EP0791131B1 - Resonanz-schalldämpfer - Google Patents
Resonanz-schalldämpfer Download PDFInfo
- Publication number
- EP0791131B1 EP0791131B1 EP95935283A EP95935283A EP0791131B1 EP 0791131 B1 EP0791131 B1 EP 0791131B1 EP 95935283 A EP95935283 A EP 95935283A EP 95935283 A EP95935283 A EP 95935283A EP 0791131 B1 EP0791131 B1 EP 0791131B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- resonator
- section
- fact
- muffler
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N1/00—Silencing apparatus characterised by method of silencing
- F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
- F01N1/12—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using spirally or helically shaped channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/34—Ultra-small engines, e.g. for driving models
Definitions
- the invention relates to a combined resonator and Silencer system for 2-stroke internal combustion engines, with a resonator with a rotationally symmetrical housing, into which an inlet connection flows into a silencer containing outlet pipe opens, the resonator housing a diverging one after the other in the direction of flow Diffuser section, optionally an intermediate section constant flow cross-section, as well as a converging reflector section limited.
- Resonance silencer systems of this type are e.g. in the F. Laimböck, "Analysis of tax times, time cross sections and Exhaust systems of modern two-stroke two-wheel engines ", conference report Graz two-wheel conference November 7, 1984, Graz University of Technology.
- the basic characteristics of resonator systems are a precisely defined diffuser section with a defined cross-sectional expansion, Diffuser slope and length in relation to the total resonator length, if necessary an intermediate section constant cross-section (usually 5 to 15% of the total length), and a precisely defined reflector section, usually a counter cone with a length of 15 to 25% of the total length.
- the inlet port opens in the axial direction into the diffuser section of the resonator housing, so that it flows axially, and on the outlet section closes the reflector section in the axial direction with the silencer as a separate component.
- the opposing diverging and converging Sections in the resonator housing are formed for each injected exhaust gas pressure wave a returning vacuum wave from which the emptying of the cylinder of the internal combustion engine supported and overall better Combustion, exhaust gas reduction and performance increase leads.
- the Downstream silencer is required because of the resonator housing itself has no sound absorbing effect.
- the overall length of both the resonator and the subsequent silencer is inversely proportional to Speed of the internal combustion engine.
- 2-stroke internal combustion engines with a small cubic capacity e.g. for the Model flying, for brushcutters or chainsaws
- Noise protection reasons resorted to ever lower operating speeds.
- a resonance silencer of conventional construction has an overall installation length of over 1 m, what in the mentioned applications is not portable. In these cases, so far the advantages of a resonance silencer are dispensed with, and compact silencers were used, which none Have resonance effect and therefore uneconomical and polluting work.
- the aim of the invention is a resonance silencer with extremely compact dimensions, so that the advantages of the principle of resonance also small 2-stroke internal combustion engines, such as engines for Aircraft models, lawn mowers, chainsaws, brushcutters etc., let take advantage.
- the silencer which is in the outlet pipe is arranged entirely in the interior of the resonator housing relocated, as it were, as the core of the interior of the housing enforced.
- the overall length of the resonator drastically shortened because of the tangential flow Exhaust the resonator housing helically around the core flow through so that the effective flow path inside the Resonator housing a multiple of the overall length of the Resonator housing is.
- the diffuser section can expediently provide support by continuously increasing the diameter of the Resonator housing and / or the reflector section by a continuous reduction in the diameter of the Resonator housing can be reinforced in its effect.
- the pitch of the helical guide wall can be, for example are kept constant, and the diffuser section and the Reflector sections are only described above Diameter changes of the resonator housing reached.
- the pitch of the helical Guide wall is varied accordingly, and preferably the Diffuser section through a continuous or - purpose Manufacturing simplification - gradual increase in pitch the helical conductor wall is formed.
- the reflector section can preferably by the The helical guide wall runs onto a radial one End wall of the resonator housing are formed.
- the helical guide wall is a helical one acoustic silencing chamber to which the outlet pipe arranged over a multitude with variable step size Exhaust openings opens.
- the helical chamber is in this case the outlet pipe connected in parallel and the variable pitch serves to form variable elementary silencing chambers, around a whole range of sound frequencies to be able to absorb or compensate.
- the inlet port under a acute angle to the longitudinal axis of the resonator housing in this leads to what is a smooth transition into the helical Flow allows.
- a particularly advantageous constructive solution is characterized in that the outlet pipe with radial openings communicates with the reflector section.
- the end of the outlet pipe can be in this area on the front wall of the resonator housing be attached, and the flow connection takes place via the radial openings mentioned.
- a tail pipe coaxially inserted which the reflector-side end wall of the resonator housing interspersed and at a distance from the diffuser end wall of the resonator housing ends.
- the inside of the outlet pipe and the outside of the tail pipe be provided with a sound-absorbing covering.
- Exhaust gas catalytic converter can be arranged without the installation length of the Enlarge resonance silencer.
- the resonance silencer shown in FIGS. 1 to 3 has a cylindrical resonator housing 1, the on one side through a dome-shaped front wall 2 and on completed on the other side by a radial end wall 3 is.
- An outlet pipe extends inside the resonator housing 1 4 coaxially from the front wall 2 to the front wall 3.
- Das Outlet pipe 4 is near the end wall 3 with radial Provide openings 5.
- Exhaust pipe 4 directly the end wall 2 to form an exhaust enforce, but is preferred - as in the illustrated Embodiment - to form a silencer inside the outlet pipe 4 created a further flow deflection, by using a tail pipe 6 coaxially, which the end wall 3 penetrates to form an exhaust and in a distance from the end wall 2 ends.
- the inside of the Outlet pipe 4 and the outside of the end pipe 6 are with provided a sound-absorbing covering 7.
- the inlet port 8 opens tangentially (see Fig. 2) and preferably at an acute angle to the longitudinal axis of the resonator housing 1 (see Fig. 3) in the annular space between Resonator housing 1 and outlet tube 4.
- a helical baffle 10 Fig. 1 arranged, the themselves - in the flow direction from the inlet port 8 to the Openings 5 of the outlet pipe 4 seen - counterclockwise winds around the outlet pipe 4.
- the inlet port 8 opens directly into the first thread 11. Between this and the End wall 2 is an unused dead space 12. At the the openings 5 of the outlet pipe 4 facing the end Guide wall 10 on the end wall 3 at an angle.
- the pitch h of the helical guide wall 10 increases in a first axial section 13 continuously from the inlet port 8 away, remains constant in a second axial section 14 and decreases in a third axial section 15 inevitably by running onto the front wall 3 the effective flow cross section expands continuously in section 13, remains constant and reduced in section 14 again in section 15.
- Sections 13 to 15 therefore correspond to the diffuser section, intermediate section and Reflector section with conventional resonance silencers axial flow, but require significantly less installation length, because they are helically wrapped around the outlet pipe are.
- section 14 can be omitted and / or Pitch h in section 15 even before it hits the End wall gradually reduced.
- Support can be given in Section 13 also the outer diameter D of the resonator housing be progressively increased as in the embodiment 4, and / or progressing in section 15 be reduced.
- the pitch h and the diameter D are two Parameters for influencing the flow cross section in the Sections 13, 14 and 15 available, etc. the pitch h and the diameter D.
- the diffuser section is formed only by the transition from a first (short) section with a constant, small pitch h 1 to a second section with a large pitch h 2 (not shown), and here the diffuser section arises in the course of a Helical revolution in the area of the transition stage.
- the first (short) section before the gradual transition can be regarded as a mere extension of the tangentially opening inlet connector and can therefore be counted among them.
- FIG. 5 shows an embodiment for vertical installation, for example below the engine of a brushcutter short overall length and large outside diameter.
- the annular space between the outlet pipe 4 and resonator housing 1 in the drawing from right to flows through on the left is based on the double deflection inside of the outlet pipe 4 is omitted, so that space for installation a conventional catalyst 16 in the outlet pipe 4 between the openings 5 and the tail pipe 6 is created.
- This embodiment without a helical guide wall 10 is particularly suitable for 2-stroke engines with revs from 15,000 to 30,000 rpm, whereas for lower speeds the embodiment with baffle is preferable.
- the presented can Construction the installation length of a resonance silencer more conventional at least 1/3 to about 1/10 of the length Resonance silencer with axial flow reduced (see e.g. Fig. 5).
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
- Pipe Accessories (AREA)
- Surgical Instruments (AREA)
- Characterised By The Charging Evacuation (AREA)
- Control Of Motors That Do Not Use Commutators (AREA)
- Reciprocating, Oscillating Or Vibrating Motors (AREA)
- Compressor (AREA)
Description
Claims (11)
- Kombinierte Resonator- und Schalldämpferanlage für 2-Takt-Verbrennungskraftmaschinen, mit einem Resonator mit drehsymmetrischem Gehäuse (1), in das ein Einlaßstutzen (8) mündet und das seinerseits in ein einen Schalldämpfer enthaltendes Auslaßrohr (4) mündet, wobei das Resonatorgehäuse (1) in Strömungsrichtung aufeinanderfolgend einen divergierenden Diffusorabschnitt (13), gegebenenfalls einen Zwischenabschnitt (14) gleichbleibenden Strömungsquerschnittes, sowie einen konvergierenden Reflektorabschnitt (15) begrenzt, dadurch gekennzeichnet, daß das Auslaßrohr (4) das Resonatorgehäuse (1) koaxial durchsetzt und der Einlaßstutzen (8) tangential in den Diffusorabschnitt (13) mündet.
- Kombinierte Resonator- und Schalldämpferanlage nach Anspruch 1, dadurch gekennzeichnet, daß in dem Ringraum, welcher durch die koaxiale Anordnung des Auslaßrohres (4) im Resonatorgehäuse (1) zwischen diesen ausgebildet ist, eine vom Einlaßstutzen (8) bis zum Anfang des Auslaßrohres (4) verlaufende wendelförmige Leitwand (10) angeordnet ist.
- Kombinierte Resonator- und Schalldämpferanlage nach Anspruch 2, dadurch gekennzeichnet, daß der Diffusorabschnitt (13) durch eine kontinuierliche Vergrößerung der Ganghöhe (h) der wendelförmigen Leitwand (10) gebildet ist.
- Kombinierte Resonator- und Schalldämpferanlage nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Reflektorabschnitt (15) durch das Auflaufen der wendelförmigen Leitwand (10) auf eine radiale Stirnwand (3) des Resonatorgehäuses (1) gebildet ist.
- Kombinierte Resonator- und Schalldämpferanlage nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Einlaßstutzen (8) unter einem spitzen Winkel zu der Längsachse des Resonatorgehäuses (1) in dieses mündet.
- Kombinierte Resonator- und Schalldämpferanlage nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Auslaßrohr (4) über radiale Öffnungen (5) mit dem Reflektorabschnitt (15) in Verbindung steht.
- Kombinierte Resonator- und Schalldämpferanlage nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß in das Auslaßrohr (4) ein Endrohr (6) koaxial eingesetzt ist, welches eine Stirnwand (3) des Resonatorgehäuses (1) durchsetzt und in einem Abstand von der gegenüberliegenden Stirnwand (2) des Resonatorgehäuses (1) endet.
- Kombinierte Resonator- und Schalldämpferanlage nach Anspruch 7, dadurch gekennzeichnet, daß die Innenseite des Auslaßrohres (4) und die Außenseite des Endrohres (6) mit einem schalldämmenden Belag (7) versehen sind.
- Kombinierte Resonator- und Schalldämpferanlage nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß im Inneren des Auslaßrohres (4) ein Abgas-Katalysator (16) angeordnet ist.
- Kombinierte Resonator- und Schalldämpferanlage nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß der Einlaßstutzen (8) als direkt an die Zylinderauslaßöffnung der Verbrennungskraftmaschine anflanschbarer Rohrkrümmer ausgebildet ist.
- Kombinierte Resonator- und Schalldämpferanlage nach Anspruch 2, dadurch gekennzeichnet, daß der Diffusorabschnitt durch eine stufenweise Vergrößerung der Ganghöhe (h1-h2) der wendelförmigen Leitwand (10) gebildet ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT2068/94 | 1994-11-08 | ||
AT0206894A AT407772B (de) | 1994-11-08 | 1994-11-08 | Kombinierte resonator- und schalldämpferanlage |
PCT/AT1995/000202 WO1996014497A1 (de) | 1994-11-08 | 1995-10-13 | Resonanz-schalldämpfer |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0791131A1 EP0791131A1 (de) | 1997-08-27 |
EP0791131B1 true EP0791131B1 (de) | 1998-08-26 |
Family
ID=3527094
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95935283A Expired - Lifetime EP0791131B1 (de) | 1994-11-08 | 1995-10-13 | Resonanz-schalldämpfer |
Country Status (10)
Country | Link |
---|---|
US (1) | US5844178A (de) |
EP (1) | EP0791131B1 (de) |
JP (1) | JPH10508356A (de) |
CN (1) | CN1078927C (de) |
AT (2) | AT407772B (de) |
AU (1) | AU3736495A (de) |
CA (1) | CA2204611C (de) |
DE (1) | DE59503380D1 (de) |
ES (1) | ES2120236T3 (de) |
WO (1) | WO1996014497A1 (de) |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001071169A1 (en) * | 2000-03-21 | 2001-09-27 | Silentor Holding A/S | A silencer containing one or more porous bodies |
AUPR982302A0 (en) | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A fluid flow controller |
AUPR982502A0 (en) | 2002-01-03 | 2002-01-31 | Pax Fluid Systems Inc. | A heat exchanger |
CN1612979B (zh) | 2002-01-03 | 2011-11-23 | 百思科技公司 | 涡环发生器 |
US6959782B2 (en) * | 2002-03-22 | 2005-11-01 | Tecumseh Products Company | Tuned exhaust system for small engines |
US6913112B2 (en) * | 2003-02-05 | 2005-07-05 | Arvin Technologies, Inc. | Noise attenuation assembly |
US20040245044A1 (en) * | 2003-04-18 | 2004-12-09 | Gabriella Cerrato-Jay | Tuned muffler for small internal combustion engines |
US6892853B2 (en) * | 2003-05-01 | 2005-05-17 | Agency For Science Technology And Research | High performance muffler |
AU2003903386A0 (en) | 2003-07-02 | 2003-07-17 | Pax Scientific, Inc | Fluid flow control device |
EA008030B1 (ru) | 2003-11-04 | 2007-02-27 | Пакс Сайентифик, Инк. | Устройство для циркуляции текучей среды |
KR20070012357A (ko) | 2004-01-30 | 2007-01-25 | 팍스 싸이언티픽 인코퍼레이션 | 원심 팬, 펌프 또는 터빈용 하우징 |
JP4586513B2 (ja) * | 2004-11-29 | 2010-11-24 | 日産自動車株式会社 | 消音器構造 |
US7472774B1 (en) * | 2006-01-27 | 2009-01-06 | Lockheed Martin Corporation | Versatile engine muffling system |
WO2008042251A2 (en) * | 2006-09-29 | 2008-04-10 | Pax Streamline, Inc. | Axial flow fan |
US7762374B2 (en) * | 2006-11-22 | 2010-07-27 | Honeywell International Inc. | Turbine engine diffusing exhaust muffler |
US7681690B2 (en) * | 2007-07-13 | 2010-03-23 | Longyear Tm, Inc. | Noise abatement device for a pneumatic tool |
JP4993755B2 (ja) * | 2008-03-18 | 2012-08-08 | 日産自動車株式会社 | 吸気音発生装置 |
US7735603B2 (en) * | 2008-05-28 | 2010-06-15 | Longyear Tm, Inc. | Noise reducing device for a pneumatic tool |
US8181671B2 (en) * | 2009-09-15 | 2012-05-22 | Butler Boyd L | Anti-resonant pulse diffuser |
US8215449B2 (en) * | 2009-12-02 | 2012-07-10 | Longyear Tm, Inc. | Muffler system for noise abatement and ice control |
US11187136B2 (en) * | 2017-12-19 | 2021-11-30 | The United States Of America As Represented By The Secretary Of The Army | Vorticity based noise abatement |
CN109204850B (zh) * | 2018-09-07 | 2020-11-06 | 观典防务技术股份有限公司 | 一种无人机发动机进行气流整流机构 |
US11867102B2 (en) * | 2019-08-28 | 2024-01-09 | Snap-On Incorporated | Pneumatic tool exhaust muffler |
CN113404579A (zh) * | 2020-11-18 | 2021-09-17 | 哈尔滨工业大学(威海) | 机动车复合排气*** |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1505893A (en) * | 1920-03-06 | 1924-08-19 | Hunter William | Silencer for internal-combustion engines |
GB345895A (en) * | 1930-06-23 | 1931-04-02 | Carl Axel Skaerlund | Improvements relating to silencers for internal combustion engines |
CH199018A (fr) * | 1934-07-19 | 1938-07-31 | Zygmunt Wilman | Silencieux spécialement pour moteurs à explosions et procédé pour sa fabrication. |
US2173550A (en) * | 1936-07-17 | 1939-09-19 | Coanda Henri | Exhaust of gases from engines |
US2494947A (en) * | 1946-11-16 | 1950-01-17 | Fairbanks Morse & Co | Engine manifold construction |
US3888331A (en) * | 1974-05-03 | 1975-06-10 | Gen Motors Corp | Power tuned wave interference silencer |
US3913703A (en) * | 1974-05-03 | 1975-10-21 | Gen Motors Corp | Single inner assembly wave interference silencer |
DE2519690A1 (de) * | 1974-05-03 | 1975-11-13 | Gen Motors Corp | Geraeuschdaempfer |
US3941206A (en) * | 1974-05-08 | 1976-03-02 | Burgess Industries Incorporated | Noise attenuating snubber |
JPS5236219A (en) * | 1975-09-13 | 1977-03-19 | Teruo Kashiwara | Exhaust equipment for internal combustion engine |
US4129196A (en) * | 1977-09-29 | 1978-12-12 | Everett Wilhelm S | Fluid acoustic silencer |
DE3246218A1 (de) * | 1982-12-14 | 1984-06-14 | Kaari, Kauko, Dipl.-Ing., 00270 Helsinki | Verfahren und vorrichtung zum verbessern des leistungsvermoegens und des wirkungsgrads eines verbrennungsmotors sowie zum verringern der von ihm bewirkten verschmutzungslast |
US4679597A (en) * | 1985-12-20 | 1987-07-14 | Kim Hotstart Mfg. Co., Inc. | Liquid pulsation dampening device |
US4792014A (en) * | 1987-12-24 | 1988-12-20 | Shin Seng Lin | Tail pipe for drafting engine exhaust gas |
FR2642470A1 (fr) * | 1989-01-27 | 1990-08-03 | Glaenzer Spicer Sa | Silencieux pour gaz d'echappement et partie de ligne d'echappement comportant un tel silencieux |
DE4020867C1 (en) * | 1990-06-29 | 1992-01-02 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | IC-engine exhaust housing - has exhaust guides sited between cleaner and housing wall |
-
1994
- 1994-11-08 AT AT0206894A patent/AT407772B/de not_active IP Right Cessation
-
1995
- 1995-10-13 AU AU37364/95A patent/AU3736495A/en not_active Abandoned
- 1995-10-13 AT AT95935283T patent/ATE170260T1/de not_active IP Right Cessation
- 1995-10-13 US US08/817,141 patent/US5844178A/en not_active Expired - Fee Related
- 1995-10-13 CA CA002204611A patent/CA2204611C/en not_active Expired - Fee Related
- 1995-10-13 ES ES95935283T patent/ES2120236T3/es not_active Expired - Lifetime
- 1995-10-13 DE DE59503380T patent/DE59503380D1/de not_active Expired - Fee Related
- 1995-10-13 WO PCT/AT1995/000202 patent/WO1996014497A1/de active IP Right Grant
- 1995-10-13 EP EP95935283A patent/EP0791131B1/de not_active Expired - Lifetime
- 1995-10-13 CN CN95196099A patent/CN1078927C/zh not_active Expired - Fee Related
- 1995-10-13 JP JP8514889A patent/JPH10508356A/ja not_active Ceased
Also Published As
Publication number | Publication date |
---|---|
US5844178A (en) | 1998-12-01 |
CA2204611A1 (en) | 1996-05-17 |
ES2120236T3 (es) | 1998-10-16 |
EP0791131A1 (de) | 1997-08-27 |
ATE170260T1 (de) | 1998-09-15 |
CN1078927C (zh) | 2002-02-06 |
CA2204611C (en) | 2005-08-23 |
AU3736495A (en) | 1996-05-31 |
AT407772B (de) | 2001-06-25 |
JPH10508356A (ja) | 1998-08-18 |
WO1996014497A1 (de) | 1996-05-17 |
DE59503380D1 (de) | 1998-10-01 |
CN1163652A (zh) | 1997-10-29 |
ATA206894A (de) | 2000-10-15 |
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