EP2476871A2 - Exhaust assembly for use with a combustion engine - Google Patents
Exhaust assembly for use with a combustion engine Download PDFInfo
- Publication number
- EP2476871A2 EP2476871A2 EP11196003A EP11196003A EP2476871A2 EP 2476871 A2 EP2476871 A2 EP 2476871A2 EP 11196003 A EP11196003 A EP 11196003A EP 11196003 A EP11196003 A EP 11196003A EP 2476871 A2 EP2476871 A2 EP 2476871A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- combustion gas
- flow path
- gas flow
- exhaust assembly
- sound
- 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.)
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Classifications
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- 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
- F01N1/10—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling in combination with sound-absorbing materials
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- 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
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- 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
- F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
- F01N1/168—Silencing apparatus characterised by method of silencing by using movable parts for controlling or modifying silencing characteristics only
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- 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
- F01N1/24—Silencing apparatus characterised by method of silencing by using sound-absorbing materials
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- 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
- F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
- F01N1/166—Silencing apparatus characterised by method of silencing by using movable parts for changing gas flow path through the silencer or for adjusting the dimensions of a chamber or a pipe
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- 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
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/36—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being an exhaust flap
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- 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
- F01N2470/00—Structure or shape of gas passages, pipes or tubes
- F01N2470/02—Tubes being perforated
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- 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
- F01N2590/00—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines
- F01N2590/04—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines for motorcycles
Definitions
- the invention relates to an exhaust assembly for use with an internal combustion engine according to the preamble of claim 1.
- Such an exhaust assembly is known from DE 697 02 447 T2 known.
- the exhaust arrangement is characterized in that the two combustion gas flow paths have a different damping characteristic.
- the first combustion gas flow path is characterized by a damping device with which the combustion gases emitted by the exhaust system can be silenced.
- the second combustion gas flow path is characterized by the fact that no damping device or only one attenuated damping device is provided, so that the outflowing along the second combustion gas flow path Combustion gases are not silenced or attenuated.
- the user thus has the option of optionally changing over the damping characteristic of the exhaust system. If the combustion gases are passed over the first combustion gas flow path, the combustion gases are silenced and the noise is reduced accordingly. On the other hand, when the combustion gases are conducted via the second combustion gas flow path, the combustion gases flow unattenuated at a correspondingly higher power of the internal combustion engine and cause a higher noise level.
- Object of the present invention is therefore to propose a new exhaust assembly for use with an internal combustion engine, the damping characteristic can be changed by a control device and thereby has an improved noise characteristics.
- the exhaust arrangement according to the invention is based on the basic idea that the damping devices of the first combustion gas flow path comprise a high-frequency damper, with the high-frequency damper predominantly higher frequencies of the frequency spectrum contained in the combustion gas can be attenuated.
- the term high-frequency damper is thus to be understood that the high-frequency damper is suitable for damping the relatively higher frequencies of the frequency spectrum contained in the combustion gas. It is therefore not the attenuation of high-frequency oscillations of the electromagnetic wave spectrum.
- the high-frequency damper has no significant influence on the desired lower frequencies of the frequency spectrum contained in the combustion gas.
- the high-frequency damper of the exhaust assembly according to the invention is designed constructively, is basically arbitrary.
- the design of the high-frequency damper in the manner of a closed sound-collecting chamber, which communicates with the first combustion gas flow path via sound passage openings is preferred.
- the sound passage openings are not part of the first combustion gas flow path and are not substantially traversed by the combustion gas. Rather, only the sound waves pass through the sound passage openings and are selectively damped in the closed sound chamber so that predominantly higher frequencies are removed or reduced.
- the closed sound chamber has only a very small or no influence.
- the sound-absorbing chamber can be filled with a damping material, for example with insulating wool.
- a particularly easy and inexpensive to manufacture embodiment of the exhaust assembly according to the invention is obtained when the exhaust assembly has a gas-tight housing and a perforated inner tube spaced therefrom.
- the housing is closed on one side around the inner tube and connected via connecting means with a combustion gas supply pipe.
- a valve device is then provided for completely or partially closing the inner tube.
- the combustion gas can then escape without interruption through the inner tube into the environment, so that the inner tube forms the second combustion gas flow path when the valve device is open. If the valve device is closed, the combustion gas can no longer flow out through the inner tube, but is deflected at the valve device.
- the combustion gas then flows first via the inner tube and via perforation openings formed therein into a bypass, which comprises the inner tube in a cylindrical shape and forms part of the first combustion gas flow path. From this bypass, the combustion gas can then then again flow back through perforation openings in the inner tube to emanate from there into the environment or the combustion gas flows directly from the bypass into the environment. Damping devices could optionally be installed in the bypass behind the perforation openings of the inner tube.
- the sound passage openings of the cylindrically shaped sound collecting chamber can be arranged on the inside of the housing, which in turn is the outside of the bypass for the first combustion gas flow path forms. As a result, the combustion gas then flows out through the bypass and passes through the sound passage openings of the sound collecting chamber surrounding this bypass in a cylindrical manner.
- the cylindrical sound collecting chamber is formed by a gas-tight, outer housing wall and a perforated, inner Schall be trecswandung.
- the perforation in the sound passage wall need not be completely formed, but also the partial perforation of the sound passage is already sufficient in many cases.
- a deflecting element may be provided in the first combustion gas flow path, with which the flow path of the combustion gases along the perforated, inner Schall bestoryswandung the sound chamber is extended. Through this extended flow path along the sound passage wall of the sound-trapping chamber a correspondingly higher proportion of the sound waves is passed through the Schall shedstoryswandungen and attenuated correspondingly higher.
- additional sound passage openings may also be present between the second combustion gas flow path and the sound-absorbing chamber.
- the sound collecting chamber can then combine both the first combustion gas flow path and the second combustion gas flow path contained higher frequencies of the frequency spectrum contained in the combustion gas.
- the additional sound passage openings may be disposed in the common flow path formed by the first and second combustion gas flow paths.
- this inner tube may preferably also have sound passage openings which are not part of the first combustion gas flow path and are substantially not traversed by the combustion gas.
- Fig. 1 shows a first embodiment 01 of an exhaust assembly according to the invention, which is connected via a combustion gas supply pipe 02 with an internal combustion engine, not shown.
- the exhaust assembly 01 consists essentially of an inner tube 03, a gas-tight housing 04 and a valve device 05.
- the valve device 05 By pivoting the valve device 05, the cross section of the inner tube 03 can be opened and closed operator-controlled. Is the Valve device 05 is opened, so the combustion gas flowing from the combustion gas supply pipe 02 into the exhaust arrangement can flow out into the environment without substantial damping and without interruption by the inner pipe 03.
- This undamped and uninterrupted flow path through the inner tube 03 forms the second combustion gas flow path in the sense of the present invention.
- valve device 05 If the valve device 05 is closed, as it is in Fig. 1 is exemplified, the flow path is interrupted by the inner tube 03 and the combustion gas flows through openings 06 in a cylindrical bypass channel 07. At the end of the bypass channel 07, the combustion gases then flow through openings 08 back into the inner tube 03 and from there into the environment , This corresponds to the first combustion gas flow path in the sense of the present invention and is indicated schematically by the flow arrows 09.
- the bypass channel 07 is bounded on the outside by a perforated, internal sound passage wall 10, which has a plurality of sound passage openings.
- a perforated, internal sound passage wall 10 of the bypass channel 07 of the first combustion gas flow path is connected to a cylindrical sound collecting chamber 11 which is formed between the gas-tight outer housing 04 and the perforated inner Schall bestoryswandung 10.
- the resulting in the bypass channel 07 of the first combustion gas flow path higher frequencies are strongly attenuated when passing through the sound passage openings in the Schall shedswandung 10.
- damping wool 12 is introduced to reinforce the damping effect, the in Fig. 1 is indicated by dashed lines.
- the perforation of the sound passage wall 10 continues at the transition to the inner tube 03, so that the inner tube 03 has the only schematically indicated sound passage openings 13.
- the higher frequencies of the combustion gas contained Frequency spectrum are attenuated even when the valve device 05 is open.
- Fig. 2 shows a second embodiment 14 of an exhaust assembly according to the invention, which in turn comprises a combustion gas supply pipe 02 for supplying the combustion gases from an internal combustion engine.
- the exhaust assembly 14 consists essentially of an inner tube 15, a housing wall 16 and a valve means 17.
- the valve means 17 When the valve means 17 is open, the combustion gas can flow continuously from the combustion gas supply pipe 02 through the inner tube 15 into the environment. Due to the lack of damping, this increases performance and increases noise.
- the valve device 17 is closed, the combustion gases flow through openings 18 into a bypass channel 19, the combustion gases being deflected in the opposite direction on a deflecting element 20. At the end of the bypass channel 19, the combustion gases then flow through openings 21 and 22 back into the inner tube 15 and from there into the environment.
- the bypass passage 19 is in turn encompassed by a cylindrical sound-trapping chamber 23, the inner sound passage wall 24 of which is perforated with a multiplicity of sound passage openings 25 only indicated.
- the sound waves passing through the sound passage openings 25 from the bypass channel 19 into the sound-trapping chamber 23 are strongly damped with respect to the higher frequencies contained in the frequency spectrum and thus the desired damping effect is made possible.
- the deflection element 20 the flow path of the combustion gases along the Schall shedswandung 24 is greatly extended with the sound passage openings 25 and thus increases the damping effect accordingly.
- the insulating wool 26 in the sound trap chamber 23 is in Fig. 2 again indicated by dashed lines.
- the front part of the inner tube 15 may also be perforated with sound passage openings 25 in front of the openings 18 in order to allow the passage of sound waves when the valve device 17 is open.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
Abstract
Description
Die Erfindung betrifft eine Auspuffanordnung zur Verwendung mit einem Verbrennungsmotor nach dem Oberbegriff des Anspruchs 1. Eine solche Auspuffanordnung ist aus der
Bei der bekannten Auspuffanordnung sind zwei getrennte Verbrennungsgasströmungswege ansteuerbar, um die Dämpfungscharakteristik der Auspuffanordnung zu verändern. Als Steueranordnung kommt dabei insbesondere ein drehbar gelagertes Ventil zum Einsatz, mit dem die Verbrennungsgasströmungswege selektiv versperrt beziehungsweise geöffnet werden können, um die Gasverteilung in den beiden Verbrennungsgasströmungswegen zu ändern. Die Auspuffanordnung ist dabei dadurch gekennzeichnet, dass die beiden Verbrennungsgasströmungswege eine unterschiedliche Dämpfungscharakteristik aufweisen. Der erste Verbrennungsgasströmungsweg ist dabei durch eine Dämpfungseinrichtung charakterisiert, mit der die von der Auspuffanordnung abgegebenen Verbrennungsgase schallgedämpft werden können. Der zweite Verbrennungsgasströmungsweg zeichnet sich dagegen dadurch aus, dass keine oder lediglich eine abgeschwächte Dämpfungseinrichtung vorgesehen ist, so dass die entlang des zweiten Verbrennungsgasströmungsweges ausströmenden Verbrennungsgase nicht oder abgeschwächt schallgedämpft werden.In the known exhaust arrangement two separate combustion gas flow paths are controllable to change the damping characteristic of the exhaust assembly. As a control arrangement, in particular a rotatably mounted valve is used, with which the combustion gas flow paths can be selectively blocked or opened in order to change the gas distribution in the two combustion gas flow paths. The exhaust arrangement is characterized in that the two combustion gas flow paths have a different damping characteristic. The first combustion gas flow path is characterized by a damping device with which the combustion gases emitted by the exhaust system can be silenced. On the other hand, the second combustion gas flow path is characterized by the fact that no damping device or only one attenuated damping device is provided, so that the outflowing along the second combustion gas flow path Combustion gases are not silenced or attenuated.
Im Ergebnis hat der Benutzer durch Ansteuerung der Steuereinrichtung also die Möglichkeit, die Dämpfungscharakteristik der Auspuffanordnung wahlweise umzustellen. Werden die Verbrennungsgase über den ersten Verbrennungsgasströmungsweg geleitet, so werden die Verbrennungsgase schallgedämpft und die Geräuschentwicklung entsprechend gemindert. Werden die Verbrennungsgase dagegen über den zweiten Verbrennungsgasströmungsweg geleitet, so strömen die Verbrennungsgase bei entsprechend höherer Leistung des Verbrennungsmotors ungedämpft aus und verursachen ein höheres Geräuschniveau.As a result, by actuating the control device, the user thus has the option of optionally changing over the damping characteristic of the exhaust system. If the combustion gases are passed over the first combustion gas flow path, the combustion gases are silenced and the noise is reduced accordingly. On the other hand, when the combustion gases are conducted via the second combustion gas flow path, the combustion gases flow unattenuated at a correspondingly higher power of the internal combustion engine and cause a higher noise level.
Diese bekannten Auspuffanordnungen kommen insbesondere bei großvolumigen Verbrennungsmotoren von Motorrädern zum Einsatz. Die Benutzer derartiger Motorräder wünschen sich dabei bevorzugt eine möglichst tieffrequente Geräuschcharakteristik, die an ein Blubbergeräusch erinnert. Untersuchungen haben nun gezeigt, dass durch die in gattungsgemäßen Auspuffanordnungen erforderliche Steuerungseinrichtung, die vielfach in der Art einer Ventilklappe ausgebildet ist, unerwünschte, nämlich relativ hohe Geräuschfrequenzen erzeugt werden, wohingegen die erwünschten tiefen Frequenzanteile durch die Dämpfungseinrichtung im ersten Verbrennungsgasströmungsweg ausgefiltert werden. Im Ergebnis weisen die bekannten Auspuffanordnungen der Steuerungseinrichtung zur Änderung der Dämpfungscharakteristik deshalb eine Geräuschcharakteristik auf, die hinsichtlich der Frequenzverteilung vielfach kritisiert wird.These known exhaust arrangements are used in particular in large-volume combustion engines of motorcycles. The users of such motorcycles preferably want a low-frequency as possible noise characteristic that is reminiscent of a Blubberger sound. Investigations have now shown that undesirable, namely relatively high noise frequencies are generated by the required in generic exhaust arrangements, which is often designed in the manner of a valve flap, whereas the desired low frequency components are filtered out by the damping device in the first combustion gas flow path. As a result, the known exhaust arrangements of the control device for changing the damping characteristic therefore have a noise characteristic which is often criticized with regard to the frequency distribution.
Aufgabe der vorliegenden Erfindung ist es deshalb, eine neue Auspuffanordnung zur Verwendung mit einem Verbrennungsmotor vorzuschlagen, deren Dämpfungscharakteristik durch eine Steuerungseinrichtung geändert werden kann und dabei eine verbesserte Geräuschcharakteristik aufweist.Object of the present invention is therefore to propose a new exhaust assembly for use with an internal combustion engine, the damping characteristic can be changed by a control device and thereby has an improved noise characteristics.
Diese Aufgabe wird durch eine Auspuffanordnung nach der Lehre des Anspruchs 1 gelöst.This object is achieved by an exhaust arrangement according to the teaching of claim 1.
Vorteilhafte Ausführungsformen der Erfindung sind Gegenstand der Unteransprüche.Advantageous embodiments of the invention are the subject of the dependent claims.
Die erfindungsgemäße Auspuffanordnung beruht auf dem Grundgedanken, dass die Dämpfungseinrichtungen des ersten Verbrennungsgasströmungsweges einen Hochfrequenzdämpfer umfassen, wobei mit dem Hochfrequenzdämpfer überwiegend höhere Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums gedämpft werden können. Der Begriff Hochfrequenzdämpfer ist dabei also so zu verstehen, dass der Hochfrequenzdämpfer zur Dämpfung der relativ höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums geeignet ist. Es handelt sich also nicht um die Dämpfung von hochfrequenten Schwingungen des elektromagnetischen Wellenspektrums. Durch die Dämpfung dieser höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums wird die Geräuschcharakteristik der Auspuffanordnung entscheidend verbessert, da die unerwünschten höherfrequenten Frequenzen entfernt beziehungsweise verringert werden. Auf die erwünschten tieferen Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums hat der Hochfrequenzdämpfer dagegen keinen wesentlichen Einfluss. Wie der Hochfrequenzdämpfer der erfindungsgemäßen Auspuffanordnung konstruktiv ausgebildet ist, ist grundsätzlich beliebig. Bevorzugt ist dabei jedoch die Ausbildung des Hochfrequenzdämpfers in der Art einer geschlossenen Schallfangkammer, die mit dem ersten Verbrennungsgasströmungsweg über Schalldurchtrittsöffnungen in Verbindung steht. Die Schalldurchtrittsöffnungen sind dabei nicht Teil des ersten Verbrennungsgasströmungsweges und werden im Wesentlichen nicht vom Verbrennungsgas durchströmt. Vielmehr treten durch die Schalldurchtrittsöffnungen lediglich die Schallwellen hindurch und werden in der geschlossenen Schallfangkammer selektiv dahingehend gedämpft, dass überwiegend höhere Frequenzen entfernt oder vermindert werden. Auf die erwünschten tiefer liegenden Frequenzen hat die geschlossene Schallfangkammer dagegen nur einen sehr geringen beziehungsweise keinen Einfluss.The exhaust arrangement according to the invention is based on the basic idea that the damping devices of the first combustion gas flow path comprise a high-frequency damper, with the high-frequency damper predominantly higher frequencies of the frequency spectrum contained in the combustion gas can be attenuated. The term high-frequency damper is thus to be understood that the high-frequency damper is suitable for damping the relatively higher frequencies of the frequency spectrum contained in the combustion gas. It is therefore not the attenuation of high-frequency oscillations of the electromagnetic wave spectrum. By damping these higher frequencies of the frequency spectrum contained in the combustion gas, the noise characteristics of the exhaust system is significantly improved because the unwanted higher-frequency frequencies are removed or reduced. On the other hand, the high-frequency damper has no significant influence on the desired lower frequencies of the frequency spectrum contained in the combustion gas. As the high-frequency damper of the exhaust assembly according to the invention is designed constructively, is basically arbitrary. However, the design of the high-frequency damper in the manner of a closed sound-collecting chamber, which communicates with the first combustion gas flow path via sound passage openings, is preferred. The sound passage openings are not part of the first combustion gas flow path and are not substantially traversed by the combustion gas. Rather, only the sound waves pass through the sound passage openings and are selectively damped in the closed sound chamber so that predominantly higher frequencies are removed or reduced. On the desired low-lying frequencies, however, the closed sound chamber has only a very small or no influence.
Um den erwünschten Dämpfungseffekt zur Dämpfung der höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums zu verstärken, kann die Schallfangkammer mit einem Dämpfungsmaterial, beispielsweise mit Dämmwolle, ausgefüllt werden.In order to enhance the desired damping effect for damping the higher frequencies of the frequency spectrum contained in the combustion gas, the sound-absorbing chamber can be filled with a damping material, for example with insulating wool.
Eine besonders einfach und kostengünstig herzustellende Ausführungsform der erfindungsgemäßen Auspuffanordnung ergibt sich, wenn die Auspuffanordnung ein gasdichtes Gehäuse und ein davon beabstandetes perforiertes Innenrohr aufweist. Das Gehäuse ist dabei auf einer Seite um das Innenrohr geschlossen und über Verbindungseinrichtungen mit einem Verbrennungsgaszuleitungsrohr verbunden. Im Abstand von den Verbindungseinrichtungen ist dann eine Ventileinrichtung zum vollständig oder teilweise schließenden Innenrohr vorgesehen. Bei offener Ventileinrichtung kann das Verbrennungsgas dann ohne Unterbrechung durch das Innenrohr in die Umwelt austreten, so dass das Innenrohr bei geöffneter Ventileinrichtung den zweiten Verbrennungsgasströmungsweg bildet. Wird die Ventileinrichtung geschlossen, so kann das Verbrennungsgas nicht mehr durch das Innenrohr ausströmen, sondern wird an der Ventileinrichtung umgelenkt. Im Ergebnis strömt das Verbrennungsgas dann zunächst über das Innenrohr und über darin ausgebildete Perforationsöffnungen in einen Bypass, der das Innenrohr zylinderförmig umfasst und Teil des ersten Verbrennungsgasströmungsweges ist. Aus diesem Bypass kann das Verbrennungsgas dann anschließend wieder durch Perforationsöffnungen zurück in das Innenrohr strömen, um von dort aus in die Umwelt auszuströmen oder das Verbrennungsgas strömt direkt aus dem Bypass in die Umwelt. In den hinter den Perforationsöffnungen des Innenrohrs liegenden Bypass könnten wahlweise Dämpfungseinrichtungen eingebaut werden. Auf der Innenseite des Gehäuses, die ihrerseits die Außenseite des Bypasses für den ersten Verbrennungsgasströmungsweg bildet, können die Schalldurchtrittsöffnungen der zylindrisch ausgebildeten Schallfangkammer angeordnet werden. Im Ergebnis strömt dann das Verbrennungsgas durch den Bypass aus und passiert dabei die Schalldurchtrittsöffnungen der diesen Bypass zylindrisch umgebenden Schallfangkammer.A particularly easy and inexpensive to manufacture embodiment of the exhaust assembly according to the invention is obtained when the exhaust assembly has a gas-tight housing and a perforated inner tube spaced therefrom. The housing is closed on one side around the inner tube and connected via connecting means with a combustion gas supply pipe. At a distance from the connecting devices, a valve device is then provided for completely or partially closing the inner tube. When the valve device is open, the combustion gas can then escape without interruption through the inner tube into the environment, so that the inner tube forms the second combustion gas flow path when the valve device is open. If the valve device is closed, the combustion gas can no longer flow out through the inner tube, but is deflected at the valve device. As a result, the combustion gas then flows first via the inner tube and via perforation openings formed therein into a bypass, which comprises the inner tube in a cylindrical shape and forms part of the first combustion gas flow path. From this bypass, the combustion gas can then then again flow back through perforation openings in the inner tube to emanate from there into the environment or the combustion gas flows directly from the bypass into the environment. Damping devices could optionally be installed in the bypass behind the perforation openings of the inner tube. On the inside of the housing, which in turn is the outside of the bypass for the first combustion gas flow path forms, the sound passage openings of the cylindrically shaped sound collecting chamber can be arranged. As a result, the combustion gas then flows out through the bypass and passes through the sound passage openings of the sound collecting chamber surrounding this bypass in a cylindrical manner.
Bei der Auspuffanordnung mit Innenrohr und Ventileinrichtung ist es besonders vorteilhaft, wenn die zylindrische Schallfangkammer von einer gasdichten, äußeren Gehäusewandung und einer perforierten, inneren Schalldurchtrittswandung gebildet wird. Die Perforation in der Schalldurchtrittswandung muss dabei nicht vollständig ausgebildet sein, sondern auch die teilweise Perforierung der Schalldurchtrittswandung ist vielfach bereits ausreichend.In the exhaust arrangement with inner tube and valve device, it is particularly advantageous if the cylindrical sound collecting chamber is formed by a gas-tight, outer housing wall and a perforated, inner Schalldurchtrittswandung. The perforation in the sound passage wall need not be completely formed, but also the partial perforation of the sound passage is already sufficient in many cases.
Um den erwünschten Dämpfungseffekt zur Dämpfung der höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums zu verstärken, kann gemäß einer bevorzugten Ausführungsvariante im ersten Verbrennungsgasströmungsweg ein Umlenkelement vorgesehen sein, mit dem der Strömungsweg der Verbrennungsgase entlang der perforierten, inneren Schalldurchtrittswandung der Schallfangkammer verlängert wird. Durch diesen verlängerten Strömungsweg entlang der Schalldurchtrittswandung der Schallfangkammer wird ein entsprechend höherer Anteil der Schallwellen durch die Schalldurchtrittswandungen durchgeleitet und entsprechend höher gedämpft.In order to enhance the desired damping effect for damping the higher frequencies of the frequency spectrum contained in the combustion gas, according to a preferred embodiment, a deflecting element may be provided in the first combustion gas flow path, with which the flow path of the combustion gases along the perforated, inner Schalldurchtrittswandung the sound chamber is extended. Through this extended flow path along the sound passage wall of the sound-trapping chamber a correspondingly higher proportion of the sound waves is passed through the Schalldurchtrittswandungen and attenuated correspondingly higher.
Um die unerwünschten höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums auch dann entfernen beziehungsweise verringern zu können, wenn diese Frequenzen beim Ausströmen entlang des zweiten Verbrennungsgasströmungsweges entstehen, können auch zwischen dem zweiten Verbrennungsgasströmungsweg und der Schallfangkammer zusätzliche Schalldurchtrittsöffnungen vorhanden sein. Im Ergebnis kann dann die Schallfangkammer kombiniert sowohl die im ersten Verbrennungsgasströmungsweg als auch im zweiten Verbrennungsgasströmungsweg enthaltenen höheren Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums dämpfen.In order to be able to remove or reduce the undesired higher frequencies of the frequency spectrum contained in the combustion gas even when these frequencies arise during the outflow along the second combustion gas flow path, additional sound passage openings may also be present between the second combustion gas flow path and the sound-absorbing chamber. As a result, the sound collecting chamber can then combine both the first combustion gas flow path and the second combustion gas flow path contained higher frequencies of the frequency spectrum contained in the combustion gas.
Um die kombinierte Dämpfung der höheren Frequenzen sowohl im zweiten Verbrennungsgasströmungsweg als auch im ersten Verbrennungsgasströmungsweg zu realisieren, können die zusätzlichen Schalldurchtrittsöffnungen auch im gemeinsamen Strömungsweg angeordnet sein, der zusammen vom ersten und dem zweiten Verbrennungsgasströmungsweg gebildet wird.In order to realize the combined damping of the higher frequencies in both the second combustion gas flow path and the first combustion gas flow path, the additional sound passage openings may be disposed in the common flow path formed by the first and second combustion gas flow paths.
Wird eine Ausführungsform der Auspuffanordnung verwendet, die ein Innenrohr aufweist, so kann dieses Innenrohr bevorzugt auch Schalldurchtrittsöffnungen aufweisen, die nicht Teil des ersten Verbrennungsgasströmungsweges sind und im Wesentlichen nicht vom Verbrennungsgas durchströmt werden.If an embodiment of the exhaust arrangement is used, which has an inner tube, then this inner tube may preferably also have sound passage openings which are not part of the first combustion gas flow path and are substantially not traversed by the combustion gas.
Zwei Ausführungsformen der erfindungsgemäßen Auspuffanordnung sind in den Zeichnungen schematisiert dargestellt und werden nachfolgend beispielhaft erläutert.Two embodiments of the exhaust assembly according to the invention are shown schematically in the drawings and are explained below by way of example.
Es zeigen:
- Fig.1
- eine erste Ausführungsform einer erfindungsgemäßen Auspuffanordnung im Längsschnitt;
- Fig. 2
- eine zweite Ausführungsform einer erfindungsgemäßen Auspuffanordnung im Längsschnitt.
- Fig.1
- a first embodiment of an exhaust assembly according to the invention in longitudinal section;
- Fig. 2
- a second embodiment of an exhaust assembly according to the invention in longitudinal section.
Wird die Ventileinrichtung 05 geschlossen, wie es in
Der Bypasskanal 07 wird außenseitig von einer perforierten, inneren Schalldurchtrittswandung 10 begrenzt, die eine Vielzahl von Schalldurchtrittsöffnungen aufweist. Durch diese Schalldurchtrittsöffnungen in der Schalldurchtrittswandung 10 wird der Bypasskanal 07 des ersten Verbrennungsgasströmungsweges mit einer zylindrischen Schallfangkammer 11 verbunden, die zwischen der gasdichten, äußeren Gehäusewandung 04 und der perforierten, inneren Schalldurchtrittswandung 10 gebildet wird. Die im Bypasskanal 07 des ersten Verbrennungsgasströmungsweges entstehenden höheren Frequenzen werden beim Durchtritt durch die Schalldurchtrittsöffnungen in der Schalldurchtrittswandung 10 stark abgedämpft. In der Schallfangkammer 11 ist zur Verstärkung des Dämpfungseffektes Dämpfungswolle 12 eingebracht, die in
Claims (9)
dadurch gekennzeichnet,
dass die Dämpfungseinrichtungen des ersten Verbrennungsgasströmungsweges einen Hochfrequenzdämpfer (11, 23) umfassen, wobei mit dem Hochfrequenzdämpfer überwiegend höhere Frequenzen des im Verbrennungsgas enthaltenen Frequenzspektrums gedämpft werden können.An exhaust assembly (01, 14) for use with an internal combustion engine, the exhaust assembly (01, 14) comprising: means (02) for connecting to the internal combustion engine, at least one exhaust, and at least one muffler; wherein control means (05, 17) for controlling the damping characteristic of the exhaust assembly are provided, and wherein the exhaust assembly (01, 14) at least a first combustion gas flow path and a second combustion gas flow path, and wherein the control means (05, 17) during use with a Combustion engine connected exhaust assembly (01, 14) are selectively operable by an operator, and wherein the control means (05, 17) are able to selectively distribute an approximately constant current generated by the combustion gases of the engine regardless of the volume of the combustion gases on the combustion gas flow paths wherein the first combustion gas flow path includes at least one damper, and wherein the second combustion gas flow path has substantially no damper, so that the combustion gas flow paths have substantially different damping characteristics from each other point,
characterized,
that the damping devices of the first combustion gas flow path a radio frequency attenuator (11, 23), said mainly higher frequencies of the frequency spectrum contained in the combustion gas can be attenuated with the high frequency absorber.
dadurch gekennzeichnet,
dass der Hochfrequenzdämpfer in der Art einer geschlossenen Schallfangkammer (11, 23) ausgebildet ist, die mit dem ersten Verbrennungsgasströmungsweg über Schalldurchtrittsöffnungen (13, 25) in Verbindung steht, wobei die Schalldurchtrittsöffnungen (13, 25) nicht Teil des ersten Verbrennungsgasströmungsweges sind und im wesentlichen nicht vom Verbrennungsgas durchströmt werden.Exhaust assembly according to claim 1,
characterized,
in that the high-frequency damper is designed in the manner of a closed sound-collecting chamber (11, 23) which communicates with the first combustion gas flow path via sound passage openings (13, 25), the sound passage openings (13, 25) not being part of the first combustion gas flow path and substantially not be traversed by the combustion gas.
dadurch gekennzeichnet,
dass die Schallfangkammer (11, 23) mit einem Dämpfungsmaterial, insbesondere mit Dämmwolle (12, 26), ausgefüllt ist.Exhaust assembly according to claim 1 or 2,
characterized,
that the sound trap chamber (11, 23) is filled with a damping material, in particular with insulating wool (12, 26).
dadurch gekennzeichnet,
dass die Auspuffanordnung (01, 14) ein gasdichtes Gehäuse (04, 16) und ein davon beabstandetes perforiertes Innenrohr (03, 15) aufweist, wobei das Gehäuse (04, 16) auf einer Seite um das Innenrohr geschlossen ist, und wobei mit Abstand von den Verbindungseinrichtungen (02) eine Ventileinrichtung (05, 17) zum vollständigen oder teilweisen Schließen des Innenrohres (03, 15) vorgesehen ist, und wobei die Anordnung derart ausgebildet ist, dass bei offener Ventileinrichtung (05, 17) der zweite Verbrennnungsgasströmungsweg sich ohne Unterbrechung durch das Innenrohr (03, 15) in die Umwelt erstreckt, um einen freien Strömungsweg zu bilden, während bei geschlossener Ventileinrichtung (05, 17) der erste Verbrennungsgasströmungsweg über das Innenrohr (03, 15) und die darin ausgebildeten Perforationsöffnungen (06, 08; 18, 22) durch einen Bypasskanal (07, 19) zwischen dem Innenrohr (03, 15) und dem Gehäuse (04, 16) in die Umwelt verläuft, und wobei auf der Innenseite des Gehäuses (04, 16) die zylindrische Schallfangkammer (11, 23) angeordnet ist, die über Schalldurchtrittsöffnungen (13, 25) mit dem ersten Verbrennungsgasströmungsweg in Verbindung steht.Exhaust assembly according to one of claims 1 to 3,
characterized,
in that the exhaust assembly (01, 14) comprises a gas-tight housing (04, 16) and a perforated inner tube (03, 15) spaced therefrom, the housing (04, 16) being closed on one side around the inner tube, and at a distance from the connecting means (02) a valve means (05, 17) for complete or partial closing of the inner tube (03, 15) is provided, and wherein the arrangement is designed such that with open valve means (05, 17) of the second Verbrennnungsgasströmungsweg without Interruption through the inner tube (03, 15) extends into the environment to form a free flow path, while with closed valve means (05, 17) of the first combustion gas flow over the inner tube (03, 15) and the perforation openings formed therein (06, 08 18, 22) through a bypass channel (07, 19) between the inner tube (03, 15) and the housing (04, 16) extends into the environment, and wherein on the inside of the housing (04, 16) the cylindrical sound-collecting chamber (11, 23) is arranged, which communicates via sound passage openings (13, 25) with the first combustion gas flow path.
dadurch gekennzeichnet,
dass die zylindrische Schallfangkammer (11, 23) von einer gasdichten, äußeren Gehäusewandung (04, 16) und einer perforierten, inneren Schalldurchtrittswandung (13, 25) gebildet wird.Exhaust assembly according to one of claims 1 to 4,
characterized,
that the cylindrical sound trap chamber (11, 23) of a gas-tight outer housing wall (04, 16) and a perforated inner Schalldurchtrittswandung (13, 25) is formed.
dadurch gekennzeichnet,
dass im erste Verbrennungsgasströmungsweg ein Umlenkelement (20) vorgesehen ist, mit dem der Strömungsweg der Verbrennungsgase entlang der perforierten, inneren Schalldurchtrittswandung (24) der Schallfangkammer (23) verlängert wird.Exhaust assembly according to one of claims 1 to 5,
characterized,
in that a deflecting element (20) is provided in the first combustion gas flow path with which the flow path of the combustion gases is extended along the perforated, inner sound passage wall (24) of the sound-collecting chamber (23).
dadurch gekennzeichnet,
dass auch zwischen dem zweiten Verbrennnungsgasströmungsweg und der Schallfangkammer zusätzliche Schalldurchtrittsöffnungen vorhanden sind.Exhaust assembly according to one of claims 1 to 6,
characterized,
additional sound passage openings are present between the second Verbrennnungsgasströmungsweg and the sound trap chamber.
dadurch gekennzeichnet,
dass auch zwischen dem gemeinsamen Strömungsweg, der vom ersten und zweiten Verbrennnungsgasströmungsweg gemeinsam gebildet wird, und der Schallfangkammer (11) zusätzliche Schalldurchtrittsöffnungen (13) vorhanden sind.Exhaust assembly according to one of claims 1 to 7,
characterized,
in that additional sound passage openings (13) are also present between the common flow path, which is formed jointly by the first and second combustion gas flow paths, and the sound-collecting chamber (11).
dadurch gekennzeichnet,
dass das Innenrohr Schalldurchtrittsöffnungen aufweist, die nicht Teil des ersten Verbrennungsgasströmungsweges sind und im wesentlichen nicht vom Verbrennungsgas durchströmt werden.Exhaust assembly according to one of claims 1 to 8,
characterized,
in that the inner tube has sound passage openings which are not part of the first combustion gas flow path and are substantially not traversed by the combustion gas.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202011001554U DE202011001554U1 (en) | 2011-01-14 | 2011-01-14 | Exhaust assembly for use with an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
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EP2476871A2 true EP2476871A2 (en) | 2012-07-18 |
EP2476871A3 EP2476871A3 (en) | 2013-10-30 |
Family
ID=43878064
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP11196003.5A Withdrawn EP2476871A3 (en) | 2011-01-14 | 2011-12-29 | Exhaust assembly for use with a combustion engine |
Country Status (3)
Country | Link |
---|---|
US (1) | US20120181106A1 (en) |
EP (1) | EP2476871A3 (en) |
DE (1) | DE202011001554U1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11076951B2 (en) | 2012-09-25 | 2021-08-03 | Edwards Lifesciences Corporation | Systems for replacing a native heart valve and aorta with a prosthetic heart valve and conduit |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10443479B2 (en) | 2014-10-30 | 2019-10-15 | Roush Enterprises, Inc. | Exhaust control system |
WO2017079156A1 (en) * | 2015-11-02 | 2017-05-11 | Roush Enterprises, Inc. | Muffler with selected exhaust pathways |
Citations (1)
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DE69702447T2 (en) | 1996-04-22 | 2001-02-22 | Wilhelmus Lambertus Arnoldus Meusen | EXHAUST GAS DEVICE FOR INTERNAL COMBUSTION ENGINES AND VEHICLE WITH THIS DEVICE |
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US207384A (en) * | 1878-08-27 | Improvement in nozzles for the escape of steam or gases under pressure | ||
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US1613322A (en) * | 1921-03-21 | 1927-01-04 | Julius F Goetz | Muffler |
US1860146A (en) * | 1929-02-15 | 1932-05-24 | Emmet P Gray | Muffler |
US2625234A (en) * | 1950-05-10 | 1953-01-13 | Perry B Fina | Valve controlled muffler with a plurality of through passages |
US3097074A (en) * | 1960-11-07 | 1963-07-09 | Gen Motors Corp | Catalytic converter |
SE517825C2 (en) * | 1997-11-14 | 2002-07-23 | Volvo Car Corp | Device and method of silencing unit and use of the device in a motor vehicle |
US5979596A (en) * | 1998-07-23 | 1999-11-09 | Baker; Gary A. | Automatic compression brake muffler |
JP2000230416A (en) * | 1999-02-08 | 2000-08-22 | Honda Motor Co Ltd | Failure detecting device for exhaust changeover valve in internal combustion engine |
US6612400B2 (en) * | 2002-01-05 | 2003-09-02 | Andres E. Bravo | Electronically controlled variable loudness muffler |
US7510051B2 (en) * | 2005-05-12 | 2009-03-31 | Timothy Daniel Schrandt | Switchable loud and quiet exhaust apparatus |
DE102006044381B4 (en) * | 2005-09-23 | 2015-07-30 | Werner Müller | Exhaust device with secondary power or torque control |
US7380638B2 (en) * | 2006-04-24 | 2008-06-03 | Willey Barry A | Exhaust noise control for motorcycles |
US20080023264A1 (en) * | 2006-07-27 | 2008-01-31 | Pacini Larry W | Muffler having adjustable butterfly valve for improved sound attenuation and engine performance |
US20080078613A1 (en) * | 2006-09-29 | 2008-04-03 | Chin-Chi Liu | Exhaust pipe structure improvement |
US7434570B2 (en) * | 2007-03-16 | 2008-10-14 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
US7896130B2 (en) * | 2009-05-22 | 2011-03-01 | Tenneco Automotive Operating Company Inc. | Snap action valve with inertia damper |
US20100307864A1 (en) * | 2009-06-09 | 2010-12-09 | Bohata John F | Automotive muffler having means for switching between loud and quieter modes |
-
2011
- 2011-01-14 DE DE202011001554U patent/DE202011001554U1/en not_active Expired - Lifetime
- 2011-12-29 EP EP11196003.5A patent/EP2476871A3/en not_active Withdrawn
-
2012
- 2012-01-05 US US13/343,963 patent/US20120181106A1/en not_active Abandoned
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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DE69702447T2 (en) | 1996-04-22 | 2001-02-22 | Wilhelmus Lambertus Arnoldus Meusen | EXHAUST GAS DEVICE FOR INTERNAL COMBUSTION ENGINES AND VEHICLE WITH THIS DEVICE |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11076951B2 (en) | 2012-09-25 | 2021-08-03 | Edwards Lifesciences Corporation | Systems for replacing a native heart valve and aorta with a prosthetic heart valve and conduit |
Also Published As
Publication number | Publication date |
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EP2476871A3 (en) | 2013-10-30 |
US20120181106A1 (en) | 2012-07-19 |
DE202011001554U1 (en) | 2011-04-14 |
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