US20020083703A1 - Manifold arrangement for exhaust systems - Google Patents

Manifold arrangement for exhaust systems Download PDF

Info

Publication number
US20020083703A1
US20020083703A1 US10/001,188 US118801A US2002083703A1 US 20020083703 A1 US20020083703 A1 US 20020083703A1 US 118801 A US118801 A US 118801A US 2002083703 A1 US2002083703 A1 US 2002083703A1
Authority
US
United States
Prior art keywords
pipes
pipe
parallel
manifold arrangement
arrangement according
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.)
Abandoned
Application number
US10/001,188
Other languages
English (en)
Inventor
Andreas Werth
Christian Skorianz
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.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of US20020083703A1 publication Critical patent/US20020083703A1/en
Abandoned legal-status Critical Current

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
    • 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
    • F01N13/04—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 having two or more silencers in parallel, e.g. having interconnections for multi-cylinder engines
    • 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
    • F01N1/06—Silencing apparatus characterised by method of silencing by using interference effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • 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
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • 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
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/28—Construction of catalytic reactors
    • F01N3/2882—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices
    • F01N3/2885—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices with exhaust silencers in a single housing
    • 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
    • F01N2330/00—Structure of catalyst support or particle filter
    • F01N2330/02—Metallic plates or honeycombs, e.g. superposed or rolled-up corrugated or otherwise deformed sheet metal
    • 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
    • F01N2330/00—Structure of catalyst support or particle filter
    • F01N2330/06—Ceramic, e.g. monoliths
    • 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
    • F01N2330/00—Structure of catalyst support or particle filter
    • F01N2330/12—Metallic wire mesh fabric or knitting
    • 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
    • F01N2330/00—Structure of catalyst support or particle filter
    • F01N2330/14—Sintered material

Definitions

  • the invention relates to a manifold arrangement for exhaust systems of internal combustion engines, especially multi-cylinder motorcycle engines, for installation between the exhaust gas outlet pipes coming from the, or each, cylinder and at least one muffler, where the exhaust gas outlet pipes of the cylinders are combined stepwise, if applicable, so as to finally form one joint pipe where behind said joint pipe a branch is provided that divides the exhaust gas flow into at least two pipes which are separated from each other, are parallel in a flow-wise manner and together having a larger cross-sectional surface than the joint pipe, and behind said pipes a joining element is provided, so as to again form one single collector pipe where the collector pipe has a free flow cross-section that matches at least the surface sum of the parallel pipes and performs a wave impedance function in said collector pipe.
  • Each cylinder induces oscillations that are maintained at least until the next outflow cycle of said same cylinder, where complex resonance patterns of residual oscillations can develop if multiple cylinders are provided, which are in resonance with the shock waves coming from the cylinders in the critical speed and frequency ranges and which in said resonance ranges will result in a decrease in the performance and an increase in the noise level.
  • EP 421 724 discloses an arrangement where the exhaust gas flow is divided into at least two pipes which are subsequently recombined. Said arrangement works by damping standing waves by means of interference based on the parallel pipes having varying lengths. It is mentioned several times that pressure reactions in the preceding sections of the exhaust gas line, such as a wave impedance, for example, should be prevented. It is also of considerable importance that the cross-sectional surface of the parallel pipes is at least equal or larger than the inlet cross-sectional surface and also at least equal or larger than the downstream sections.
  • the objective of the invention is a manifold arrangement as described above offering an increase in efficiency continuously over the full range of speed of a multi-cylinder engine while largely preventing adverse resonance phenomena while providing adequate sound damping, which can be achieved at the same time with the smallest possible size so as to especially allow it to be used in motorcycles or so as not to excessively reduce the available space for other components in automobiles.
  • the collector pipe has a free flow cross-section matching at least the surface sum of the parallel pipes and that a component serving as a wave impedance is installed in said continuing collector pipe, which component allows the exhaust gas volume flow to pass unhindered while pressure waves are forced to perform the most complete possible total reflection on said component.
  • the division of the exhaust gas flow from the single joint pipe into at least two parallel pipes causes a pressure wave, which is undivided before the branch, to be divided into multiple waves whose total energy is equal to the original wave and which pass through the downstream parallel channels in the form of individualized and independent wave fronts.
  • microwave impedance component dissolves the portion of the wave energy that escapes the total reflection and passes the component into a diffuse wave pattern, thereby preventing the development of undesired resonance oscillations in a muffler installed downstream.
  • the low pressure waves resulting from the alternating reflections in the proposed arrangement which would travel in the direction to the muffler after the collector pipe, are reflected as similar low pressure waves in the direction to the engine whereby an additional portion of the original pressure wave energy is utilized for supporting the charge changing.
  • the total cross-sectional surface of the parallel pipes is at least 25% larger than the free flow cross-section of the joint pipe, preferably between 40% and 60% larger. This refers to the surface of the joint pipe that precedes the parallel pipes or channels at its junction with the branch.
  • the length of the parallel pipes between the branch and the joining element should advantageously be equal to at least twice the respective diameter of said pipes so as to ensure that separate and independent wave fronts are able to develop in the parallel channels and that the original wave is not merely briefly spread open.
  • One advantage of the proposed arrangement is that the total length of the parallel pipe sections is irrelevant for the function as the travel times of the individual reflection waves within the arrangement are uncoupled from the ignition frequency of the engine because of the multiple wave reflections induced between the components of the invention.
  • the wave impedance is configured as a metal sheet provided with holes or slots.
  • the wave impedance is configured as a perforated plate cylinder that is oriented substantially parallel to the axis whose side facing the parallel pipes is sealed, while the other side facing the components of the exhaust system installed downstream, especially the muffler, is open.
  • the wave impedance can be increased with a given hole diameter provided that the holes or slots have a non-negligible longitudinal dimension or that they are axially extended by means of short pipe sections or protuberances in the metal sheet. This easily allows producing the desired wave impedance with easily achieved hole sizes.
  • the wave impedance can also be a catalytic converter body having honeycombed pits, for example, with which the required noise and exhaust gas emission limits can easily be met with a very small structural size while optimally and evenly increasing the output, even in motorcycles.
  • the wave impedance is a porous metal or ceramic body, preferably made of sintered material.
  • the wave impedance could also be an easily produced knit or woven device of metal filaments.
  • the total cross-section of the through-openings in the wave impedance component is larger than the total cross-section of the parallel pipes the flow resistance is not or only slightly higher than that of the preceding exhaust system, thereby preventing an adverse effect on the performance of the engine.
  • the total cross-section of the through-openings is between approx. 30% and 40% larger than the total cross-section of the pipes.
  • the wave impedance is advantageously disposed directly behind the joining element with the distance to its end being max. about twice the local pipe diameter.
  • At least two branches and at least two joining elements can be provided parallel relative to each other where the pipes of each branch lead to different joining elements.
  • FIG. 1 shows a first embodiment of the invention for four-cylinder engines.
  • FIG. 2 illustrates another variant for four-cylinder engines.
  • FIG. 3 and the profile A-A illustrate a special embodiment of the parallel pipes.
  • FIG. 4 illustrates another embodiment of the exhaust system of the invention having two branches, two parallel pipe arrangements and two wave impedance components.
  • the commonly configured primary outlet pipes 1 to 4 of the individual cylinders of a four-cylinder engine are combined in pairs, as is also known and common, into two secondary continuing exhaust gas pipes 5 and 6 .
  • a similar arrangement is also standard for six-cylinder engines where groups of three primary outlet pipes are combined into one secondary continuing pipe.
  • the secondary exhaust gas pipes 5 , 6 can have a non-circular cross-section, if applicable, for example when they are structurally configured as two separated pipe halves as a result of dividing a single pipe.
  • the secondary exhaust gas pipes 5 , 6 associated with a group of primary outlet pipes are combined into a single collector pipe 7 in said known arrangement, which combines the exhaust gas flow of all cylinders and where devices such as mufflers or catalytic converters 14 are usually connected.
  • the latter can also be combined in one single component.
  • Similar arrangements are also common for eight- or twelve-cylinder engines where one series of cylinders is equipped with such an exhaust gas elbow.
  • Combining the primary exhaust gas pipes that are installed directly downstream of the individual cylinders into a joint continuing exhaust gas pipe is also common in two- or three-cylinder engines with the difference that based on the lower number of cylinders the primary outlet pipes run directly into the single collector pipe 7 that leads to a muffler or catalytic converter 14 .
  • a branch 8 is installed behind the collector or joint pipe 7 which divides the exhaust gas flow into at least two downstream parallel pipe sections 9 and 10 .
  • Said pipe sections 9 , 10 are subsequently recombined by means of the joining element 11 into a single collector pipe 12 in which a wave impedance 13 is installed.
  • the device 14 for example the muffler or catalytic converter, is connected to said collector pipe 12 containing the wave impedance 13 .
  • the wave impedance 13 is advantageously disposed concentrically in the collector pipe 12 .
  • the special effectiveness of the proposed arrangement is based on the following physical reasons: the nature of the propagation of a shock wave induced by opening an engine outlet, and the fundamental difference between partial and total reflection of said waves.
  • the shock waves induced in the rhythm of the operating cycle of a piston-type engine propagate at the local speed of sound in the exhaust gas as a transmission medium on the inside of the exhaust pipe in the direction of the exhaust opening. Said waves are individualized events strictly correlating with opening an engine outlet. Their nature corresponds to that of a shock wave caused by an explosion or a sonic boom as they too are the result of an abrupt introduction of pressure energy into the transmission medium spreading there as a singular pulse with one single prominent amplitude.
  • shock waves should not erroneously be mistaken for standing waves that develop on the inside of an exhaust system, because the singular wave fronts of shock waves can pass through each other without changing their pulse, similar to two different waves on the surface of a lake, while two different standing waves on the inside of the exhaust pipes overlay each other based on the resonance or interference mode, depending on the phase difference.
  • Such standing waves on the inside of the exhaust gas system are induced by said shock waves, but they differ from said shock waves similar to the cause differing from its effect.
  • EP 0 421 724 A1 specifies a pipe arrangement for attenuating standing waves by means of interference.
  • pipe lengths are required that considerably exceed the available space, especially in a motorcycle.
  • the arrangement with the branch 8 that divides the exhaust gas flow from the collector pipe 7 into two parallel continuing pipes 9 and 10 which are subsequently rejoined by means of a joining element 11 serves as a means for producing increased surfaces within the free flow cross-section in the exhaust gas pipe of the exhaust system. It is known that on such surface jumps as those on the branch 8 and the joining element 11 , a partial reflection of the shock wave takes place based on which its pulse is divided into two waves, one of which maintains the original propagation direction toward the end of the exhaust while the second wave is reflected in the opposite direction.
  • the following dimensioning rules define the lower limit of the geometric proportions in an exhaust system of the invention which are relevant for the efficiency of the partial wave reflection.
  • the minimum length of the parallel pipes 9 and 10 which should preferably be equal to at least twice the respective diameter of said pipes, ensures that a shock wave pulse, which is undivided before the branch 8 , is divided into two pulses whose total energy ideally, i.e., not taking into account unavoidable wall losses, is equal to that of the original pulse.
  • each of the partial waves propagating in the pipes 9 and 10 in the direction to the end of the exhaust is partially reflected on the increased surface represented by the free flow cross-section of said component relative to the individual surface of the pipes 9 and 10 .
  • the partial character of said reflection causes one part of the pulse energy of each partial wave to be reflected again as partial shock waves opposite to the original direction of the exhaust gas flow back to the branch 8 through the respective pipes, while the other part of the pulse energy propagates as partial shock waves in the original propagation direction.
  • the defined minimal surface of the pipes 9 and 10 ensures an adequately sized surface on the branch 8 where another and partial reflection is caused of the (partial) waves returning through said pipes.
  • This second partial reflection within the arrangement again generates two pairs of shock waves propagating in different directions, one pair in the direction to the engine and the other pair being the products of the second reflection having the orientation of the original pulse.
  • the partial wave reflection of one and the same shock wave on the joining element 11 and the branch 8 ties up a large proportion, ideally half, of the pulse energy of the original shock wave within the arrangement in that it is forced to perform alternating multiple reflections between the ends of the pipes 9 and 10 .
  • the Carnot pulse loss inevitably taking place in each of said parallel wave reflections causes the pulse energy to convert into heat and thus working off the original shock wave.
  • each individual shock wave generated by opening a cylinder outlet into multiple sub-waves that takes place in the proposed arrangement also effectively prevents any oscillation interference with the preceding primary elbows of the exhaust system on whose opening, as is known in the art, the shock waves generated at the ignition frequency of the engine experience an advantageous (partial) wave reflection optimizing the efficiency of the engine.
  • the reason for this is not only the above mentioned decrease in the pulse energy of the shock waves, which also reduces the activation of any residual standing waves, the reason is basically that the exponential splitting and dividing the original wave into multiple sub-waves is accompanied by a similar multiplication of the natural frequency of standing waves that are activated by said sub-waves.
  • FIG. 2 shows an arrangement of the invention where two exhaust mufflers 14 and 14 ′ are coupled to the joint pipe 7 at the branch 8 in that the branch 8 divides the exhaust gas flow into two pairs of parallel pipe sections 9 and 10 and 9 ′ and 10 ′ each having devices the 11 to 13 and 11 ′ to 13 ′ installed downstream.
  • FIG. 3 A structural alternative to two separate parallel pipes in the arrangement of the invention is illustrated in FIG. 3 and the profile A-A.
  • the exhaust gas parallel in the pipe sections 9 , 10 it is guided through only one pipe whose cross-sectional surface advantageously is equal to that of the collector pipe 12 and whose continuation it represents.
  • Said pipe is divided into two channels by means of a divider sheet 15 through which the exhaust gas has to flow.
  • the wave impedance 13 is placed at the end of said channels, preferably as described above, truly axial in the collector pipe 12 where the muffler or catalytic converter 14 is connected, again in the conventional manner.
  • the function of the branch 8 that divides the exhaust gas coming from the joint pipe 7 into the channels defined by the divider sheet 15 is preferably performed by a conical expansion member that widens the cross-section of the joint pipe 7 to the cross-section of the collector pipe 12 .
  • FIG. 4 shows an especially favorable embodiment of an arrangement of the invention where the two secondary exhaust pipes 5 and 6 that jointly transport the exhaust gas from a cylinder or a group of cylinders of an engine and between which a connection 15 may be provided are associated with a wave impedance 13 or 13 ′ with a downstream muffler 14 and 14 ′.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Health & Medical Sciences (AREA)
  • Toxicology (AREA)
  • Exhaust Silencers (AREA)
  • Exhaust Gas After Treatment (AREA)
  • Branch Pipes, Bends, And The Like (AREA)
US10/001,188 1999-05-03 2001-11-02 Manifold arrangement for exhaust systems Abandoned US20020083703A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ATA789/99 1999-05-03
AT78999 1999-05-03
PCT/AT2000/000115 WO2000066884A1 (de) 1999-05-03 2000-05-03 Sammelrohr-anordnung für auspuffanlagen

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2000/000115 Continuation WO2000066884A1 (de) 1999-05-03 2000-05-03 Sammelrohr-anordnung für auspuffanlagen

Publications (1)

Publication Number Publication Date
US20020083703A1 true US20020083703A1 (en) 2002-07-04

Family

ID=3499795

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/001,188 Abandoned US20020083703A1 (en) 1999-05-03 2001-11-02 Manifold arrangement for exhaust systems

Country Status (7)

Country Link
US (1) US20020083703A1 (de)
EP (1) EP1177368B1 (de)
JP (1) JP2002543336A (de)
AT (1) ATE264990T1 (de)
AU (1) AU4723200A (de)
DE (1) DE50006155D1 (de)
WO (1) WO2000066884A1 (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1612384A1 (de) * 2004-07-02 2006-01-04 Ford Global Technologies, LLC Schalldämpfervorrichtung
US20060053780A1 (en) * 2004-09-13 2006-03-16 Hiroyuki Kikuchi Motorcycle exhaust system
US20070137189A1 (en) * 2005-12-16 2007-06-21 Hiroyuki Kikuchi Vehicle exhaust apparatus and motorcycle equipped therewith
US20080229733A1 (en) * 2005-12-19 2008-09-25 Newburry Donald M Catalytic converter system and element for diesel engines
US20100022148A1 (en) * 2008-07-22 2010-01-28 Yamaha Hatsudoki Kabushiki Kaisha Exhaust device for outboard motor multi-cylinder engine
US20100251704A1 (en) * 2006-01-13 2010-10-07 Honda Motor Co., Ltd. Multiple-cylinder internal combustion engine having cylinder head provided with centralized exhaust passageway
US20110039461A1 (en) * 2005-12-12 2011-02-17 Brunswick Corporation Exhaust plenum for distributing exhaust gas uniformly through a catalyst module
US20110079005A1 (en) * 2009-10-01 2011-04-07 Albert Earl Hatchett Device & method for coverting a motorcycle exhaust system into a multiple exhaust system
US10598073B2 (en) * 2017-05-19 2020-03-24 Honda Motor Co., Ltd. Exhaust system of internal combustion engine
CN115875107A (zh) * 2023-03-03 2023-03-31 临沂临工重托机械有限公司 一种发动机的排气净化装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT4965U3 (de) * 2001-04-30 2002-06-25 Sinus Fahrzeugkomponenten Enwi Sammelrohr-anordnung für auspuffanlagen von brennkraftmaschinen
JP2007032541A (ja) * 2005-07-29 2007-02-08 Toyota Motor Corp 内燃機関の排気浄化システム
CN105626220A (zh) * 2016-01-30 2016-06-01 太仓丹妮尔模塑汽配有限公司 一种具有超强消音功能的汽车排气管

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53110617U (de) 1977-02-09 1978-09-04
US4953352A (en) * 1985-08-26 1990-09-04 Campbell Monty A Exhaust system
IT206464Z2 (it) 1986-02-27 1987-08-10 Alfa Romeo Spa Impianto di scarico per un motore a c.i..
DE3712495A1 (de) 1986-04-15 1987-10-22 Sebring Auspuff Schalldaempfer fuer die abgase von brennkraftmaschinen
DE3740238A1 (de) * 1986-12-04 1988-06-23 Audi Ag Abgasanlage fuer eine brennkraftmaschine mit zwei zylinderbaenken
DE3828599A1 (de) * 1988-08-23 1990-03-08 Bayerische Motoren Werke Ag Abgasanlage einer mehrzylindrigen brennkraftmaschine
US5033581A (en) 1989-10-02 1991-07-23 Feuling Engineering, Inc. Muffler for an internal combustion engine
AT3287U3 (de) * 1999-05-03 2000-03-27 Skorianz Christian Sammelrohr-anordnung für auspuffanlagen

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1612384A1 (de) * 2004-07-02 2006-01-04 Ford Global Technologies, LLC Schalldämpfervorrichtung
US20060053780A1 (en) * 2004-09-13 2006-03-16 Hiroyuki Kikuchi Motorcycle exhaust system
US7290388B2 (en) * 2004-09-13 2007-11-06 Kawasaki Jukogyo Kabushiki Kaisha Motorcycle exhaust system
US20110039461A1 (en) * 2005-12-12 2011-02-17 Brunswick Corporation Exhaust plenum for distributing exhaust gas uniformly through a catalyst module
US20070137189A1 (en) * 2005-12-16 2007-06-21 Hiroyuki Kikuchi Vehicle exhaust apparatus and motorcycle equipped therewith
US7458210B2 (en) * 2005-12-16 2008-12-02 Kawasaki Jukogyo Kabushiki Kaisha Vehicle exhaust apparatus and motorcycle equipped therewith
US20080229733A1 (en) * 2005-12-19 2008-09-25 Newburry Donald M Catalytic converter system and element for diesel engines
US8066950B2 (en) 2005-12-19 2011-11-29 Miratech Holdings, Llc Catalytic converter system and element for diesel engines
US7849683B2 (en) * 2006-01-13 2010-12-14 Honda Motor Co., Ltd Multiple-cylinder internal combustion engine having cylinder head provided with centralized exhaust passageway
US20100251704A1 (en) * 2006-01-13 2010-10-07 Honda Motor Co., Ltd. Multiple-cylinder internal combustion engine having cylinder head provided with centralized exhaust passageway
US20100022148A1 (en) * 2008-07-22 2010-01-28 Yamaha Hatsudoki Kabushiki Kaisha Exhaust device for outboard motor multi-cylinder engine
US8113893B2 (en) * 2008-07-22 2012-02-14 Yamaha Hatsudoki Kabushiki Kaisha Exhaust device for outboard motor multi-cylinder engine
US20110079005A1 (en) * 2009-10-01 2011-04-07 Albert Earl Hatchett Device & method for coverting a motorcycle exhaust system into a multiple exhaust system
US8359847B2 (en) 2009-10-01 2013-01-29 Albert Earl Hatchett Device and method for converting a motorcycle exhaust system into a multiple exhaust system
US10598073B2 (en) * 2017-05-19 2020-03-24 Honda Motor Co., Ltd. Exhaust system of internal combustion engine
CN115875107A (zh) * 2023-03-03 2023-03-31 临沂临工重托机械有限公司 一种发动机的排气净化装置

Also Published As

Publication number Publication date
AU4723200A (en) 2000-11-17
ATE264990T1 (de) 2004-05-15
EP1177368B1 (de) 2004-04-21
DE50006155D1 (de) 2004-05-27
JP2002543336A (ja) 2002-12-17
WO2000066884A1 (de) 2000-11-09
EP1177368A1 (de) 2002-02-06

Similar Documents

Publication Publication Date Title
US20020083703A1 (en) Manifold arrangement for exhaust systems
US5726397A (en) Vehicle exhaust device
US4467887A (en) Exhaust mufflers for internal combustion engines
US2520756A (en) Exhaust silencer for internalcombustion engines
US3072214A (en) Gas blending and sound-attenuating system and apparatus
US3700069A (en) Wave interference silencer
JPH11336555A (ja) 往復動内燃機関
US4172508A (en) Exhaust silencers
US20200173320A1 (en) Acoustic volume in hot-end of exhaust systems
US20070272479A1 (en) Exhaust System for an Internal Combustion Engine
US2960179A (en) Exhaust muffler
US6052990A (en) Exhaust pipe and method and system for enhancing engine performance
KR100347305B1 (ko) 디젤발전기용 연장관형 소음기
RU2460889C1 (ru) Глушитель шума выпуска отработавших газов двигателя внутреннего сгорания автотранспортного средства
US2069751A (en) Exhaust silencer
RU2099552C1 (ru) Способ выпуска потока отработавших газов двухтактного двигателя внутреннего сгорания и глушитель шума
US3082840A (en) Muffler
RU2187668C2 (ru) Многоцилиндровый двигатель внутреннего сгорания
RU2282730C2 (ru) Глушитель шума выпуска двигателя внутреннего сгорания
RU2196899C2 (ru) Четырехцилиндровый четырехтактный двигатель внутреннего сгорания
JPH0299711A (ja) 排気消音装置
JPH0693853A (ja) マフラー
RU15118U1 (ru) Система выхлопа энергетической установки
SU1638323A1 (ru) Глушитель шума выхлопа двигател внутреннего сгорани
RU2225518C2 (ru) Многоцилиндровый двигатель внутреннего сгорания (варианты)

Legal Events

Date Code Title Description
STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION