EP1798390B1 - Engine exhaust apparatus - Google Patents

Engine exhaust apparatus Download PDF

Info

Publication number
EP1798390B1
EP1798390B1 EP06022147A EP06022147A EP1798390B1 EP 1798390 B1 EP1798390 B1 EP 1798390B1 EP 06022147 A EP06022147 A EP 06022147A EP 06022147 A EP06022147 A EP 06022147A EP 1798390 B1 EP1798390 B1 EP 1798390B1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
accordance
flow
exhaust
gas system
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.)
Active
Application number
EP06022147A
Other languages
German (de)
French (fr)
Other versions
EP1798390A3 (en
EP1798390A2 (en
EP1798390B2 (en
Inventor
Rainer Diez
Michael Herbig
Stefan Max
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Friedrich Boysen GmbH and Co KG
Original Assignee
Friedrich Boysen GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=37719822&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1798390(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Friedrich Boysen GmbH and Co KG filed Critical Friedrich Boysen GmbH and Co KG
Publication of EP1798390A2 publication Critical patent/EP1798390A2/en
Publication of EP1798390A3 publication Critical patent/EP1798390A3/en
Application granted granted Critical
Publication of EP1798390B1 publication Critical patent/EP1798390B1/en
Publication of EP1798390B2 publication Critical patent/EP1798390B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/003—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/003—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages
    • F01N1/006—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages comprising at least one perforated tube extending from inlet to outlet of the silencer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1888—Construction facilitating manufacture, assembly, or disassembly the housing of the assembly consisting of two or more parts, e.g. two half-shells

Definitions

  • the present invention relates to an exhaust system for internal combustion engines, in particular motor vehicle engines, according to the preamble of claim 1.
  • turbochargers Especially with turbo engines, it is important that the silencers only a small back pressure is built up, otherwise the turbocharger can not work properly. Another problem with turbochargers is that engines with turbochargers in the upper rpm range are quieter. In order to give the driver a sense of the speed traveled, it is desirable that the driving noise increases with the performance of the engine.
  • the invention has for its object to provide an exhaust system of the type mentioned, which is particularly suitable for use with turbo engines and also allows for turbocharged engines with the performance rising muzzle noise.
  • the two non-flow areas are connected to each other, for example by a pipe section.
  • the two flow-through areas can be advantageously connected to each other via a respective branch and at least one tube.
  • the tube can preferably be guided through the two non-perfused areas and provided there in each case with a perforation, whereby at the same time the two through-flowed areas and the two non-perfused areas are connected to one another.
  • the connection between the two non-flow areas or the two flow-through areas may optionally be closed, in particular by an exhaust flap arranged in the pipe section.
  • This embodiment provides additional tuning options and can be used so that the mouth noise with increasing power also increases.
  • the compound is preferably closed at high speeds or full load and opened at low speeds or partial load.
  • the associated exhaust system can be closed if desired. Via the connection to the other exhaust gas line, the exhaust gas then flows into this other exhaust gas line and, together with the exhaust gas there, to its exhaust gas outlet opening. This results in a cost-effective possibility of variation of the sound-damping behavior of the exhaust system, by which in particular a sporty load feedback can be created.
  • the exhaust flap is closed results in a high sound attenuation, the between the connection between the two exhaust lines and the exhaust flap section is connected in shunt to the other exhaust line. If the exhaust flap is opened, however, a lower sound attenuation and a correspondingly sportier sound is given.
  • the area of the muffler through which the exhaust gas flows is preferably about 10 to about 15% of the total volume. Hereby, particularly good results could be achieved.
  • the area through which the exhaust gas flows may have a volume of less than 2 liters. Such a small area through which flow is particularly advantageous for the mentioned purpose and has not yet been realized.
  • a further reduction in the backpressure can advantageously be achieved in that the area through which it flows has no bent pipe sections.
  • the area flowed through is provided with a short straight pipe section.
  • the exhaust gas can flow through the muffler almost unhindered.
  • the pipe section in the perfused region of the muffler has a perforation and is arranged in a damping chamber, in particular absorption chamber.
  • the absorption chamber forms a non-perfused exhaust gas volume, which is connected by the perforation in the pipe section to the exhaust stream and an additional damping, especially in higher frequency ranges, offers.
  • At least one branch to at least one non-flow-through region can be provided in front of the area through which flow passes.
  • the arrangement of the branch in front of the area through which the damping effect of this area can effectively dampen even by the branch noise.
  • At least one resonator chamber is provided as a non-perfused area.
  • Resonator chambers can be tuned to specific frequencies, for example, to ensure a good damping in the lower speed range.
  • two resonator chambers are connected via a crosspiece to the exhaust stream. This results in good tuning options for two different frequency ranges.
  • the two resonator chambers can also communicate with one another via a perforated intermediate wall.
  • a different tuning can then be done in particular by two guided in the two resonator chambers Abstimmrohr harmonye.
  • Such tuning tube pieces are also advantageous when using two resonator chambers.
  • a compact design of the muffler results when the area through which flowed through and the region through which no flow occurs are arranged in a common housing. Also, connections between the two areas are easy to produce in this construction.
  • the two flow-through areas and the two non-flow areas can be arranged in a common housing. This in turn leads to a compact design. But it is also possible to provide two separate housing, wherein in particular in each case a flow-through area and a non-flow area is assigned to one of the two housings.
  • the geometric design and the arrangement of the muffler is thereby more flexible and can be better adapted to local conditions of a motor vehicle.
  • the resonator chambers are preferably on the lower orders of
  • the exhaust system according to the invention can also be used for diesel engines.
  • the resonator chamber is preferably tuned to the noise peak in the lower speed range of the diesel engine. Even with diesel engines can be achieved by a good sound attenuation without undue impairment of the performance of the diesel engine.
  • An exhaust system with a silencer according to the invention can also be designed without a central silencer.
  • the entire volume flowed through can be further reduced and total, for example, in a six-cylinder engine only 1.5 to 2 liters.
  • connection between the two exhaust lines can be permanently open. Switching means can be eliminated thereby, whereby the costs are further reduced.
  • connection between the two exhaust gas lines is formed according to an embodiment of the invention as a trouser pipe.
  • This is structurally particularly simple and allows for open exhaust flap pressure equalization between the two exhaust strands, while with the exhaust flap closed an overflow of the exhaust gas from one into the other exhaust line is possible.
  • connection between the two exhaust gas lines can also be designed as a perforation in a common partition wall between the two exhaust gas lines. Such a connection is particularly advantageous if the connection is formed in a common muffler of the two exhaust gas lines.
  • a downpipe as a connection between the two exhaust lines can also be used instead of a middle silencer. This results in a further simplified structure.
  • the in Fig. 1 shown muffler comprises two muffler housing 1 and 1 ', each having an exhaust gas inlet opening 2, 2' and an exhaust gas outlet opening 3, 3 'have.
  • the two housings 1, 1 'each have an exhaust gas passage opening 4, 4', which are arranged opposite one another. Through the two exhaust gas passage openings 4, 4 ', an exhaust pipe 5 is guided.
  • Fig. 2 shows the internal structure of the in Fig. 1 Shown on the right silencer 1, wherein the in Fig. 1 Silencer 1 'shown on the left is substantially mirror-inverted.
  • a pipe section 6 is used, which is part of the exhaust pipe system of a motor vehicle exhaust system.
  • the pipe section 6 is connected to a cross pipe piece 7 with four diametrically opposite passage openings 8, 9, 10 and 11.
  • At the first passage opening 8 is the exhaust pipe section 6 connected.
  • To the opposite passage opening 9 includes a short exhaust pipe section 12 with its one end 13, while the second end 14 of the short pipe section 12 opens into the exhaust gas outlet opening 3 of the muffler 1.
  • a short curved pipe section 15 is inserted, and in the opposite passage opening 11 a straight short pipe section sixteenth
  • the opening in the exhaust gas outlet opening 3 of the muffler 1 short straight pipe section 12 is surrounded by a wall 17 formed by a chamber 18 which is filled with absorbent material 19. Via a perforation 20 in the short straight pipe section 12, the absorption chamber 18 is connected to the exhaust gas flow I.
  • the short curved pipe section 15 opens into a resonator chamber 21, which is formed by the housing 1 of the muffler and provided in the housing 1 intermediate wall 22.
  • the intermediate wall 22 is arranged laterally to the damping chamber 18 and approximately parallel to the short straight pipe section 12, so that the resonator chamber 21 surrounds the absorption chamber 18.
  • the second short straight pipe section 16 opens into the second chamber 23 formed on the other side of the intermediate wall 22, which is likewise designed as a resonator chamber.
  • the intermediate wall 22 between the first resonator chamber 21 and the second resonator chamber 23 may be formed perforated. In the illustrated embodiment, however, it is closed.
  • the pipe section 5 inserted into the exhaust gas passage opening 4 of the silencer is, as shown, up to the intermediate wall 22 of the silencer housing 1 out and preferably welded with this.
  • the pipe section 5 is fixed and the entire structure of the muffler stabilized.
  • the pipe section 5 is provided with a perforation 24, via which the pipe section 5 is connected to the second resonator chamber 23.
  • an exhaust flap 26 is arranged, via which the pipe section 5 can be optionally closed.
  • the actuation of the exhaust flap 26 via not shown here means preferably in dependence on the engine speed.
  • the flap 26 may also be omitted, or the connecting pipe may be omitted or permanently closed, for example by the perforation 24 is omitted. Without a flap, there is a compromise between sound and comfort, with closed or omitted connecting pipe, the left and right sides can be tuned differently.
  • the silencer shown is particularly intended for a dual-flow exhaust system, such as a 6-cylinder V-engine.
  • Each of the two exhaust gas lines is connected to one of the two exhaust gas inlet openings 2, 2 'of the illustrated muffler.
  • How to get in Fig. 2 detects the exhaust gas entering via the exhaust gas inlet opening 2 in the direction of arrow I first flows through the cross pipe piece 7 and then the short straight pipe section 12 before it then leaves the muffler again via the exhaust gas outlet opening 3.
  • the way through the muffler is very short and has no directional changes.
  • the exhaust back pressure is very low.
  • the noise of the exhaust gas is attenuated by the absorption chamber 18. additionally There is a sound attenuation through the two resonator chambers 21 and 23, which are connected via the short curved pipe section 15 and the short straight pipe section 16 to the cross tube piece 7 and thus to the exhaust stream I. Over the length of the two pipe sections 15 and 16, the two resonator chambers 21 and 23 are tuned to specific frequency ranges of the exhaust noise, in a turbocharged engine in particular to the higher orders of the exhaust noise.
  • the volume of the flow-through area which is determined by the pipe cross piece 7 and the short straight pipe section 12, according to the invention is particularly small. In particular, it is less than 2 liters, in a 6-cylinder engine, for example, 1.7 liters.
  • the volume of the non-perfused area which is determined by the two resonator chambers 21 and 23 and the absorption chamber 18, relatively large. In the mentioned 6-cylinder engine, it is for example about 15 liters.
  • Fig. 3 illustrated exhaust system includes a first exhaust line 27 and a second exhaust line 28. Both exhaust lines each have a pre-muffler 29 and a muffler 30 on. Between the pre-silencers 29 and the mufflers 30, the two exhaust gas lines 27 and 28 are connected to each other via a sheath 31. In addition, the two mufflers 30 are connected via a connecting tube 32 with each other.
  • Each of the two end silencers 30 of the two exhaust gas lines 27 and 28 is also provided with an end tube 33.
  • an exhaust flap 34 is used, via which the flow through the tail pipe 33 of the first exhaust line 27 can be blocked.
  • the two end muffler 30 can in the in Figures 1 and 2 be formed and described above. But it is also possible any other configuration.
  • the exhaust valve 34 can be opened and closed, for example, depending on the engine speed.
  • the exhaust flap can be closed at low engine speeds to achieve a high level of noise reduction.
  • the exhaust gases of both exhaust lines 27 and 28 can then be ejected only via the tail pipe 33 of the second exhaust line 28. This results in a high sound attenuation with low noise. Due to the low speed there is no unacceptably high exhaust back pressure.
  • the overflow of the exhaust gas from the closed first exhaust line 27 into the second exhaust line takes place via the trouser pipe 31. With the connecting pipe 32 open, an overflow can also be effected by this. Depending on that, then a more or less large section of the first Exhaust line 27 connected in shunt to the second exhaust line 28.
  • Fig. 4 illustrated exhaust system agrees with the in Fig. 3 represented largely agree. It is merely 30 instead of the nozzle tube 31 between the pre-mufflers 29 and the mufflers 30 a middle silencer 35 is provided. This is common to both exhaust lines 27 and 28 and has a connection between the two exhaust lines, for example a perforated wall. The operation of this exhaust system agrees with that of Fig. 3 match.
  • the in Fig. 5 End silencer shown is designed as a common muffler two exhaust lines of an exhaust system. It comprises a housing 36 in which a trouser tube 37 is arranged. Two ends of the trouser pipe 37 form inlet pipes 38, to which the two exhaust gas lines can be connected. The two other ends 39 of the trouser tube 37 are each connected to an outlet tube 40. These are in turn connected to a tailpipe 41.
  • an exhaust valve 42 is inserted, through which the flow through this tail pipe 41 can be blocked.
  • the exhaust flap 42 is closed, the exhaust gas of both exhaust lines flows through the other tail pipe 41, wherein the exhaust gas stream of the obstructed exhaust gas line passes through the trouser pipe 37 in the other exhaust line. This results again in a high sound attenuation with the appropriate comfort.
  • the exhaust flap 42 is open, however, the exhaust gases flow through both tailpipes 41, wherein only a pressure equalization takes place between the two exhaust gas strands via the trouser pipe 37.
  • the internal structure of the rear muffler can otherwise be formed in a known manner, in particular as shown with absorption chambers 43, 44 and resonator 45 and resonator 46. About intermediate walls 47, the chambers 43, 44 and 45 are separated. Via perforations 48, the outlet tubes 40 and the trouser tube 37 are connected to the absorption chambers 43 and 44.
  • the short curved pipe section 15 is omitted, and the pipe section 16 is connected to the tube 5.
  • the connecting pipe 5 has a perforation 49.
  • the absorption chamber 23 is connected to the corresponding chamber of the second muffler of the exhaust system.
  • Fig. 7 variant shown in turn largely agrees with the variant of Fig. 6 match.
  • the chamber 21 is formed as an absorption chamber and the wall 17 is omitted, so that here only two non-flow chambers 21 and 23 are present.
  • the silencer of Fig. 7 is used in particular for the right side of the exhaust system and has no exhaust flap, while the silencer of Fig. 6 is preferably used for the left side of the exhaust system and is provided with an exhaust flap.

Abstract

An exhaust silencer, especially for a turbo charged IC engine, has a small volume straight through chamber linked to a larger volume expansion chamber. The silencer has inlet and outlet (4, 5) ports and comprises a perforated tube linked to cross tubes which connect to an array of expansion chambers whose size and layout provides enhanced damping in the lower engine speeds. The design is optimized to provide progressive increase in sound with engine speed.

Description

Die vorliegende Erfindung betrifft eine Abgasanlage für Brennkraftmaschinen, insbesondere Kraftfahrzeugmotoren, gemäß dem Oberbegriff von Anspruch 1.The present invention relates to an exhaust system for internal combustion engines, in particular motor vehicle engines, according to the preamble of claim 1.

Besonders bei Turbomotoren ist es wichtig, dass durch die Schalldämpfer nur ein geringer Gegendruck aufgebaut wird, da sonst der Turbolader nicht richtig arbeiten kann. Ein weiteres Problem bei Turboladern ist, dass Motoren mit Turboladern im oberen Drehzahlbereich leiser werden. Um dem Fahrer ein Gefühl für die gefahrene Geschwindigkeit zu geben, ist es aber wünschenswert, dass das Fahrgeräusch mit der Leistung des Motors ansteigt.Especially with turbo engines, it is important that the silencers only a small back pressure is built up, otherwise the turbocharger can not work properly. Another problem with turbochargers is that engines with turbochargers in the upper rpm range are quieter. In order to give the driver a sense of the speed traveled, it is desirable that the driving noise increases with the performance of the engine.

Eine Abgasanlage gemäß dem Oberbegriff von Anspruch 1 ist bekannt aus DE-A1-197 43 447 . Weiterer relevanter Stand der Technik ist offenbart in EP-A2-1 380 734 und WO-A1-2005033485 .An exhaust system according to the preamble of claim 1 is known from DE-A1-197 43 447 , Further relevant prior art is disclosed in EP-A2-1 380 734 and WO-A1-2005033485 ,

Der Erfindung liegt die Aufgabe zugrunde, eine Abgasanlage der eingangs genannten Art anzugeben, die besonders gut für Turbomotoren einsetzbar ist und auch bei Turbomotoren ein mit der Leistung ansteigendes Mündungsgeräusch ermöglicht.The invention has for its object to provide an exhaust system of the type mentioned, which is particularly suitable for use with turbo engines and also allows for turbocharged engines with the performance rising muzzle noise.

Diese Aufgabe wird durch eine Abgasanlage mit den Merkmalen von Anspruch 1 gelöst.This object is achieved by an exhaust system with the features of claim 1.

Durch diese Ausgestaltung der Abgasanlage ergibt sich so gut wie kein Gegendruck. Trotzdem kann durch den großen nicht durchströmten Bereich eine gute Schalldämpfung im unteren Drehzahlbereich erreicht werden. Dadurch kann einerseits ein optimales Arbeiten eines Turboladers gewährleistet und andererseits ein mit der Leistung ansteigendes Mündungsgeräusch erzielt werden.This configuration of the exhaust system results in virtually no back pressure. Nevertheless, due to the large non-perfused area a good sound attenuation in the lower speed range can be achieved. As a result, on the one hand, optimal functioning of a turbocharger can be ensured and, on the other hand, a muzzle noise rising with the power can be achieved.

Erfindungsgemäß sind die beiden nicht durchströmten Bereiche miteinander verbunden, beispielsweise durch ein Rohrstück. Auch die beiden durchströmten Bereiche können vorteilhaft über je einen Abzweig und mindestens ein Rohr miteinander verbunden sein. Das Rohr kann dabei bevorzugt durch die beiden nicht durchströmten Bereiche geführt und dort jeweils mit einer Perforierung versehen sein, wodurch gleichzeitig die beiden durchströmten Bereich als auch die beiden nicht durchströmten Bereiche miteinander verbunden sind. In beiden Fällen kann die Verbindung zwischen den beiden nicht durchströmten Bereichen bzw. den beiden durchströmten Bereichen wahlweise verschließbar sein, insbesondere durch eine in dem Rohrstück angeordnete Abgasklappe. Diese Ausgestaltung ergibt zusätzliche Abstimmmöglichkeiten und kann so eingesetzt werden, dass das Mündungsgeräusch mit ansteigender Leistung ebenfalls ansteigt. Hierfür wird die Verbindung bevorzugt bei hohen Drehzahlen oder Volllast geschlossen und bei niedrigen Drehzahlen oder Teillast geöffnet.According to the invention, the two non-flow areas are connected to each other, for example by a pipe section. The two flow-through areas can be advantageously connected to each other via a respective branch and at least one tube. In this case, the tube can preferably be guided through the two non-perfused areas and provided there in each case with a perforation, whereby at the same time the two through-flowed areas and the two non-perfused areas are connected to one another. In both cases, the connection between the two non-flow areas or the two flow-through areas may optionally be closed, in particular by an exhaust flap arranged in the pipe section. This embodiment provides additional tuning options and can be used so that the mouth noise with increasing power also increases. For this purpose, the compound is preferably closed at high speeds or full load and opened at low speeds or partial load.

Durch die Abgasklappe kann der zugehörige Abgasstrang auf Wunsch geschlossen werden. Über die Verbindung zu dem anderen Abgasstrang strömt das Abgas dann in diesen anderen Abgasstrang und zusammen mit dem dortigen Abgas zu dessen Abgasaustrittsöffnung. Damit ergibt sich eine kostengünstige Variationsmöglichkeit des Schalldämpfungsverhaltens der Abgasanlage, durch die insbesondere ein sportliches Last-Feedback geschaffen werden kann. Bei geschlossener Abgasklappe ergibt sich eine hohe Schalldämpfung, wobei der zwischen der Verbindung zwischen den beiden Abgassträngen und der Abgasklappe gelegene Abschnitt im Nebenschluss an den anderen Abgasstrang angeschlossen ist. Wird die Abgasklappe geöffnet, ist dagegen eine geringere Schalldämpfung und entsprechend ein sportlicherer Klang gegeben.By the exhaust flap, the associated exhaust system can be closed if desired. Via the connection to the other exhaust gas line, the exhaust gas then flows into this other exhaust gas line and, together with the exhaust gas there, to its exhaust gas outlet opening. This results in a cost-effective possibility of variation of the sound-damping behavior of the exhaust system, by which in particular a sporty load feedback can be created. When the exhaust flap is closed results in a high sound attenuation, the between the connection between the two exhaust lines and the exhaust flap section is connected in shunt to the other exhaust line. If the exhaust flap is opened, however, a lower sound attenuation and a correspondingly sportier sound is given.

Eine vorteilhafte Anordnung einer solchen Abgasklappe ist im Endrohr. Aufgrund der Verbindung zwischen den beiden Abgassträngen kann das ansonsten bei Verwendung einer Abgasklappe im Endrohr erforderliche zweite Endrohr entfallen. Die Kosten für die Abgasanlage sind dadurch reduziert.An advantageous arrangement of such exhaust flap is in the tailpipe. Due to the connection between the two exhaust strands, the second tail pipe otherwise required when using an exhaust flap in the tailpipe can be omitted. The costs for the exhaust system are reduced.

Eine weitere Kostenreduzierung ergibt sich, wenn eine derartige Abgasklappe nur in einem der beiden Abgasstränge vorgesehen ist. Die Abgasanlage benötigt dann insgesamt nur diese eine Abgasklappe und ein Endrohr je Abgasstrang. Dennoch kann einerseits bei geschlossener Abgasklappe eine hoher Komfort durch starke Schalldämpfung und bei geöffneter Abgasklappe ein sportlicher Klang dank geringem Abgasgegendruck erreicht werden.A further cost reduction results if such an exhaust flap is provided only in one of the two exhaust gas lines. The exhaust system then only needs a total of these exhaust flap and tailpipe per exhaust line. Nevertheless, on the one hand with a closed exhaust flap high comfort can be achieved by strong sound attenuation and with the exhaust flap open a sporty sound thanks to low exhaust back pressure.

Bevorzugt beträgt der vom Abgas durchströmte Bereich des Schalldämpfers ca. 10 bis ca. 15 % des Gesamtvolumens. Hiermit konnten besonders gute Ergebnisse erzielt werden.The area of the muffler through which the exhaust gas flows is preferably about 10 to about 15% of the total volume. Hereby, particularly good results could be achieved.

Bei einem üblichen Kraftfahrzeugmotor, beispielsweise 6-Zylinder-Motor, kann der vom Abgas durchströmte Bereich ein Volumen von weniger als 2 Liter aufweisen. Ein derartig geringer durchströmter Bereich ist für den genannten Einsatzweck besonders vorteilhaft und wurde bisher noch nicht realisiert.In a conventional motor vehicle engine, for example a 6-cylinder engine, the area through which the exhaust gas flows may have a volume of less than 2 liters. Such a small area through which flow is particularly advantageous for the mentioned purpose and has not yet been realized.

Eine weitere Verringerung des Gegendrucks kann vorteilhafterweise dadurch erreicht werden, dass der durchströmte Bereich keine gebogenen Rohrabschnitte aufweist. Insbesondere ist der durchströmte Bereich mit einem kurzen geraden Rohrstück versehen. Das Abgas kann dadurch nahezu ungehindert den Schalldämpfer durchströmen.A further reduction in the backpressure can advantageously be achieved in that the area through which it flows has no bent pipe sections. In particular, the area flowed through is provided with a short straight pipe section. The exhaust gas can flow through the muffler almost unhindered.

Nach einer weiteren Ausgestaltung der Erfindung weist das Rohrstück im durchströmten Bereich des Schalldämpfers eine Perforierung auf und ist in einer Dämpfungskammer, insbesondere Absorptionskammer angeordnet. Die Absorptionskammer bildet ein nicht durchströmtes Abgasvolumen, welches durch die Perforierung im Rohrstück an den Abgasstrom angebunden ist und eine zusätzliche Dämpfung, insbesondere in höheren Frequenzbereichen, bietet.According to a further embodiment of the invention, the pipe section in the perfused region of the muffler has a perforation and is arranged in a damping chamber, in particular absorption chamber. The absorption chamber forms a non-perfused exhaust gas volume, which is connected by the perforation in the pipe section to the exhaust stream and an additional damping, especially in higher frequency ranges, offers.

Vor dem durchströmten Bereich kann außerdem mindestens ein Abzweig zu mindestens einem nicht durchströmten Bereich vorgesehen sein. Durch die Anordnung des Abzweiges vor dem durchströmten Bereich kann die Dämpfungswirkung dieses Bereiches auch durch den Abzweig entstehende Geräusche wirksam dämpfen.In addition, at least one branch to at least one non-flow-through region can be provided in front of the area through which flow passes. The arrangement of the branch in front of the area through which the damping effect of this area can effectively dampen even by the branch noise.

Bevorzugt ist mindestens eine Resonatorkammer als nicht durchströmter Bereich vorgesehen. Resonatorkammern können auf bestimmte Frequenzen abgestimmt werden, um beispielsweise eine gute Dämpfung im unteren Drehzahlbereich sicherzustellen.Preferably, at least one resonator chamber is provided as a non-perfused area. Resonator chambers can be tuned to specific frequencies, for example, to ensure a good damping in the lower speed range.

Nach einer besonders bevorzugten Ausgestaltung sind zwei Resonatorkammern über ein Kreuzstück an den Abgasstrom angeschlossen. Hierdurch ergeben sich gute Abstimmmöglichkeiten auf zwei unterschiedliche Frequenzbereiche.According to a particularly preferred embodiment, two resonator chambers are connected via a crosspiece to the exhaust stream. This results in good tuning options for two different frequency ranges.

Die beiden Resonatorkammern können aber auch über eine perforierte Zwischenwand miteinander in Verbindung stehen. Eine unterschiedliche Abstimmung kann dann insbesondere durch zwei in die beiden Resonatorkammern geführte Abstimmrohrstücke erfolgen. Solche Abstimmrohrstücke sind auch bei Verwendung von zwei Resonatorkammern vorteilhaft.However, the two resonator chambers can also communicate with one another via a perforated intermediate wall. A different tuning can then be done in particular by two guided in the two resonator chambers Abstimmrohrstücke. Such tuning tube pieces are also advantageous when using two resonator chambers.

Eine vorteilhafte Ausgestaltung ergibt sich, wenn eine erste Absorptionskammer über einen Abzweig vor dem kurzen geraden Rohrstück und eine zweite Absorptionskammer über eine Perforierung im kurzen geraden Rohrstück an den Abgasstrom angeschlossen ist. Mit verhältnismäßig wenig Aufwand können dadurch gute Abstimmmöglichkeiten geschaffen werden.An advantageous embodiment is obtained when a first absorption chamber is connected via a branch in front of the short straight pipe section and a second absorption chamber via a perforation in the short straight pipe section to the exhaust gas stream. With relatively little effort this can be created good tuning options.

Ein kompakter Aufbau des Schalldämpfers ergibt sich, wenn der durchströmte Bereich und der nicht durchströmte Bereich in einem gemeinsamem Gehäuse angeordnet sind. Auch sind Verbindungen zwischen den beiden Bereichen bei dieser Bauweise einfach herstellbar.A compact design of the muffler results when the area through which flowed through and the region through which no flow occurs are arranged in a common housing. Also, connections between the two areas are easy to produce in this construction.

Die beiden durchströmten Bereiche und die beiden nicht durchströmten Bereiche können in einem gemeinsamen Gehäuse angeordnet sein. Dies führt wiederum zu einem kompakten Aufbau. Es ist aber auch möglich, zwei getrennte Gehäuse vorzusehen, wobei insbesondere jeweils ein durchströmter Bereich und ein nicht durchströmter Bereich einem der beiden Gehäuse zugeordnet ist. Der geometrische Aufbau und die Anordnung des Schalldämpfers ist hierdurch flexibler und kann besser an örtliche Gegebenheiten eines Kraftfahrzeuges angepasst werden.The two flow-through areas and the two non-flow areas can be arranged in a common housing. This in turn leads to a compact design. But it is also possible to provide two separate housing, wherein in particular in each case a flow-through area and a non-flow area is assigned to one of the two housings. The geometric design and the arrangement of the muffler is thereby more flexible and can be better adapted to local conditions of a motor vehicle.

Bei Verwendung der erfindungsgemäßen Abgasanlage für einen Turbomotor sind die Resonatorkammern bevorzugt auf die tieferen Ordnungen desWhen using the exhaust system according to the invention for a turbo engine, the resonator chambers are preferably on the lower orders of

Geräusches des Turbomotors abgestimmt, beispielsweise 3. bzw. 6. Ordnung im Bereich Leerlauf bis ca. 2100 U/min. Damit kann eine besonders gute Schalldämpfung mit geringer Beeinträchtigung der Leistung des Turbomotors erreicht werden.Sounds of the turbo engine tuned, for example, 3rd or 6th order in the idle area to about 2100 U / min. Thus, a particularly good sound attenuation can be achieved with little impairment of the performance of the turbo engine.

Die erfindungsgemäße Abgasanlage kann auch für Dieselmotoren eingesetzt werden. In diesem Fall ist die Resonatorkammer bevorzugt auf die Geräuschspitze im unteren Drehzahlbereich des Dieselmotors abgestimmt. Auch bei Dieselmotoren kann dadurch eine gute Schalldämpfung ohne übermäßige Beeinträchtigung der Leistung des Dieselmotors erreicht werden.The exhaust system according to the invention can also be used for diesel engines. In this case, the resonator chamber is preferably tuned to the noise peak in the lower speed range of the diesel engine. Even with diesel engines can be achieved by a good sound attenuation without undue impairment of the performance of the diesel engine.

Eine Abgasanlage mit einem erfindungsgemäßen Schalldämpfer kann auch ohne Mittelschalldämpfer ausgebildet sein. Das gesamte durchströmte Volumen kann dadurch weiter reduziert werden und insgesamt beispielsweise bei einem Sechszylindermotor nur 1,5 bis 2 Liter betragen.An exhaust system with a silencer according to the invention can also be designed without a central silencer. The entire volume flowed through can be further reduced and total, for example, in a six-cylinder engine only 1.5 to 2 liters.

Die Verbindung zwischen den beiden Abgassträngen kann dauernd geöffnet sein. Schaltmittel können dadurch entfallen, wodurch die Kosten weiter gesenkt werden.The connection between the two exhaust lines can be permanently open. Switching means can be eliminated thereby, whereby the costs are further reduced.

Die Verbindung zwischen den beiden Abgassträngen ist nach einer Ausgestaltung der Erfindung als Hosenrohr ausgebildet. Dies ist konstruktiv besonders einfach und ermöglicht bei geöffneter Abgasklappe einen Druckausgleich zwischen den beiden Abgassträngen, während bei geschlossener Abgasklappe ein Überströmen des Abgases aus dem einen in den anderen Abgasstrang möglich ist.The connection between the two exhaust gas lines is formed according to an embodiment of the invention as a trouser pipe. This is structurally particularly simple and allows for open exhaust flap pressure equalization between the two exhaust strands, while with the exhaust flap closed an overflow of the exhaust gas from one into the other exhaust line is possible.

Die Verbindung zwischen den beiden Abgassträngen kann auch als Perforation in einer gemeinsamen Trennwand zwischen den beiden Abgassträngen ausgebildet sein. Eine solche Verbindung ist insbesondere dann vorteilhaft, wenn die Verbindung in einem gemeinsamen Schalldämpfer der beiden Abgasstränge ausgebildet ist.The connection between the two exhaust gas lines can also be designed as a perforation in a common partition wall between the two exhaust gas lines. Such a connection is particularly advantageous if the connection is formed in a common muffler of the two exhaust gas lines.

Ein Hosenrohr als Verbindung zwischen den beiden Abgassträngen kann auch anstelle eines Mittelschalldämpfers eingesetzt sein. Dadurch ergibt sich ein noch weiter vereinfachter Aufbau.A downpipe as a connection between the two exhaust lines can also be used instead of a middle silencer. This results in a further simplified structure.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend beschrieben. Es zeigen, jeweils in schematischer Darstellung:

Fig. 1
eine Draufsicht auf einen Schalldämpfer einer erfindungsgemäßen Abgasanlage,
Fig. 2
einen Schnitt durch einen Teil des Schalldämpfers von Fig. 1,
Fig. 3
eine Draufsicht auf eine weitere erfindungemäße Abgasanlage,
Fig. 4
eine Draufsicht auf noch eine erfindungsgemäße Abgasanlage,
Fig. 5
einen Schnitt durch einen Endschalldämpfer einer erfindungsgemäßen Abgasanlage,
Fig. 6
eine Darstellung gemäß Fig. 2 eines weiteren Schalldämpfers einer erfindungsgemäßen Abgasanlage, und
Fig. 7
eine Darstellung gemäß Fig. 2 noch eines Schalldämpfers einer erfindungsgemäßen Abgasanlage.
An embodiment of the invention is illustrated in the drawing and will be described below. They show, in a schematic representation in each case:
Fig. 1
a top view of a muffler of an exhaust system according to the invention,
Fig. 2
a section through a part of the muffler of Fig. 1 .
Fig. 3
a top view of a further erfindungemäße exhaust system,
Fig. 4
a top view of still an exhaust system according to the invention,
Fig. 5
a section through an end muffler of an exhaust system according to the invention,
Fig. 6
a representation according to Fig. 2 a further muffler of an exhaust system according to the invention, and
Fig. 7
a representation according to Fig. 2 nor a muffler of an exhaust system according to the invention.

Der in Fig. 1 dargestellte Schalldämpfer umfasst zwei Schalldämpfergehäuse 1 und 1', die jeweils eine Abgaseintrittsöffnung 2, 2' und eine Abgasaustrittsöffnung 3, 3' aufweisen. Darüber hinaus weisen die beiden Gehäuse 1, 1' jeweils eine Abgasdurchtrittsöffnung 4, 4' auf, die einander gegenüberliegend angeordnet sind. Durch die beiden Abgasdurchtrittsöffnungen 4, 4' ist ein Abgasrohr 5 geführt.The in Fig. 1 shown muffler comprises two muffler housing 1 and 1 ', each having an exhaust gas inlet opening 2, 2' and an exhaust gas outlet opening 3, 3 'have. In addition, the two housings 1, 1 'each have an exhaust gas passage opening 4, 4', which are arranged opposite one another. Through the two exhaust gas passage openings 4, 4 ', an exhaust pipe 5 is guided.

Fig. 2 zeigt den inneren Aufbau des in Fig. 1 rechts dargestellten Schalldämpfers 1, wobei der in Fig. 1 links dargestellte Schalldämpfer 1' im Wesentlichen hierzu spiegelbildlich aufgebaut ist. In die Abgaseintrittsöffnung 2 ist ein Rohrstück 6 eingesetzt, welches Teil des Abgasrohrsystems einer Kraftfahrzeugabgasanlage ist. Das Rohrstück 6 ist mit einem Kreuzrohrstück 7 mit vier diametral gegenüberliegenden Durchtrittsöffnungen 8, 9, 10 und 11 verbunden. An die erste Durchtrittsöffnung 8 ist das Abgasrohrstück 6 angeschlossen. An die gegenüberliegende Durchtrittsöffnung 9 schließt ein kurzes Abgasrohrstück 12 mit seinem einen Ende 13 an, während das zweite Ende 14 des kurzen Rohrstücks 12 in der Abgasaustrittsöffnung 3 des Schalldämpfers 1 mündet. In die dritte Durchtrittsöffnung 10 des Kreuzrohrstückes 7 ist ein kurzes gekrümmtes Rohrstück 15 eingesetzt, und in die gegenüberliegende Durchtrittsöffnung 11 ein gerades kurzes Rohrstück 16. Fig. 2 shows the internal structure of the in Fig. 1 Shown on the right silencer 1, wherein the in Fig. 1 Silencer 1 'shown on the left is substantially mirror-inverted. In the exhaust gas inlet opening 2, a pipe section 6 is used, which is part of the exhaust pipe system of a motor vehicle exhaust system. The pipe section 6 is connected to a cross pipe piece 7 with four diametrically opposite passage openings 8, 9, 10 and 11. At the first passage opening 8 is the exhaust pipe section 6 connected. To the opposite passage opening 9 includes a short exhaust pipe section 12 with its one end 13, while the second end 14 of the short pipe section 12 opens into the exhaust gas outlet opening 3 of the muffler 1. In the third passage opening 10 of the cross tube piece 7, a short curved pipe section 15 is inserted, and in the opposite passage opening 11 a straight short pipe section sixteenth

Das in der Abgasaustrittsöffnung 3 des Schalldämpfers 1 mündende kurze gerade Rohrstück 12 ist von einer durch eine Wandung 17 gebildeten Kammer 18 umgeben, die mit Absorptionsmaterial 19 gefüllt ist. Über eine Perforierung 20 im kurzen geraden Rohrstück 12 ist die Absorptionskammer 18 an den Abgasstrom I angeschlossen.The opening in the exhaust gas outlet opening 3 of the muffler 1 short straight pipe section 12 is surrounded by a wall 17 formed by a chamber 18 which is filled with absorbent material 19. Via a perforation 20 in the short straight pipe section 12, the absorption chamber 18 is connected to the exhaust gas flow I.

Das kurze gekrümmte Rohrstück 15 mündet in einer Resonatorkammer 21, die durch das Gehäuse 1 des Schalldämpfers und eine im Gehäuse 1 vorgesehene Zwischenwand 22 gebildet ist. Die Zwischenwand 22 ist seitlich zur Dämpfungskammer 18 und in etwa parallel zum kurzen geraden Rohrstück 12 angeordnet, so dass die Resonatorkammer 21 die Absorptionskammer 18 umgibt.The short curved pipe section 15 opens into a resonator chamber 21, which is formed by the housing 1 of the muffler and provided in the housing 1 intermediate wall 22. The intermediate wall 22 is arranged laterally to the damping chamber 18 and approximately parallel to the short straight pipe section 12, so that the resonator chamber 21 surrounds the absorption chamber 18.

Das zweite kurze gerade Rohrstück 16 mündet in der auf der anderen Seite der Zwischenwand 22 gebildeten zweiten Kammer 23, die ebenfalls als Resonatorkammer ausgebildet ist. Die Zwischenwand 22 zwischen erster Resonatorkammer 21 und zweiter Resonatorkammer 23 kann perforiert ausgebildet sein. Im dargestellten Ausführungsbeispiel ist sie jedoch geschlossen.The second short straight pipe section 16 opens into the second chamber 23 formed on the other side of the intermediate wall 22, which is likewise designed as a resonator chamber. The intermediate wall 22 between the first resonator chamber 21 and the second resonator chamber 23 may be formed perforated. In the illustrated embodiment, however, it is closed.

Das in die Abgasdurchtrittsöffnung 4 des Schalldämpfers eingesetzte Rohrstück 5 ist, wie dargestellt, bis zur Zwischenwand 22 des Schalldämpfergehäuses 1 geführt und mit dieser bevorzugt verschweißt. Dadurch ist das Rohrstück 5 fixiert und der gesamte Aufbau des Schalldämpfers stabilisiert. In seinem die zweite Resonatorkammer 23 durchgreifenden Abschnitt ist das Rohrstück 5 mit einer Perforierung 24 versehen, über welche das Rohrstück 5 an die zweite Resonatorkammer 23 angeschlossen ist. Wie in Fig. 1 dargestellt, ist in dem zwischen den beiden Teilen des Schalldämpfers gelegenen Abschnitt 25 des Rohrstücks 5 eine Abgasklappe 26 angeordnet, über welche das Rohrstück 5 wahlweise verschlossen werden kann. Die Betätigung der Abgasklappe 26 erfolgt über hier nicht dargestellte Mittel bevorzugt in Abhängigkeit von der Motordrehzahl. Die Klappe 26 kann aber auch entfallen, oder das Verbindungsrohr kann entfallen oder dauernd geschlossen sein, beispielsweise indem die Perforation 24 weggelassen wird. Ohne Klappe ergibt sich ein Kompromiss zwischen Sound und Komfort, bei geschlossenem oder entfallenem Verbindungsrohr können die linke und rechte Seite unterschiedlich abgestimmt werden.The pipe section 5 inserted into the exhaust gas passage opening 4 of the silencer is, as shown, up to the intermediate wall 22 of the silencer housing 1 out and preferably welded with this. As a result, the pipe section 5 is fixed and the entire structure of the muffler stabilized. In its section penetrating the second resonator chamber 23, the pipe section 5 is provided with a perforation 24, via which the pipe section 5 is connected to the second resonator chamber 23. As in Fig. 1 shown, in the located between the two parts of the muffler portion 25 of the pipe section 5, an exhaust flap 26 is arranged, via which the pipe section 5 can be optionally closed. The actuation of the exhaust flap 26 via not shown here means preferably in dependence on the engine speed. But the flap 26 may also be omitted, or the connecting pipe may be omitted or permanently closed, for example by the perforation 24 is omitted. Without a flap, there is a compromise between sound and comfort, with closed or omitted connecting pipe, the left and right sides can be tuned differently.

Der dargestellte Schalldämpfer ist insbesondere für eine zweiflutige Abgasanlage, beispielsweise eines 6 Zylinder V-Motors vorgesehen. Jeder der beiden Abgasstränge ist an eine der beiden Abgaseintrittsöffnungen 2, 2' des dargestellten Schalldämpfers angeschlossen. Wie man in Fig. 2 erkennt, durchströmt das über die Abgaseintrittsöffnung 2 in Richtung des Pfeils I eintretende Abgas zunächst das Kreuzrohrstück 7 und anschließend das kurze gerade Rohrstück 12, bevor es dann über die Abgasaustrittsöffnung 3 den Schalldämpfer wieder verlässt. Wie man erkennt, ist der Weg durch den Schalldämpfer sehr kurz und weist keinerlei Richtungsänderungen auf. Der Abgasgegendruck ist dadurch sehr gering.The silencer shown is particularly intended for a dual-flow exhaust system, such as a 6-cylinder V-engine. Each of the two exhaust gas lines is connected to one of the two exhaust gas inlet openings 2, 2 'of the illustrated muffler. How to get in Fig. 2 detects the exhaust gas entering via the exhaust gas inlet opening 2 in the direction of arrow I first flows through the cross pipe piece 7 and then the short straight pipe section 12 before it then leaves the muffler again via the exhaust gas outlet opening 3. As you can see, the way through the muffler is very short and has no directional changes. The exhaust back pressure is very low.

Während des Durchströmens des geraden Rohrstückes 12 wird das Geräusch des Abgases durch die Absorptionskammer 18 gedämpft. Zusätzlich erfolgt eine Schalldämpfung durch die beiden Resonatorkammern 21 und 23, die über das kurze gekrümmte Rohrstück 15 bzw. das kurze gerade Rohrstück 16 an das Kreuzrohrstück 7 und damit an den Abgasstrom I angeschlossen sind. Über die Länge der beiden Rohrstücke 15 und 16 sind die beiden Resonatorkammern 21 und 23 auf bestimmte Frequenzbereiche des Abgasgeräusches abgestimmt, bei einem Turbomotor insbesondere auf die höheren Ordnungen des Abgasgeräusches.During the passage of the straight pipe section 12, the noise of the exhaust gas is attenuated by the absorption chamber 18. additionally There is a sound attenuation through the two resonator chambers 21 and 23, which are connected via the short curved pipe section 15 and the short straight pipe section 16 to the cross tube piece 7 and thus to the exhaust stream I. Over the length of the two pipe sections 15 and 16, the two resonator chambers 21 and 23 are tuned to specific frequency ranges of the exhaust noise, in a turbocharged engine in particular to the higher orders of the exhaust noise.

Eine zusätzliche Dämpfung ergibt sich durch die Verbindung der beiden Teile 1, 1' des Schalldämpfers über das Rohrstück 5. Diese zusätzliche Dämpfung wird bevorzugt im unteren Drehzahlbereich bzw. Teillast eingesetzt, indem dann die Abgasklappe 26 im Rohrstück 5 geöffnet wird. Bei hohen Drehzahlen bzw. Volllast wird die Abgasklappe 26 dagegen geschlossen, so dass diese zusätzliche Dämpfung entfällt. Dadurch kann vorteilhafterweise bei höheren Drehzahlen ein lauteres Motorgeräusch erreicht werden, was insbesondere bei Turbomotoren wünschenswert ist, die ansonsten bei höheren Drehzahlen zu leise sind.An additional damping results from the connection of the two parts 1, 1 'of the muffler on the pipe section 5. This additional damping is preferably used in the lower speed range or partial load, then the exhaust valve 26 is opened in the pipe section 5. At high speeds or full load, however, the exhaust valve 26 is closed, so that this additional damping is eliminated. As a result, a louder engine noise can advantageously be achieved at higher speeds, which is particularly desirable in turbo engines, which are otherwise too quiet at higher speeds.

Das Volumen des durchströmten Bereiches, welches durch das Rohrkreuzstück 7 und das kurze gerade Rohrstück 12 bestimmt ist, ist erfindungsgemäß besonders klein. Insbesondere beträgt es weniger als 2 Liter, bei einem 6-Zylinder-Motor beispielsweise 1,7 Liter. Demgegenüber ist das Volumen des nicht durchströmten Bereiches, welches durch die beiden Resonatorkammern 21 und 23 sowie die Absorptionskammer 18 bestimmt ist, verhältnismäßig groß. Bei dem genannten 6-Zylinder-Motor beträgt es beispielsweise ca. 15 Liter. Durch diese Aufteilung von nicht durchströmtem Volumen und durchströmtem Volumen erhält man einen sehr geringen Abgasgegendruck bei dennoch sehr guter Schalldämpfungswirkung, die aber auch für Turbomotoren im höheren Drehzahlbereich nicht zu groß ist.The volume of the flow-through area, which is determined by the pipe cross piece 7 and the short straight pipe section 12, according to the invention is particularly small. In particular, it is less than 2 liters, in a 6-cylinder engine, for example, 1.7 liters. In contrast, the volume of the non-perfused area, which is determined by the two resonator chambers 21 and 23 and the absorption chamber 18, relatively large. In the mentioned 6-cylinder engine, it is for example about 15 liters. Through this division of non-flowed volume and volume flowed through, one obtains a very low exhaust gas backpressure with nevertheless very good sound damping effect, which is not too great for turbo engines in the higher speed range.

Die in Fig. 3 dargestellte Abgasanlage umfasst einen ersten Abgasstrang 27 und einen zweiten Abgasstrang 28. Beide Abgasstränge weisen jeweils einen Vorschalldämpfer 29 und einen Endschalldämpfer 30 auf. Zwischen den Vorschalldämpfern 29 und den Endschalldämpfern 30 sind die beiden Abgasstränge 27 und 28 über ein Hosenrohr 31 miteinander verbunden. Außerdem sind die beiden Endschalldämpfer 30 über ein Verbindungsrohr 32 miteinander verbunden.In the Fig. 3 illustrated exhaust system includes a first exhaust line 27 and a second exhaust line 28. Both exhaust lines each have a pre-muffler 29 and a muffler 30 on. Between the pre-silencers 29 and the mufflers 30, the two exhaust gas lines 27 and 28 are connected to each other via a sheath 31. In addition, the two mufflers 30 are connected via a connecting tube 32 with each other.

Jeder der beiden Endschalldämpfer 30 der beiden Abgasstränge 27 und 28 ist außerdem mit einem Endrohr 33 versehen. In das Endrohr 33 des ersten Abgasstranges 27 ist eine Abgasklappe 34 eingesetzt, über welche der Durchfluss durch das Endrohr 33 des ersten Abgasstranges 27 gesperrt werden kann. Die beiden Endschalldämpfer 30 können in der in den Figuren 1 und 2 dargestellten und vorstehend beschriebenen Weise ausgebildet sein. Es ist aber auch jede andere Ausgestaltung möglich.Each of the two end silencers 30 of the two exhaust gas lines 27 and 28 is also provided with an end tube 33. In the tail pipe 33 of the first exhaust line 27, an exhaust flap 34 is used, via which the flow through the tail pipe 33 of the first exhaust line 27 can be blocked. The two end muffler 30 can in the in Figures 1 and 2 be formed and described above. But it is also possible any other configuration.

Der Betrieb der in Fig. 3 dargestellten Abgasanlage erfolgt in üblicher Weise, wobei die Abgasklappe 34 auf- und zugesteuert werden kann, beispielsweise in Abhängigkeit von der Motordrehzahl. So kann die Abgasklappe bei niedrigen Motordrehzahlen geschlossen sein, um eine hohe Schalldämpfung zu erreichen. Die Abgase beider Abgasstränge 27 und 28 können dann nur über das Endrohr 33 des zweiten Abgasstrangs 28 ausgestoßen werden. Hierdurch ergibt sich eine hohe Schalldämpfung mit geringer Geräuschentwicklung. Aufgrund der niedrigen Drehzahl entsteht dabei kein inakzeptabel hoher Abgasgegendruck. Das Überströmen des Abgases aus dem geschlossenen ersten Abgasstrang 27 in den zweiten Abgasstrang erfolgt dabei über das Hosenrohr 31. Bei geöffnetem Verbindungsrohr 32 kann ein Überströmen außerdem auch durch dieses erfolgen. Je nachdem ist dann ein mehr oder weniger großer Abschnitt des ersten Abgasstrangs 27 im Nebenschluss an den zweiten Abgasstrang 28 angeschlossen.Operation of in Fig. 3 The exhaust system shown in the usual way, the exhaust valve 34 can be opened and closed, for example, depending on the engine speed. Thus, the exhaust flap can be closed at low engine speeds to achieve a high level of noise reduction. The exhaust gases of both exhaust lines 27 and 28 can then be ejected only via the tail pipe 33 of the second exhaust line 28. This results in a high sound attenuation with low noise. Due to the low speed there is no unacceptably high exhaust back pressure. The overflow of the exhaust gas from the closed first exhaust line 27 into the second exhaust line takes place via the trouser pipe 31. With the connecting pipe 32 open, an overflow can also be effected by this. Depending on that, then a more or less large section of the first Exhaust line 27 connected in shunt to the second exhaust line 28.

Bei geöffneter Abgasklappe 34 können die Abgase durch beide Endrohre 33 ausströmen. Die Abgasströme des ersten und des zweiten Abgasstrangs 27, 28 bleiben dabei weitgehend getrennt. Über das Hosenrohr 31 erfolgt lediglich ein Druckausgleich. In diesem-Zustand ergibt sich eine geringere Schalldämpfung mit entsprechend geringerem Gegendruck und höherer Geräuschentwicklung. Diese ist als Last-Feedback allerdings erwünscht.When the exhaust flap 34 is open, the exhaust gases can flow out through both end pipes 33. The exhaust gas streams of the first and second exhaust line 27, 28 remain largely separated. About the sheath tube 31 is only a pressure compensation. In this state results in a lower sound attenuation with correspondingly lower back pressure and higher noise. However, this is desirable as load feedback.

Die in Fig. 4 dargestellte Abgasanlage stimmt mit der in Fig. 3 dargestellten weitgehend überein. Es ist lediglich anstelle des Hosenrohres 31 zwischen den Vorschalldämpfern 29 und den Endschalldämpfern 30 ein Mittelschalldämpfer 35 vorgesehen. Dieser ist beiden Abgassträngen 27 und 28 gemein und weist eine Verbindung zwischen den beiden Abgassträngen, beispielsweise eine perforierte Wand auf. Auch der Betrieb dieser Abgasanlage stimmt mit derjenigen von Fig. 3 überein.In the Fig. 4 illustrated exhaust system agrees with the in Fig. 3 represented largely agree. It is merely 30 instead of the nozzle tube 31 between the pre-mufflers 29 and the mufflers 30 a middle silencer 35 is provided. This is common to both exhaust lines 27 and 28 and has a connection between the two exhaust lines, for example a perforated wall. The operation of this exhaust system agrees with that of Fig. 3 match.

Der in Fig. 5 dargestellte Endschalldämpfer ist als gemeinsamer Schalldämpfer zweier Abgasstränge einer Abgasanlage ausgebildet. Er umfasst ein Gehäuse 36, in welchem ein Hosenrohr 37 angeordnet ist. Zwei Enden des Hosenrohres 37 bilden Einlassrohre 38, an welche die beiden Abgasstränge anschließbar sind. Die beiden anderen Enden 39 des Hosenrohres 37 sind jeweils mit einem Auslassrohr 40 verbunden. Diese sind wiederum mit je einem Endrohr 41 verbunden.The in Fig. 5 End silencer shown is designed as a common muffler two exhaust lines of an exhaust system. It comprises a housing 36 in which a trouser tube 37 is arranged. Two ends of the trouser pipe 37 form inlet pipes 38, to which the two exhaust gas lines can be connected. The two other ends 39 of the trouser tube 37 are each connected to an outlet tube 40. These are in turn connected to a tailpipe 41.

In das eine Endrohr 41 ist ein Abgasklappe 42 eingesetzt, durch welche der Durchfluss durch dieses Endrohr 41 versperrt werden kann. Damit ergibt sich dieselbe Funktion wie bei den Abgasanlagen der Figuren 3 und 4. Bei geschlossener Abgasklappe 42 strömt das Abgas beider Abgasstränge durch das andere Endrohr 41 aus, wobei der Abgasstrom des versperrten Abgasstranges über das Hosenrohr 37 in den anderen Abgasstrang gelangt. Dadurch ergibt sich wieder eine hohe Schalldämpfung mit entsprechendem Komfort. Bei geöffneter Abgasklappe 42 strömen die Abgase dagegen durch beide Endrohre 41, wobei zwischen den beiden Abgassträngen über das Hosenrohr 37 lediglich ein Druckausgleich stattfindet.In the one end pipe 41, an exhaust valve 42 is inserted, through which the flow through this tail pipe 41 can be blocked. This results in the same function as in the exhaust systems of Figures 3 and 4 , When the exhaust flap 42 is closed, the exhaust gas of both exhaust lines flows through the other tail pipe 41, wherein the exhaust gas stream of the obstructed exhaust gas line passes through the trouser pipe 37 in the other exhaust line. This results again in a high sound attenuation with the appropriate comfort. When the exhaust flap 42 is open, however, the exhaust gases flow through both tailpipes 41, wherein only a pressure equalization takes place between the two exhaust gas strands via the trouser pipe 37.

Vom Innenaufbau her kann der Endschalldämpfer im übrigen in bekannter Weise ausgebildet sein, insbesondere wie dargestellt mit Absorptionskammern 43, 44 und Resonatorkammer 45 sowie Resonatorrohr 46. Über Zwischenwände 47 sind die Kammern 43, 44 und 45 voneinander getrennt. Über Perforierungen 48 sind die Auslassrohre 40 und das Hosenrohr 37 an die Absorptionskammern 43 und 44 angeschlossen.The internal structure of the rear muffler can otherwise be formed in a known manner, in particular as shown with absorption chambers 43, 44 and resonator 45 and resonator 46. About intermediate walls 47, the chambers 43, 44 and 45 are separated. Via perforations 48, the outlet tubes 40 and the trouser tube 37 are connected to the absorption chambers 43 and 44.

Die in Fig. 6 dargestellte Variante stimmt weitgehend mit der Variante von Fig. 2 überein. Im Unterschied hierzu ist jedoch das kurze gekrümmte Rohrstück 15 weggelassen, und das Rohrstück 16 ist mit dem Rohr 5 verbunden. Im Bereich der Kammer 23, die hier als Absorptionskammer ausgebildet ist, weist das Verbindungsrohr 5 eine Perforierung 49 auf. Hierdurch ist die Absorptionskammer 23 mit der entsprechenden Kammer des zweiten Schalldämpfers der Abgasanlage verbunden.In the Fig. 6 illustrated variant is largely consistent with the variant of Fig. 2 match. In contrast, however, the short curved pipe section 15 is omitted, and the pipe section 16 is connected to the tube 5. In the region of the chamber 23, which is designed here as an absorption chamber, the connecting pipe 5 has a perforation 49. As a result, the absorption chamber 23 is connected to the corresponding chamber of the second muffler of the exhaust system.

Die in Fig. 7 dargestellte Variante stimmt wiederum weitgehend mit der Variante von Fig. 6 überein. Im Unterschied hierzu ist jedoch die Kammer 21 als Absorptionskammer ausgebildet und die Wandung 17 ist weggelassen, so dass hier nur zwei nicht durchströmte Kammern 21 und 23 vorhanden sind. Der Schalldämpfer von Fig. 7 wird insbesondere für die rechte Seite der Abgasanlage eingesetzt und weist keine Abgasklappe auf, während der Schalldämpfer von Fig. 6 bevorzugt für die linke Seite der Abgasanlage eingesetzt wird und mit einer Abgasklappe versehen ist.In the Fig. 7 variant shown in turn largely agrees with the variant of Fig. 6 match. In contrast, however, the chamber 21 is formed as an absorption chamber and the wall 17 is omitted, so that here only two non-flow chambers 21 and 23 are present. The silencer of Fig. 7 is used in particular for the right side of the exhaust system and has no exhaust flap, while the silencer of Fig. 6 is preferably used for the left side of the exhaust system and is provided with an exhaust flap.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
erstes Schalldämpfergehäusefirst silencer housing
1'1'
zweites Schalldämpfergehäusesecond silencer housing
22
Abgaseintrittsöffnung von 1Exhaust gas inlet opening of 1
22
Abgaseintrittsöffnung von 1'Exhaust gas inlet opening of 1 '
33
Abgasaustrittsöffnung von 1Exhaust outlet of 1
3'3 '
Abgasaustrittsöffnung von 1'Exhaust outlet of 1 '
44
Abgasdurchtrittsöffnung von 1Exhaust gas passage opening of 1
4'4 '
Abgasdurchtrittsöffnung von 1'Exhaust gas passage opening of 1 '
55
Rohrstückpipe section
66
Rohrstückpipe section
77
KreuzrohrstückCross pipe section
88th
AbgaseintrittsöffnungExhaust gas inlet opening
99
AbgaseintrittsöffnungExhaust gas inlet opening
1010
AbgaseintrittsöffnungExhaust gas inlet opening
1111
AbgaseintrittsöffnungExhaust gas inlet opening
1212
kurzes gerades Rohrstückshort straight piece of pipe
1313
erstes Ende von 12first end of 12
1414
zweites Ende von 12second end of 12
1515
kurzes gebogenes Rohrstückshort bent piece of pipe
1616
kurzes gerades Rohrstückshort straight piece of pipe
1717
Wandungwall
1818
Absorptionskammerabsorption chamber
1919
Absorptionsmaterialabsorbent material
2020
Perforierungperforation
2121
erste Resonatorkammerfirst resonator chamber
2222
Zwischenwandpartition
2323
zweite Resonatorkammersecond resonator chamber
2424
Perforierungperforation
2525
Abschnitt von 5Section of 5
2626
Abgasklappeexhaust flap
2727
erster Abgasstrangfirst exhaust system
2828
zweiter Abgasstrangsecond exhaust system
2929
Vorschalldämpfersilencer
3030
Endschalldämpfermuffler
3131
HosenrohrY-pipe
3232
Verbindungsrohrconnecting pipe
3333
Endrohrtailpipe
3434
Abgasklappeexhaust flap
3535
Mittelschalldämpfermiddle silencer
3636
Gehäusecasing
3737
HosenrohrY-pipe
3838
Einlassrohrinlet pipe
3939
Auslassende von 37Exit end of 37
4040
Auslassrohroutlet pipe
4141
Endrohrtailpipe
4242
Abgasklappeexhaust flap
4343
Absorptionskammerabsorption chamber
4444
Absorptionskammerabsorption chamber
4545
Resonatorkammerresonator
4646
Resonatorrohrresonator
4747
Zwischenwandpartition
4848
Perforationperforation
4949
Perforationperforation
5050
Abzweigjunction
II
AbgasstromrichtungExhaust gas flow direction

Claims (22)

  1. An exhaust gas system for internal combustion engines, in particular for motor vehicle engines, with two exhaust tracts (27, 28) in particular each associated with one cylinder bank of an engine and each having a silencer (1, 1'), in particular a rear silencer, with an exhaust gas inlet opening (2, 2'), an exhaust gas outlet opening (3, 3'), a region (7, 12) through which exhaust gas flows and a region (18, 21, 23) through which exhaust gas does not flow, wherein an exhaust gas flap (34, 42) is provided in a region of one of the two exhaust gas tracts (27, 28) through which flow takes place and by which this exhaust gas tract can be closed, wherein the two exhaust gas tracts (27, 28) furthermore have at least one connection (5, 31, 32, 35, 37), through which flow can take place, upstream of the exhaust gas flap (34, 42) and which is open at least with a closed exhaust gas flap (34, 42) and wherein, in addition, the region (7, 12) of the silencers (1, 1') through which the exhaust gas flows is considerably smaller than the region (18, 21, 23) through which the exhaust gas does not flow,
    characterised in that
    the two regions (18, 21, 23) through which flow does not take place are connected to one another.
  2. An exhaust gas system in accordance with claim 1, characterised in that the exhaust gas flap (34, 42) is arranged in the end pipe (33, 41); and in that the associated exhaust tract (27) only has this one end pipe (33, 41).
  3. An exhaust gas system in accordance with claim 1 or claim 2, characterised in that the connection (31, 35, 37) is permanently open; and/or in that the connection (31, 37) is made as a Y pipe.
  4. An exhaust gas system in accordance with any one of the claims 1 to 3, characterised in that the connection is made as a perforation in a common dividing wall between the two exhaust gas tracts (27, 28), with the Y pipe (31) preferably being used instead of a centre silencer or with the Y pipe preferably being inserted into a silencer, in particular into an end silencer.
  5. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the region (7, 12) of the silencer through which the exhaust gas flows amounts to approximately 10 to approximately 15% of the total volume of the silencer.
  6. An exhaust system in accordance with any one of the preceding claims characterised in that the region (7, 12) through which the exhaust gas flows has a volume of less than 2 litres.
  7. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the region (7, 12) through which flow takes place does not have any curved pipe sections.
  8. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the region (7, 12) through which flow takes place has a short, straight pipe section (12), with the short, straight pipe section (12) preferably having a perforation (20) in the region of the silencer through which flow takes place and being arranged in a damping chamber (18), in particular in an absorption chamber.
  9. An exhaust gas system in accordance with any one of the preceding claims, characterised in that a branch-off (7, 50) to at least one region (21, 23) through which flow does not take place is provided before the short, straight pipe section (12), with a first absorption chamber (23) preferably being connected to the exhaust gas flow before the short, straight pipe section (12) via a branch-off (50) and a second resonator chamber preferably being connected to the exhaust gas flow via a perforation (20) in the short, straight pipe section (12).
  10. An exhaust gas system in accordance with any one of the preceding claims, characterised in that at least one resonator chamber (21, 23) is provided as the region through which flow does not take place.
  11. An exhaust gas system in accordance with any one of the preceding claims, characterised in that two resonator chambers (21, 23) are connected to the exhaust gas flow (I) via a cross pipe (7).
  12. An exhaust gas system in accordance with any one of the preceding claims, characterised in that two resonator chambers (21, 23) having a perforated intermediate wall (22) or a non-perforated intermediate wall are provided.
  13. An exhaust gas system in accordance with any one of the preceding claims, characterised in that at least one resonator chamber (21, 23) is provided which is connected to the exhaust gas flow via a tuning pipe (15, 16).
  14. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the region (7, 12) through which flow takes place and the region (18, 21, 23) through which flow does not take place are arranged in a common housing (1).
  15. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the two regions (18, 21, 23) through which flow does not take place are connected to one another by a pipe section (5).
  16. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the two regions (7, 12) through which flow takes place are connected to one another via one respective branch-off (50) each and via at least one pipe (5), with the pipe section (5) preferably being guided by the two regions (23, 23') through which flow does not take place and being provided there in each case with a perforation (49).
  17. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the connection (5) is selectively closable, in particular by an exhaust gas flap (26) arranged in the pipe section (5), with the connection (5) preferably being closed at high speeds or at full load and being open at low speeds or part load.
  18. An exhaust gas system in accordance with any one of the preceding claims, characterised in that all the regions (18, 21, 23) are arranged in a common housing; or in that two separate housings (1, 1') are provided.
  19. An exhaust gas system in accordance with any one of the preceding claims, characterised in that it is used for a turbo engine, with the resonator chambers (21, 23) preferably being matched to the higher orders of the exhaust gas noise of the turbo engine.
  20. An exhaust gas system in accordance with any one of the claims 1 to 18, characterised in that it is used for a diesel engine, with the resonator chambers (21, 32) preferably being matched to the noise peaks in the lower speed range of the diesel engine.
  21. An exhaust gas system in accordance with any one of the preceding claims, characterised in that the matching is carried out such that the exhaust gas noise increases substantially continuously over the total speed range.
  22. An exhaust gas system in accordance with any one of the preceding claims, characterised in that no middle silencer is provided.
EP06022147.0A 2005-12-15 2006-10-23 Engine exhaust apparatus Active EP1798390B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005060053 2005-12-15
DE102006020155A DE102006020155A1 (en) 2005-12-15 2006-05-02 Exhaust system for internal combustion engines

Publications (4)

Publication Number Publication Date
EP1798390A2 EP1798390A2 (en) 2007-06-20
EP1798390A3 EP1798390A3 (en) 2007-07-04
EP1798390B1 true EP1798390B1 (en) 2009-12-30
EP1798390B2 EP1798390B2 (en) 2014-11-12

Family

ID=37719822

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06022147.0A Active EP1798390B2 (en) 2005-12-15 2006-10-23 Engine exhaust apparatus

Country Status (4)

Country Link
EP (1) EP1798390B2 (en)
AT (1) ATE453784T1 (en)
DE (2) DE102006020155A1 (en)
ES (1) ES2335794T3 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006020155A1 (en) † 2005-12-15 2007-06-21 Friedrich Boysen Gmbh & Co. Kg Exhaust system for internal combustion engines
DE102007052343B4 (en) * 2007-11-02 2022-02-10 Volkswagen Ag Method and device for displaying data in a vehicle
DE102009032214B4 (en) * 2009-07-06 2023-10-19 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Exhaust system of an internal combustion engine
DE102012112433A1 (en) 2012-12-17 2014-06-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Exhaust system for an internal combustion engine
KR101511541B1 (en) * 2013-11-15 2015-04-13 현대자동차주식회사 Structure of dual exhaust system for cda engine
DE102016106340A1 (en) 2016-04-07 2017-10-12 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Exhaust system for a motor vehicle and motor vehicle

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT137590B (en) * 1931-06-20 1934-05-11 Burgess Lab Inc C F Silencer.
US2139151A (en) * 1936-03-16 1938-12-06 Floyd E Deremer Silencer construction
DE1725614U (en) * 1956-01-16 1956-07-05 Eberspaecher J SILENCER FOR EXHAUST GAS TURBINES.
US3434565A (en) * 1967-12-21 1969-03-25 Walker Mfg Co Silencer with angled tuning tube leading to helmholtz resonator
US3500954A (en) * 1969-03-13 1970-03-17 Walker Mfg Co Exhaust silencing system
DE2110000B1 (en) * 1971-03-03 1972-11-23 Paul Gillet Gmbh, 6732 Edenkoben Exhaust system with two separate exhaust pipes
DE2706957C2 (en) * 1977-02-18 1983-04-07 Friedrich Boysen Gmbh & Co Kg, 7272 Altensteig Exhaust silencer
US4501341A (en) * 1981-03-12 1985-02-26 Jones Adrian D Low frequency muffler
JPS58148215A (en) * 1982-02-25 1983-09-03 Nissan Motor Co Ltd Muffler of automobile engine
DE3807948A1 (en) * 1988-03-10 1989-09-28 Eberspaecher J Silencer for vehicle engines
JPH0412145A (en) * 1990-04-28 1992-01-16 Mazda Motor Corp Control device for engine
JP2686165B2 (en) * 1990-05-09 1997-12-08 株式会社三五 Muffler for dual exhaust system of internal combustion engine
DE19743446C2 (en) * 1997-05-26 2002-12-12 Bayerische Motoren Werke Ag Exhaust system for an internal combustion engine
DE19743447A1 (en) 1997-09-25 1999-04-01 Voewa Plattenwerk Gmbh Process for the production of plates
US6068082A (en) * 1997-11-21 2000-05-30 D'amico, Jr.; John Muffler packing method and apparatus
US6935461B2 (en) † 1998-08-18 2005-08-30 Gregory M. Marocco Exhaust sound and emission control systems
DE20120470U1 (en) * 2001-12-18 2003-04-30 Boysen Friedrich Gmbh Co Kg Muffler means
DE10231056A1 (en) * 2002-07-10 2004-02-05 J. Eberspächer GmbH & Co. KG exhaust system
DE10331620A1 (en) * 2003-07-12 2005-02-03 Daimlerchrysler Ag Device for noise shaping in a motor vehicle
EP1507071B2 (en) * 2003-08-11 2019-10-16 Faurecia Emissions Control Technologies, Germany GmbH Exhaust silencer
DE10346479A1 (en) † 2003-10-02 2005-05-12 Bayerische Motoren Werke Ag Exhaust system for an internal combustion engine
DE102004022721A1 (en) † 2004-05-07 2005-11-24 Dr.Ing.H.C. F. Porsche Ag Double-flow exhaust system for an internal combustion engine
DE102005003582A1 (en) * 2005-01-26 2006-08-03 Dr.Ing.H.C. F. Porsche Ag Silencer for an exhaust system
DE102006020155A1 (en) † 2005-12-15 2007-06-21 Friedrich Boysen Gmbh & Co. Kg Exhaust system for internal combustion engines

Also Published As

Publication number Publication date
DE102006020155A1 (en) 2007-06-21
EP1798390A3 (en) 2007-07-04
EP1798390A2 (en) 2007-06-20
ATE453784T1 (en) 2010-01-15
ES2335794T3 (en) 2010-04-05
DE502006005775D1 (en) 2010-02-11
EP1798390B2 (en) 2014-11-12

Similar Documents

Publication Publication Date Title
EP1760279B1 (en) Silencer for an exhaust system
EP1686246B1 (en) Silencer for an exhaust gas system
EP3311009B1 (en) Exhaust system
EP1959106B2 (en) Silencer for an exhaust system
EP1798390B1 (en) Engine exhaust apparatus
DE10333096B4 (en) Vehicle exhaust system with length-compensating silencer
DE19743446C2 (en) Exhaust system for an internal combustion engine
DE102015011175B4 (en) Exhaust system for an internal combustion engine
DE10300773A1 (en) Exhaust gas unit for a multicylinder combustion engine especially for a motor vehicle has perforated mixing chamber from which exhaust gas enters an expansion chamber
EP1321639B2 (en) Silencer arrangement
DE2706957C2 (en) Exhaust silencer
DE112020002964B4 (en) Exhaust system and silencer
EP3061931A1 (en) Exhaust gas system for a combustion engine
DE10008458B4 (en) Exhaust system for a motorcycle
DE19638304A1 (en) Gas-pipe silencer with baffles in chamber
EP2788599A1 (en) Silencer arrangement
DE102009054074B4 (en) Silencer arrangement in an exhaust line of an internal combustion engine
EP0705961B1 (en) Exhaust silencer
DE102005004674B4 (en) Device for silencing pulsating gas flows
DE102005031272A1 (en) Exhaust system for four- or eight-cylinder internal combustion (IC) engine for motor vehicle, has cross joint, interposed between pre-tubes downstream of catalysts, having cross-sectional area variable as function of engine speed
DE19605540A1 (en) Exhaust gas silencer for motorcycle IC-engine
DE202017107901U1 (en) muffler assembly
DE2711190B2 (en) Silencers for flowing gases, in particular exhaust gases from vehicle internal combustion engines
DE2949139A1 (en) IC engine exhaust silencer system - has partitions forming absorption and reflection chambers of defined relative volumes and lengths of connections
DE102011010595A1 (en) Double-flow exhaust system for e.g. V-type petrol engine of vehicle, has coupling element fluidically coupling exhaust lines together, and particulate filters arranged in respective exhaust lines, which are overlapped with each other

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20070801

17Q First examination report despatched

Effective date: 20070830

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502006005775

Country of ref document: DE

Date of ref document: 20100211

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2335794

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20091230

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20091230

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100330

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100430

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100331

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: J. EBERSPAECHER GMBH & CO. KG

Effective date: 20100923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

PLAF Information modified related to communication of a notice of opposition and request to file observations + time limit

Free format text: ORIGINAL CODE: EPIDOSCOBS2

BERE Be: lapsed

Owner name: FRIEDRICH BOYSEN G.M.B.H. & CO. KG

Effective date: 20101031

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101031

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20101023

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101031

Ref country code: CZ

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101023

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101102

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101031

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101023

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20111118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101023

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101023

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091230

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 20141112

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: DE

Ref legal event code: R102

Ref document number: 502006005775

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R102

Ref document number: 502006005775

Country of ref document: DE

Effective date: 20141112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141112

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20231020

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20231227

Year of fee payment: 18