EP0791131B1 - Resonance exhaust silencer - Google Patents

Resonance exhaust silencer Download PDF

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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
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Prior art keywords
resonator
section
fact
muffler
housing
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EP95935283A
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German (de)
French (fr)
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EP0791131A1 (en
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Leopold Habsburg Lothringen
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/12—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).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Surgical Instruments (AREA)
  • Pipe Accessories (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Compressor (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)

Abstract

PCT No. PCT/AT95/00202 Sec. 371 Date Apr. 9, 1997 Sec. 102(e) Date Apr. 9, 1997 PCT Filed Oct. 13, 1995 PCT Pub. No. WO96/14496 PCT Pub. Date May 17, 1997A resonance muffler for two cycle internal combustion engines, with a rotationally symmetric resonator housing (1) into which an input pipe socket (8) is leading and which itself leads into an output pipe (4) containing a muffler, the resonator housing (1) defining consecutively in the direction of flow a diverging diffusor section (13), an optional intermediate section (14) of constant flow cross-section, as well as a converging reflector section (15), the output pipe (4) extending coaxially through the resonator housing (1) and the input pipe socket (8) leading tangentially into the diffusor section (13).

Description

Die Erfindung betrifft eine kombinierte Resonator- und Schalldämpferanlage für 2-Takt-Verbrennungskraftmaschinen, mit einem Resonator mit drehsymmetrischem Gehäuse, in das ein Einlaßstutzen mündet und das seinerseits in ein einen Schalldämpfer enthaltendes Auslaßrohr mündet, wobei das Resonatorgehäuse in Strömungsrichtung aufeinanderfolgend einen divergierenden Diffusorabschnitt, gegebenenfalls einen Zwischenabschnitt gleichbleibenden Strömungsquerschnittes, sowie einen konvergierenden Reflektorabschnitt begrenzt.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.

Die Theorie und Konstruktion leistungssteigernder Resonanz-Schalldämpferanlagen dieser Art sind z.B. im F. Laimböck, "Analyse der Steuerzeiten, Zeitquerschnitte und Auspuffanlagen neuzeitlicher Zweitakt-Zweiradmotoren", Tagungsbericht Grazer Zweiradtagung 7. November 1984, TU Graz, beschrieben. Die grundlegenden Merkmale von Resonatoranlagen sind ein genau definierter Diffusorabschnitt mit definierter Querschnittserweiterung, Diffusorsteigung und Länge im Verhältnis zur Gesamtresonatorlänge, gegebenenfalls ein Zwischenabschnitt gleichbleibenden Querschnittes (in der Regel 5 bis 15% der Gesamtlänge), und ein ebenfalls genau definierter Reflektorabschnitt, in der Regel ein Gegenkonus mit einer Länge von 15 bis 25% der Gesamtlänge.The theory and construction to increase performance 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.

Bei den bekannten Resonanz-Schalldämpfern mündet der Einlaßstutzen in axialer Richtung in den Diffusorabschnitt des Resonatorgehäuses, so daß dieses axial durchströmt wird, und an den Reflektorabschnitt schließt in axialer Richtung das Auslaßrohr mit dem Schalldämpfer als gesonderter Bauteil an. Auf Grund der einander gegenüberliegenden divergierenden und konvergierenden Abschnitte im Resonatorgehäuse bildet sich für jede eingespeiste Abgas-Druckwelle eine rücklaufende Unterdruckwelle aus, welche die Entleerung des Zylinders der Verbrennungskraftmaschine unterstützt und insgesamt zu einer besseren Verbrennung, Abgasreduktion und Leistungssteigerung führt. Der nachgeschaltete Schalldämpfer ist erforderlich, weil das Resonatorgehäuse selbst keine schalldämpfende Wirkung hat.In the known resonance silencers, 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. On Because of 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. Of the Downstream silencer is required because of the resonator housing itself has no sound absorbing effect.

Die Baulänge sowohl des Resonatorgehäuses als auch des anschließenden Schalldämpfers ist umgekehrt proportional zur Drehzahl der Verbrennungskraftmaschine. Speziell bei 2-Takt-Verbrennungskraftmaschinen mit kleinem Hubraum, z.B. für den Modellflugsport, für Motorsensen oder Kettensägen, wird aus Lärmschutzgründen zu immer niedrigeren Betriebsdrehzahlen gegriffen. Bei einer Betriebsdrehzahl von 6.000 U/min hat jedoch ein Resonanz-Schalldämpfer herkömmlicher Konstruktion eine Gesamt-Einbaulänge von über 1 m, was in den genannten Anwendungsfällen nicht tragbar ist. In diesen Fällen mußte bisher auf die Vorteile eines Resonanz-Schalldämpfers verzichtet werden, und es wurden Kompakt-Schalldämpfer eingesetzt, die keine Resonanzwirkung besitzen und daher unwirtschaftlich und umweltbelastend arbeiten. Einerseits verbleiben größere Mengen verbrannter Gase beim Spülprozeß im Zylinder, was die Verbrennung verschlechtert, anderseits gelangen größere Mengen unverbrannten Gemisches in das Abgas. Beide Effekte bewirken einen etwa 35 %-igen Leistungsabfall gegenüber einem Resonanz-Schalldämpfer.The overall length of both the resonator and the subsequent silencer is inversely proportional to Speed of the internal combustion engine. Especially with 2-stroke internal combustion engines with a small cubic capacity, e.g. for the Model flying, for brushcutters or chainsaws, is out Noise protection reasons resorted to ever lower operating speeds. At an operating speed of 6,000 rpm, however 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. On the one hand, large amounts of burnt remains Gases in the rinsing process in the cylinder, which is the combustion deteriorated, on the other hand, larger amounts of unburned Mixture in the exhaust gas. Both effects have an effect about 35% drop in performance compared to a resonance silencer.

Die Erfindung setzt sich zum Ziel, einen Resonanz-Schalldämpfer mit äußerst kompakten Abmessungen zu schaffen, so daß sich die Vorteile des Resonanzprinzipes auch bei kleinen 2-Takt-Verbrennungskraftmaschinen, wie Motoren für Flugmodelle, Rasenmäher, Kettensägen, Motorsensen etc., ausnützen lassen.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.

Dieses Ziel wird mit einem Resonanz-Schalldämpfer der einleitend genannten Art erreicht, der sich erfindungsgemäß dadurch auszeichnet, daß das Auslaßrohr das Resonatorgehäuse koaxial durchsetzt und der Einlaßstutzen tangential in den Diffusorabschnitt mündet.This goal is introduced with a resonance silencer mentioned type achieved by the invention is characterized in that the outlet tube coaxial with the resonator housing penetrates and the inlet port tangentially into the diffuser section flows.

Auf diese Weise wird eine zweifache Platzeinsparung erzielt. Einerseits wird der Schalldämpfer, welcher im Auslaßrohr angeordnet ist, zur Gänze in das Innere des Resonatorgehäuses verlagert, indem er gleichsam als Kern das Innere des Gehäuses durchsetzt. Anderseits wird die Baulänge des Resonators drastisch verkürzt, weil durch die tangentiale Anströmung die Abgase das Resonatorgehäuse wendelförmig um den Kern herum durchströmen, so daß der effektive Strömungsweg im Inneren des Resonatorgehäuses ein Vielfaches der Baulänge des Resonatorgehäuses beträgt. Die für das geschilderte Resonanzprinzip erforderliche anfängliche Vergrößerung des Strömungsquerschnittes und anschließende Verkleinerung des Strömungsquerschnittes ergibt sich dabei von selbst, weil sich die Ganghöhe der wendelförmigen Strömung durch die anfängliche Umlenkung von der tangentialen Einspeisung zur wendelförmigen Durchströmung fortschreitend erhöht, was einem divergierenden Abschnitt entspricht, und beim Auflaufen der wendelförmigen Strömung auf das andere Ende des Resonatorgehäuses wieder verringert, was einem konvergierenden Abschnitt entspricht.In this way, a double saving of space is achieved. On the one hand, 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. On the other hand, 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 one for the described Resonance principle required initial increase of Flow cross section and subsequent reduction of the Flow cross-section arises automatically because the pitch of the helical flow through the initial Redirection from tangential infeed to helical Flow increases progressively, causing a divergent Section corresponds, and when emerging the helical Flow to the other end of the resonator housing again decreased, which corresponds to a converging section.

Zweckmäßigerweise kann unterstützend der Diffusorabschnitt durch eine kontinuierliche Vergrößerung des Durchmessers des Resonatorgehäuses und/oder der Reflektorabschnitt durch eine kontinuierliche Verringerung des Durchmessers des Resonatorgehäuses in seiner Wirkung verstärkt werden. Gemäß einer besonders bevorzugten Ausführungsform der Erfindung wird jedoch alternativ oder zusätzlich zwischen Auslaßrohr und Resonatorgehäuse eine wendelförmige Leitwand angeordnet. Die Ganghöhe der wendelförmigen Leitwand kann beispielsweise konstant gehalten werden, und der Diffusorabschnitt und der Reflektorabschnitt werden lediglich über die geschilderten Durchmesseränderungen des Resonatorgehäuses erreicht. Besonders vorteilhaft ist es aber, wenn die Ganghöhe der wendelförmigen Leitwand entsprechend variiert wird, und bevorzugt der Diffusorabschnitt durch eine kontinuierliche oder - zwecks Fertigungsvereinfachung - stufenweise Vergrößerung der Ganghöhe der wendelförmigen Leiterwand gebildet wird. Nach dem gleichen Prinzip kann bevorzugt der Reflektorabschnitt durch das Auflaufen der wendelförmigen Leitwand auf eine radiale Stirnwand des Resonatorgehäuses gebildet werden.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. According to a particularly preferred embodiment of the invention however, alternatively or additionally between the outlet pipe and Resonator housing arranged a helical baffle. The 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. Especially However, it is advantageous if 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. After the same In principle, the reflector section can preferably by the The helical guide wall runs onto a radial one End wall of the resonator housing are formed.

An dieser Stelle sei erwähnt, daß aus der US-PS 4 683 978 die Verwendung eines wendelförmigen Leitbleches in einem Schalldämpfer an sich bekannt ist. Das dort beschriebene Leitblech besitzt eine konstante Ganghöhe und wird ausschließlich zur Schalldämmung und nicht zur Bildung der Diffusor- und Reflektorabschnitte des Resonatorgehäuses eines Resonanz-Schalldämpfers verwendet. Ferner ist auch aus der CH 199 018 eine wendelförmige Leitwand variabler Ganghöhe zwischen einem Auslaßrohr und einem Außengehäuse bekannt, allerdings für einen gänzlich anderen Zweck, und zwar für einen Nur-Schalldämpfer ohne Resonatorabschnitt, d.h. nicht für einen kombinierten Resonanz-Schalldämpfer, welcher eine leistungssteigernde Resonanzanlage aus Diffusorabschnitt, gegebenenfalls Zwischenabschnitt und Reflektorabschnitt aufweist. Im einzelnen bildet bei der CH 199 018 die wendelförmige Leitwand eine wendelförmige akustische Schalldämpfungskammer, zu welcher sich das Auslaßrohr über eine Vielzahl mit variabler Schrittweite angeordneter Auslaßöffnungen hin öffnet. Die wendelförmige Kammer ist in diesem Fall dem Auslaßrohr parallel geschaltet und die variable Ganghöhe dient zur Bildung variabler Elementar-Schalldämpfungskammern, um einen ganzen Bereich von Schallfrequenzen absorbieren bzw. kompensieren zu können.At this point it should be mentioned that from US Pat. No. 4,683,978 the use of a helical baffle in one Silencer is known per se. The baffle described there has a constant pitch and is exclusive for sound insulation and not for the formation of the diffuser and reflector sections of the resonator housing of a resonance silencer used. Furthermore, there is also one from CH 199 018 helical guide wall of variable pitch between an outlet pipe and an outer housing, but for one completely different purpose, for a silencer only without resonator section, i.e. not for a combined one Resonance silencer, which is a performance-enhancing resonance system from diffuser section, possibly intermediate section and has reflector section. In particular forms in the CH 199 018 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.

In jedem Fall besteht eine weitere vorteilhafte Ausführungsform der Erfindung darin, daß der Einlaßstutzen unter einem spitzen Winkel zu der Längsachse des Resonatorgehäuses in dieses mündet, was einen gleitenden Übergang in die wendelförmige Strömung ermöglicht.In any case, there is a further advantageous embodiment the invention in that 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.

Eine konstruktiv besonders vorteilhafte Lösung zeichnet sich dadurch aus, daß das Auslaßrohr über radiale Öffnungen mit dem Reflektorabschnitt in Verbindung steht. Das Ende des Auslaßrohres kann in diesem Bereich an der Stirnwand des Resonatorgehäuses befestigt werden, und die Strömungsverbindung erfolgt über die genannten radialen Öffnungen.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.

Zur Ausbildung des Schalldämpfers im Auslaßrohr wird bevorzugt in das Auslaßrohr ein Endrohr koaxial eingesetzt, welches die reflektorseitige Stirnwand des Resonatorgehäuses durchsetzt und in einem Abstand von der diffusorseitigen Stirnwand des Resonatorgehäuses endet. In diesem Fall ist es besonders günstig, wenn gemäß einem weiteren Merkmal der Erfindung die Innenseite des Auslaßrohres und die Außenseite des Endrohres mit einem schalldämmenden Belag versehen werden.It is preferred to form the muffler in the exhaust pipe in the outlet pipe, 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. In this case it is special favorable if according to a further feature of the invention the inside of the outlet pipe and the outside of the tail pipe be provided with a sound-absorbing covering.

Ferner kann in jedem Fall im Inneren des Auslaßrohres ein Abgas-Katalysator angeordnet werden, ohne die Einbaulänge des Resonanz-Schalldämpfers zu vergrößern.Furthermore, one can in any case inside the outlet pipe Exhaust gas catalytic converter can be arranged without the installation length of the Enlarge resonance silencer.

Schließlich ist es besonders vorteilhaft, wenn der Einlaßstutzen als direkt an die Zylinderauslaßöffnung der Verbrennungskraftmaschine anflanschbarer Rohrkrümmer ausgebildet ist. Dadurch läßt sich der Resonanz-Schalldämpfer in einfacher Weise gegen herkömmliche Kompakt-Schalldämpfer austauschen.Finally, it is particularly advantageous if the inlet connection than directly to the cylinder exhaust port of the internal combustion engine flange pipe elbow is formed. This allows the resonance muffler to be used in a simple manner replace with conventional compact silencers.

Die Erfindung wird nachstehend an Hand von in den Zeichnungen dargestellten Ausführungsbeispielen näher erläutert. In den Zeichnungen zeigt

  • Fig. 1 eine erste Ausführungsform des Resonanz-Schalldämpfers der Erfindung im Längsschnitt,
  • Fig. 2 in der Stirnansicht und
  • Fig. 3 in der Draufsicht,
  • die Fig. 4 bis 6 Längsschnitte durch drei weitere Ausführungsformen von erfindungsgemäßen Resonanz-Schalldämpfern, und
  • die Fig. 7 und 8 eine weitere alternative Ausführungsform des Resonanz-Schalldämpfers der Erfindung in der Stirnansicht bzw. im Längsschnitt.
    • The invention is explained in more detail below on the basis of exemplary embodiments illustrated in the drawings. In the drawings shows
  • 1 shows a first embodiment of the resonance muffler of the invention in longitudinal section,
  • Fig. 2 in front view
  • 3 in plan view,
  • 4 to 6 are longitudinal sections through three further embodiments of resonance mufflers according to the invention, and
  • 7 and 8 a further alternative embodiment of the resonance silencer of the invention in the front view and in longitudinal section.

    • Der in den Fig. 1 bis 3 dargestellte Resonanz-Schalldämpfer weist ein zylinderförmiges Resonatorgehäuse 1 auf, das auf einer Seite durch eine kuppelförmige Stirnwand 2 und auf der anderen Seite durch eine radiale Stirnwand 3 abgeschlossen ist. Im Inneren des Resonatorgehäuses 1 erstreckt sich ein Auslaßrohr 4 koaxial von der Stirnwand 2 bis zur Stirnwand 3. Das Auslaßrohr 4 ist in der Nähe der Stirnwand 3 mit radialen Öffnungen 5 versehen. Am gegenüberliegenden Ende kann das Auslaßrohr 4 die Stirnwand 2 zur Bildung eines Auspuffs direkt durchsetzen, bevorzugt wird jedoch - wie bei der dargestellten Ausführungsform - zur Ausbildung eines Schalldämpfers im Inneren des Auslaßrohres 4 eine weitere Strömungsumlenkung geschaffen, indem ein Endrohr 6 koaxial eingesetzt wird, welches die Stirnwand 3 zur Bildung eines Auspuffs durchsetzt und in einem Abstand von der Stirnwand 2 endet. Die Innenseite des Auslaßrohres 4 und die Außenseite des Endrohres 6 sind mit einem schalldämmenden Belag 7 versehen.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. At the opposite end it can 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.

    In der Nähe der Stirnwand 2 mündet in das Resonatorgehäuse 1 ein Einlaßstutzen 8, der an seinem freien Ende mit einem Flansch 9 zum direkten Anflanschen an die (nicht dargestellte) Zylinderauslaßöffnung einer 2-Takt-Verbrennungskraftmaschine ausgestattet ist. Der Einlaßstutzen 8 mündet tangential (siehe Fig. 2) und bevorzugt unter einem spitzen Winkel zur Längsachse des Resonatorgehäuses 1 (siehe Fig. 3) in den Ringraum zwischen Resonatorgehäuse 1 und Auslaßrohr 4. In diesem Ringraum ist eine wendelförmige Leitwand 10 (Fig. 1) angeordnet, die sich - in Strömungsrichtung vom Einlaßstutzen 8 bis zu den Öffnungen 5 des Auslaßrohres 4 gesehen - gegen den Uhrzeigersinn um das Auslaßrohr 4 windet. Der Einlaßstutzen 8 mündet direkt in den ersten Gewindegang 11. Zwischen diesem und der Stirnwand 2 befindet sich ein unbenützter Totraum 12. An dem den Öffnungen 5 des Auslaßrohres 4 zugewandten Ende läuft die Leitwand 10 unter einem Winkel auf die Stirnwand 3 auf.Near the end wall 2 opens into the resonator housing 1 an inlet connector 8, which is at its free end with a Flange 9 for direct flange mounting on the (not shown) Cylinder outlet opening of a 2-stroke internal combustion engine Is provided. 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. In this annulus 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.

    Die Ganghöhe h der wendelförmigen Leitwand 10 erhöht sich in einem ersten Axialabschnitt 13 kontinuierlich vom Einlaßstutzen 8 weg, bleibt in einem zweiten Axialabschnitt 14 konstant und verringert sich in einem dritten Axialabschnitt 15 zwangsläufig durch das Auflaufen auf die Stirnwand 3. Dadurch erweitert sich der wirksame Strömungsquerschnitt kontinuierlich im Abschnitt 13, bleibt im Abschnitt 14 konstant und verringert sich wieder im Abschnitt 15. Die Abschnitte 13 bis 15 entsprechen daher dem Diffusorabschnitt, Zwischenabschnitt und Reflektorabschnitt herkömmlicher Resonanz-Schalldämpfer mit axialer Durchströmung, benötigen aber wesentlich weniger Einbaulänge, weil sie wendelförmig um das Auslaßrohr gewickelt sind.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.

    Alternativ kann der Abschnitt 14 entfallen und/oder die Ganghöhe h im Abschnitt 15 bereits vor dem Auflaufen auf die Stirnwand allmählich verringert werden. Unterstützend kann im Abschnitt 13 zusätzlich der Außendurchmesser D des Resonatorgehäuses fortschreitend erhöht werden, wie es in der Ausführungsform der Fig. 4 dargestellt ist, und/oder im Abschnitt 15 fortschreitend verringert werden. Allgemein gesprochen stehen zwei Parameter zur Beeinflussung des Strömungsquerschnittes in den Abschnitten 13, 14 und 15 zur Verfügung, u.zw. die Ganghöhe h und der Durchmesser D.Alternatively, 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. Generally speaking, there 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.

    Als weitere Alternative kann anstelle einer kontinuierlichen Vergrößerung der Ganghöhe h im Abschnitt 13 eine stufenweise Vergrößerung der Ganghöhe h vorgesehen werden, was Vereinfachungen in der Fertigung bringt. Im einfachsten Fall wird der Diffusorabschnitt nur durch den Übergang von einem ersten (kurzen) Abschnitt mit einer konstanten, kleinen Ganghöhe h1 zu einem zweiten Abschnitt mit einer großen Ganghöhe h2 gebildet (nicht dargestellt), und zwar entsteht der Diffusorabschnitt hier im Verlauf einer Wendelumdrehung im Bereich der Übergangsstufe. Der erste (kurze) Abschnitt vor dem stufenweisen Übergang (dem Diffusorabschnitt) kann in diesem Fall als bloße Verlängerung des tangential einmündenden Einlaßstutzens angesehen und somit zu diesem gezählt werden.As a further alternative, instead of a continuous increase in the pitch h in section 13, a gradual increase in the pitch h can be provided, which simplifies production. In the simplest case, 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. In this case, the first (short) section before the gradual transition (the diffuser section) can be regarded as a mere extension of the tangentially opening inlet connector and can therefore be counted among them.

    Fig. 5 zeigt eine Ausführungsform für den vertikalen Einbau, beispielsweise unterhalb des Motors einer Motorsense, mit kurzer Baulänge und großem Außendurchmesser. Bei der Ausführungsform der Fig. 6, bei welcher der Ringraum zwischen Auslaßrohr 4 und Resonatorgehäuse 1 in der Zeichnung von rechts nach links durchströmt wird, wird auf die zweifache Umlenkung im Inneren des Auslaßrohres 4 verzichtet, so daß Raum für den Einbau eines herkömmlichen Katalysators 16 im Auslaßrohr 4 zwischen den Öffnungen 5 und dem Endrohr 6 geschaffen wird.5 shows an embodiment for vertical installation, for example below the engine of a brushcutter short overall length and large outside diameter. In the embodiment 6, in which 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.

    In den Fig. 7 und 8 ist eine alternative Ausführungsform speziell für hochdrehende Motoren dargestellt, für welche auf die ausdrückliche Anordnung einer Leitwand 10 verzichtet werden kann, wobei das Funktionsprinzip aber unverändert bleibt. Durch die tangentiale Anordnung des Einlaßstutzens 8 und die koaxiale, das Resonatorgehäuse 1 durchsetzende Anordnung des Auslaßrohres 4 stellt sich zwangsläufig eine wendelförmige Strömung der Abgase um das Auslaßrohr 4 in Richtung auf die Öffnungen 5 ein. Die Erweiterung des Strömungsquerschnittes im Abschnitt 13 und die Verringerung im Abschnitt 15 wird durch eine entsprechende Erweiterung bzw. Verringerung des Außendurchmessers D des Resonatorgehäuses unterstützt. Es ist aber zu beachten, daß diese Maßnahme nur unterstützend und nicht zwingend ist, weil sich durch die allmähliche Umlenkung der im wesentlichen kreisförmigen Strömung im Einspeisebereich des Einlaßstutzens 8 zu der im wesentlichen wendelförmigen Strömung im Zwischenabschnitt 14 von selbst eine Vergrößerung des effektiven Strömungsquerschnittes im Abschnitt 13 ergibt, und umgekehrt im Bereich des Auflaufens der wendelförmigen Strömung auf die Stirnwand 3 eine entsprechende Verringerung. Wird auf die Außendurchmesserveränderung verzichtet, beträgt der Resonanz) effekt immer noch ca. 65%, wenn der Resonanzeffekt der optimalen Bauform mit 100% angesetzt wird.7 and 8 is an alternative embodiment shown especially for high-revving engines, for which on the express arrangement of a guide wall 10 can be dispensed with can, but the principle of operation remains unchanged. By the tangential arrangement of the inlet connector 8 and the coaxial, the resonator housing 1 penetrating arrangement of the outlet tube 4 inevitably arises a helical flow the exhaust gases around the outlet pipe 4 in the direction of the openings 5 a. The expansion of the flow cross section in section 13 and the reduction in section 15 is due to a corresponding one Expansion or reduction of the outer diameter D of the resonator housing supported. However, it should be noted that this measure is only supportive and not mandatory because itself by the gradual redirection of the essentially circular Flow in the feed area of the inlet port 8 to the essentially helical flow in the intermediate section 14 by itself an increase in the effective flow cross-section in section 13, and vice versa in Area of helical flow impingement on the End wall 3 a corresponding reduction. Will on the Waived outside diameter change, the resonance) effect still approx. 65% if the resonance effect is the optimal Design with 100%.

    Diese Ausführungsform ohne wendelförmige Leitwand 10 eignet sich vor allem für 2-Takt-Motoren mit Umdrehungszahlen von 15.000 bis 30.000 U/min, wogegen für geringere Drehzahlen die Ausführungsform mit Leitwand vorzuziehen ist.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.

    Bei einer gegebenen Betriebsdrehzahl kann mit der vorgestellten Konstruktion die Einbaulänge eines Resonanz-Schalldämpfers auf mindestens 1/3 bis ca. 1/10 der Länge herkömmlicher Resonanz-Schalldämpfer mit axialer Durchströmung reduziert werden (siehe z.B. Fig. 5).At a given operating speed, 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).

    Claims (11)

    1. A combined resonator and muffler equipment for two cycle internal combustion engines, having a resonator with a rotationally symmetrical housing (1) with an input pipe socket (8) leading into it and which is itself leading into an output pipe (4) containing a muffler, the resonator housing (1) defining consecutively, in the direction of flow, a diverging diffusor section (13), an optional intermediate section (14) as well as a converging reflector section (15), characterized by the fact that the output pipe (4) extends coaxially through the resonator housing (1) and that the input pipe socket (8) leads tangentially into the diffusor section (13).
    2. The combined resonator and muffler equipment of claim 1, characterized by the fact that a helical guide wall (10) extending from the input pipe socket (8) to the head of the output pipe (4) is arranged within the annular chamber formed between the resonator housing (1) and the output pipe (4) coaxially arranged therein.
    3. The combined resonator and muffler equipment of claim 2, characterized by the fact that the diffusor section (13) is formed by a continuous increase of the pitch (h) of the helical guide wall (10).
    4. The combined resonator and muffler equipment of claim 2 or 3, characterized by the fact that the reflector section (15) is formed by the engagement of the helical guide wall (10) with a radial end wall (3) of the resonator housing (1).
    5. The combined resonator and muffler equipment of one of claims 1 to 4, characterized by the fact that the input pipe socket (8) leads into the resonator housing (1) at an acute angle to the longitudinal axis thereof.
    6. The combined resonator and muffler equipment of one of claims 1 to 5, characterized by the fact that the output pipe (4) is connected to the reflector section (15) by radial openings (5).
    7. The combined resonator and muffler equipment of one of claims 1 to 6, characterized by the fact that into the output pipe (4) there is coaxially inserted an end pipe (6) extending through an end wall (3) of the resonator housing (1) and ending at a distance from the opposite end wall (2) of the resonator housing (1).
    8. The combined resonator and muffler equipment of claim 7, characterized by the fact that the inner surface of the output pipe (4) and the outer surface of the end pipe (6) are provided with a sound dampening coating (7).
    9. The combined resonator and muffler equipment of one of claims 1 to 8, characterized by the fact that an emission gas catalytic converter (16) is arranged within the interior of the output pipe (4).
    10. The combined resonator and muffler equipment of one of claims 1 to 9, characterized by the fact that the input pipe socket (8) is formed as a pipe manifold for direct flanged connection to the output opening of a cylinder of the internal combustion engine.
    11. The combined resonator and muffler equipment of claim 2, characterized by the fact that the diffusor section is formed by a step-wise increase of the pitch (h1-h2) of the helical guide wall (10).
    EP95935283A 1994-11-08 1995-10-13 Resonance exhaust silencer Expired - Lifetime EP0791131B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    AT2068/94 1994-11-08
    AT0206894A AT407772B (en) 1994-11-08 1994-11-08 COMBINED RESONATOR AND MUFFLER SYSTEM
    PCT/AT1995/000202 WO1996014497A1 (en) 1994-11-08 1995-10-13 Resonance exhaust silencer

    Publications (2)

    Publication Number Publication Date
    EP0791131A1 EP0791131A1 (en) 1997-08-27
    EP0791131B1 true EP0791131B1 (en) 1998-08-26

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    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP95935283A Expired - Lifetime EP0791131B1 (en) 1994-11-08 1995-10-13 Resonance exhaust silencer

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    US (1) US5844178A (en)
    EP (1) EP0791131B1 (en)
    JP (1) JPH10508356A (en)
    CN (1) CN1078927C (en)
    AT (2) AT407772B (en)
    AU (1) AU3736495A (en)
    CA (1) CA2204611C (en)
    DE (1) DE59503380D1 (en)
    ES (1) ES2120236T3 (en)
    WO (1) WO1996014497A1 (en)

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    Also Published As

    Publication number Publication date
    US5844178A (en) 1998-12-01
    CA2204611A1 (en) 1996-05-17
    ES2120236T3 (en) 1998-10-16
    EP0791131A1 (en) 1997-08-27
    ATE170260T1 (en) 1998-09-15
    CN1078927C (en) 2002-02-06
    CA2204611C (en) 2005-08-23
    AU3736495A (en) 1996-05-31
    AT407772B (en) 2001-06-25
    JPH10508356A (en) 1998-08-18
    WO1996014497A1 (en) 1996-05-17
    DE59503380D1 (en) 1998-10-01
    CN1163652A (en) 1997-10-29
    ATA206894A (en) 2000-10-15

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