick switch outer cannula formula Rong Guanrong pulsation attenuator
DE102018112963A1 (en) * 2018-05-30 2019-12-05 Faurecia Emissions Control Technologies, Germany Gmbh Silencer for an exhaust system of an internal combustion engine
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ATE491081T1 (en) 2010-12-15
DE502008001973D1 (en) 2011-01-20
EP1959106B2 (en) 2016-01-06
EP1959106A1 (en) 2008-08-20
DE102007007600A1 (en) 2008-08-14

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