EP0100713B1 - Dichtungselement für eine Gaszyklus-Regelvorrichtung einer Brennkammer - Google Patents

Dichtungselement für eine Gaszyklus-Regelvorrichtung einer Brennkammer Download PDF

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Publication number
EP0100713B1
EP0100713B1 EP83401495A EP83401495A EP0100713B1 EP 0100713 B1 EP0100713 B1 EP 0100713B1 EP 83401495 A EP83401495 A EP 83401495A EP 83401495 A EP83401495 A EP 83401495A EP 0100713 B1 EP0100713 B1 EP 0100713B1
Authority
EP
European Patent Office
Prior art keywords
seal
combustion chamber
valve plug
plug
exhaust
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
Application number
EP83401495A
Other languages
English (en)
French (fr)
Other versions
EP0100713A1 (de
Inventor
Guy Negre
Jean-Claude Fayard
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.)
NEGRE, GUY
Elf Antar France
Original Assignee
Elf France SA
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
Priority claimed from FR8213072A external-priority patent/FR2531174A1/fr
Priority claimed from FR8213071A external-priority patent/FR2531139B1/fr
Application filed by Elf France SA filed Critical Elf France SA
Priority to AT83401495T priority Critical patent/ATE23603T1/de
Publication of EP0100713A1 publication Critical patent/EP0100713A1/de
Application granted granted Critical
Publication of EP0100713B1 publication Critical patent/EP0100713B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/16—Sealing or packing arrangements specially therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/12—Rotary or oscillatory slide valve-gear or valve arrangements specially for two-stroke engines
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention relates to a sealing member for a substantially cylindrical rotary plug crossed by at least one channel and to which an annular seal is applied with an axis transverse to the axis of rotation of the plug, in particular for sealing an exhaust port of a combustion chamber of an internal combustion engine and in which the annular seal is guided axially in a leaktight manner by its movable external surface in a bore and pressed against the plug by the pressure prevailing in the combustion chamber, the bore for guiding the seal having a slight taper, the point of which is directed towards the combustion chamber to permanently push the seal towards the plug and the contact zone between the plug and the seal being lubricated by a film of oil maintained despite the pressure of the gases from the combustion chamber passing through the plug.
  • Such a sealing member applies to a device for controlling a gas circuit, in particular for the evacuation of exhaust gases from a heat engine to control the exhaust of engines with rotary distribution such as internal combustion engines according to two or four stroke cycles, with spark or diesel ignition.
  • the orifice connected to the combustion chamber is arranged in a sealing ring housed in a bore and applied to the plug by the pressure prevailing in the combustion chamber and surrounded one or more sealing members such as segments, this ring being able to slide in the bore and its stroke being limited, on one side, by the rotor and, on the other side, by a retaining shoulder.
  • a metallic sealing ring of good rubbing quality makes it possible to seal the exhaust despite the high temperatures of the exhaust gases.
  • the sealing device is an integral part of the combustion chamber and is slidably mounted in a bore perpendicular to the distributor housing, thus achieving the intersection of two cylinders.
  • the seal of the device is pressed against the rotary distributor by the pressure prevailing in the chamber, which allows a clearance of operation between the rotary distributor and the annular seal.
  • the edges of the joint can form, at each end of the joint in contact with the plug, along a plane transverse to the axis of rotation of the plug, an end edge with an angle less than 90 °.
  • the end edge of the seal located on the side of the inlet in contact at the outlet of the channel formed in the plug with the annular seal, is provided with an inlet chamfer capable of forming an oil wedge which makes penetrate the oil film between the surfaces in contact with the plug and the annular seal.
  • the known devices have sealing difficulties at high operating temperatures or at cold start and high wear of the seals and the contact surfaces on the rotary distributor.
  • the annular seal has in its portion of smaller axial section an axial height close to the minimum height ensuring the pressure resistance of the combustion chamber prevailing inside the seal , so as to give it good elasticity to plating on the plug and to improve the behavior of the oil film.
  • the sealing member according to the invention for a substantially cylindrical rotary plug crossed by at least one channel and to which an annular seal is applied, with an axis transverse to the axis of rotation of the plug, in particular for sealing an exhaust port of a combustion chamber of an internal combustion engine and in which the annular seal is guided axially in a leaktight manner by its movable outer surface in a bore and pressed against the plug by the pressure prevailing in the combustion chamber, is remarkable in that the contact zone between the plug and the seal is lubricated by an oil film maintained despite the pressure of the gases (from the combustion chamber) passing through the bushel.
  • the outside diameter of the seal can be between 4/7 and 6/7 of the outside diameter of the plug to achieve a good compromise between the central passage section of the seal, the contact surface with the plug capable of improving the resistance of the film of oil and the curvature of the contact zones with the plug at the edges of the joint along a plane transverse to the axis of rotation of the plug, this curvature being able to reduce the resistance of the oil film.
  • the engine shown schematically in Figure 1 includes elements well known in engines operating according to the two-stroke cycle.
  • a crankcase 1 contains an engine cylinder 2 and is connected to a cylinder head 3, cooled by a circulation of liquid like the cylinder 2, to close a combustion chamber 4 into which opens a spark plug 5 or, in the case of diesel engines, a fuel injector.
  • the cylinder head 3 is shown in one piece with the engine crankcase 1, while in reality it is generally fixed by studs to the engine crankcase 1, while allowing the circulation of the coolant in a cooling circuit 6 common to the housing 1 and to the cylinder head 3.
  • a transfer chamber 7 which contains the crankshaft 8 of the engine connected to a connecting rod 9 and to the piston 10 movable in the cylinder 2.
  • This transfer chamber 7, of minimum volume compatible with the travel of the crankshaft 8 and of the connecting rod 9, are connected, on the one hand, to an inlet light 11 connected to a filtered air intake, direct in the case of a diesel engine and via a carburetor 12 in the case of a spark-ignition engine as shown in the figure and, on the other hand, transfer lights 13 which are more particularly visible in Figure 3 in the bottom dead center position of the piston 10.
  • the segments d seal 14 of the piston 10 reveal the openings 13 in the low position of the piston 10 to allow the admission of the carburetted gases, compressed in the transfer chamber 7, towards the combustion chamber 4.
  • a scraper and distributor segment placed on the piston of the side opposite to the piston head closing the combustion chamber 4 allows, from a relatively high position of the piston (substantially from 2/3 of the stroke of the piston towards top dead center) the gases sucked in s '' via the entry light 11 in the transfer chamber t 7 depression by the rise of the piston 10.
  • the engine exhaust circuit is controlled in the cylinder head 3 by a rotary valve 16 rotating in a chamber formed by a bore 17 with the walls of which it is not in contact although its external cylindrical surface is in the immediate vicinity of the bore wall.
  • This plug 16 is rotated by any means, such as a gear train or a chain or a toothed belt, at an angular speed half that of the crankshaft 8 of the engine and rotates around an axis 18 perpendicular to the cylinder axis 2.
  • the sealing of the ring 22 in the bore 23 is ensured by at least one segment 24 and the stroke of the ring 22 towards the combustion chamber 4 is limited by a retaining shoulder 25.
  • the sealing ring which has a front sealing surface 26 combined with that of the cylindrical surface of the plug 16, is pressed against the plug 16 by the pressure prevailing in the combustion chamber 4 and acting on its annular section against the pressure prevailing in the bore 17 and only slightly higher than atmospheric pressure.
  • the axis of the orifices 20 and 21 is placed in the figure substantially in the axis of the cylinder 2 but it can also be inclined. to provide a more advantageous arrangement of the spark plug 5 and allow the use of a combustion chamber 4 at the corner ensuring greater turbulence of the compressed gases and better propagation of the ignition flame.
  • the plug 16 which has also rotated comes to communicate its transverse channel 19, already connected to the exhaust orifice 21, with the orifice 20 which opens onto the combustion chamber 4 .
  • the movement of the piston 10 continues up to the bottom dead center shown, the pressure in the transfer chamber continues to increase while the pressure in the cylinder 2 and the combustion chamber 4 decreases very quickly through the wide passage section of the transverse channel 19 which is placed at the bottom dead center of the piston 10, exactly in the axis of the cylinder 2 and the orifice 20.
  • the cross section of the channel 19 is substantially equal to the section of the orifice 20 formed in the sealing ring 22 at contact of the external cylindrical surface of the plug 16 and the inlet and outlet edges of the channel 19 correspond thus substantially at bottom dead center of the piston 10 with the corresponding edges of the orifice 20 open on the combustion chamber.
  • the scraper segment then discovers the inlet lumen 11 which connects the carburetor 12 to the transfer chamber 7, in slight depression under the effect of the rise of the piston 10 towards the top dead center. While the piston 10 continues to climb towards top dead center, the vacuum in the transfer chamber 7 is maintained despite the supply of fresh gas and the inertia of the gas column between the carburetor 12 and the transfer chamber 7 allows the continued filling of the chamber 7 by a mechanical hysteresis effect until the moment when, after the top dead center of the piston 10 and the ignition of the compressed fuel mixture in the combustion chamber 4, the piston 10 descends again and closes again by the scraper segment the inlet 11, according to the position shown in Figure 1.
  • the exhaust control system which has just been described in combination with an internal combustion engine operating according to the two-stroke cycle could be applied to a 2- or 4-stroke engine to replace the exhaust valves and / or air intake in the cylinders and one could also use other adjustments of the position of the transverse channel 19 relative to the various positions of the piston 10.
  • This channel 19 could also consist of two openings of relatively small section opening out on a central section of larger section to produce an exhaust gas pre-expansion chamber in the plug 16.
  • the orifices 20 and 21 as well as the section of the channel 19 may have a circular shape but more advantageously the shape of a rectangle or a square (for example, with truncated angles).
  • the orifice 20 can open at any point on the wall of the combustion chamber 4 and can also constitute the admission of fresh gases into the combustion chamber 4.
  • the intake ports can be supplied by any means other than the overpressure in the transfer chamber 7 which can itself be etched with compressed air by the compressor of a turbocharger or a vane pump.
  • the sealing ring 22 is applied to the plug 16 by the only pressure prevailing in the combustion chamber 4 which, for high compression engines such as diesel engines, can, at the top dead center of the piston 10, reduce to the interior space of the ring 22, the injection of the fuel being effected by means of an injector delivering a sheet of atomized fuel substantially parallel to the upper surface of the piston 10 or to the inlet section of the ring 22 on the side of the combustion chamber 4.
  • the channel 19 could also, in certain versions, be replaced by a lateral notch formed on the side of the plug 16 and putting in communication a lateral exhaust 21 with the combustion chamber 4 and alternatively, if necessary, with the fresh gas intake.
  • the proposed sealing element is produced in such a way that its inertia at its minimum section, along the cutting plane 108 (see FIG. 3), allows it great flexibility so that, as soon as a pressure is applied. gas even weak (start of engine compression) in the combustion chamber 104, the radius of curvature OB of the element can conform to the radius of curvature OA of the distributor by the bending of element 103 even for appreciable differences between these two rays OA and OB and ensure permanent contact allowing sealing.
  • FIG. 4 represents the deformation of the annular seal 103, mainly under the effect of the heating in friction contact with the distributor 101.
  • the radius of curvature OA of the distributor is greater than the radius of curvature OB of the element d sealing. Under the effect of the application of pressure, the element 103 deforms outwards so that OA equals OB.
  • the radius of curvature of the distributor OA is smaller than the radius of curvature OB of the element 103 which is not subjected to pressure. Under the effect of the pressure of the combustion chamber 104, the sealing element 103 deforms inwards so that OA is equal to OB.
  • an initial radius of curvature OB which is smaller than the initial radius of curvature OA when machining the distributor 101, will preferably be chosen when machining the sealing element.
  • the clearance between the sealing element 103 and its bore 105 must be sufficient to accept the deformations of conformability without jamming detrimental to the proper functioning and be chosen as a function of the in-depth study of all the scenarios that may be encountered in operation. .
  • the minimum section 108 of the seal 103 is reduced to the lowest admissible height making it possible to withstand the stresses of the pressure prevailing in the passage 107a and which tends to cause the seal 103 to burst radially.
  • the thickness e of the seal 103 is between 1/10 and 1/8 of the outside diameter of the distributor 101 to achieve a good compromise between the pressure forces applied on the seal towards the plug, the section of the seal applied to the plug via the oil film and the deformation of the seal under the effect of the pressure of the gases from the combustion chamber passing through it.
  • the outside diameter of the element 103 and the bore 105 which guides it can be between 4/7 and 6/7 of the outside diameter of the plug 101 to achieve a good compromise between the central passage section of the seal, the surface contact with the valve capable of improving the resistance of the oil film and the curvature of the contact zones with the valve at the edges of the joint along a plane transverse to the axis of rotation of the valve, this curvature being capable of reducing the resistance oil film.
  • the axial clearance between the flat base 120 of the seal 103 and the bearing face 112 formed in the body 101a which contains the distributor 101 must be reduced to the minimum compatible with the expansions of this body 101a, of the seal 103 and of the distributor 101, that is to say for the current dimensions of two-stroke engines, at dimensions of the order of 5/10 of a millimeter.
  • the permanent plating of the sealing element 103 on the distributor 101 in the form of a bushel is ensured without the presence of a return spring simply because of the slight conicity of the bore 105 which tends to repel by a sort of mechano-pneumatic effect the seal 103 in the direction of the plug 101 against gravity acting on the element 103 when the sealing device is placed, according to FIG. 6, at the head of the combustion chamber.
  • the element 103 may have an outside diameter very close to that of the bore 105 so that during its diametral swelling under the action of the pressure of the combustion chamber 104, it comes to bear on the wall of this bore, which limits the risk of bursting.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (2)

1. Dichtungsorgan für ein wesentlich zylindrisches Drehventilküken (16, 101) mit wenigstens einem Durchlasskanal (19, 107), an welchem sich eine ringförmige Dichtung (22, 103) abstützt, deren Achse quer zur Drehachse des Ventilkükens (16, 101) verläuft, insbesondere zur Abdichtung einer Auspufföffnung einer Brennkammer (4, 104) eines Verbrennungsmotors, wobei die ringförmige Dichtung (22, 103) in axialer Richtung dicht durch ihre in einer Bohrung (23, 105) bewegliche Aussenfläche geführt und an das Ventilküken (16, 101) durch den in der Brennkammer (4, 104) herrschenden Druck angedrückt wird und wobei die die Dichtung (22, 103) führende Bohrung (23, 105) leicht kegelförmig, sich in Richtung auf die Brennkammer (4, 104) verjüngend gestaltet ist, um die Dichtung (23, 103) dauernd in Richtung auf das Ventilküken (16, 101) zu zu drücken, während die Kontaktzone zwischen dem Ventilküken (16, 101) und der Dichtung (22, 103) durch einen Ölfilm geschmiert ist, der trotz des von den das Ventilküken (16, 101) durchströmenden Gasen ausgeübten Drucks der Brennkammer (4, 104) aufrechterhalten wird, dadurch gekennzeichnet, dass die ringförmige Dichtung (103) in ihrer Zone (108) geringsten axialen Querschnitts eine axiale Höhe besizt, die etwa der Minimalhöhe entspricht, durch welche der Widerstand gegen den innerhalb der Dichtung herrschenden Druck der Brennkammer (104) gewährleistet ist, derart, dass die Dichtung bei ihrem Anpressen an das Ventilküken (101) eine befriedigende Nachgiebigkeit aufweist und die Widerstandsfähigkeit des Ölfilms erhöht wird, und dass der Aussendurchmesser der ringförmigen Dichtung (103) zwischen 4/7 und 6/7 des Aussendurchmessers des Ventilkükens (101) liegt, um einen befriedigenden Kompromiss zwischen dem Zentraldurchlassquerschnitt (107a) der Dichtung, der die Aufrechterhaltung des Ölfilms erhöhenden Berührungsfläche mit dem Ventilküken (101) sowie der der Aufrechterhaltung des Ölfilms entgegenwirkenden Krümmung der Berührungsflächen mit dem Ventilküken an den Rändern der Dichtung (103) in einer quer zur Drehachse des Ventilkükens (101) liegenden Ebene zu gewähren.
2. Organ nach Anspruch 1, dadurch gekennzeichnet, dass die ringförmige Dichtung (103) eine in axialer Richtung veränderliche Wandungsdicke aufweist, deren Trägheitsmodul im Minimalquerschnitt (108) im Hinblick auf die Verformbarkeit der Dichtung (103) und auf ihr Andrücken an das Ventilküken (101) bei geringem Druck von etwa 0,1 bis 1 bar bestimmt ist, derart dass die Widerstandsfähigkeit der Dichtung (103) gegen Sprengung unter dem Einfluss des Druckes der Brennkammer (104), sowie die Aufrechterhaltung des Ölfilms zwischen der Dichtung (103) und der Ventilkükenoblerfläche (101) gewährleistet sind.
EP83401495A 1982-07-27 1983-07-20 Dichtungselement für eine Gaszyklus-Regelvorrichtung einer Brennkammer Expired EP0100713B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83401495T ATE23603T1 (de) 1982-07-27 1983-07-20 Dichtungselement fuer eine gaszyklusregelvorrichtung einer brennkammer.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8213072 1982-07-27
FR8213072A FR2531174A1 (fr) 1982-07-27 1982-07-27 Element d'etancheite pour un boisseau rotatif
FR8213071A FR2531139B1 (fr) 1982-07-27 1982-07-27 Dispositif de controle d'un circuit de gaz d'une chambre de combustion
FR8213071 1982-07-27

Publications (2)

Publication Number Publication Date
EP0100713A1 EP0100713A1 (de) 1984-02-15
EP0100713B1 true EP0100713B1 (de) 1986-11-12

Family

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Family Applications (1)

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EP83401495A Expired EP0100713B1 (de) 1982-07-27 1983-07-20 Dichtungselement für eine Gaszyklus-Regelvorrichtung einer Brennkammer

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Country Link
US (1) US4506636A (de)
EP (1) EP0100713B1 (de)
BE (1) BE897345A (de)
DE (1) DE3367651D1 (de)

Families Citing this family (27)

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Publication number Priority date Publication date Assignee Title
FR2576060B2 (fr) * 1985-01-17 1988-01-22 Elf France Dispositif de controle de la circulation des gaz de et/ou vers une chambre de combustion de moteur a combustion interne
US4606309A (en) * 1982-07-27 1986-08-19 Elf France Device for controlling the combustion chambers exhaust and/or intake for internal combustion engines
EP0152321B1 (de) * 1984-02-03 1987-10-28 Elf France Anlage zur Kontrolle für das Öffnen und Schliessen der Brennkammer einer Brennkraftmaschine
FR2559208B1 (fr) * 1984-02-03 1987-12-04 Elf France Dispositif de controle de l'echappement et/ou de l'admission des chambres de combustion de moteur a combustion interne
US4794895A (en) * 1986-06-25 1989-01-03 Volkswagen Ag Sealing arrangement for a rotary slide valve
DE3720084A1 (de) * 1986-06-25 1988-01-07 Volkswagen Ag Dichtungsanordnung fuer einen drehschieber
GB2221954B (en) * 1988-08-16 1992-07-08 Austin Rover Group An internal combustion engine inlet manifold
IT1225433B (it) * 1988-10-26 1990-11-13 Giancarlo Brusutti Elemento di tenuta per distributore rotante di motori a combustione interna.
FR2649156B1 (fr) * 1989-06-30 1994-04-01 Institut Francais Petrole Moteur deux temps a boisseaux tournants et utilisations d'un tel moteur
US4944262A (en) * 1989-04-05 1990-07-31 Inasa Automotive, Inc. Rotative combustion chamber engine
US5771849A (en) * 1995-09-15 1998-06-30 Hamy; Norbert Internal combustion engine with crankcase pressure barrier
US5967108A (en) 1996-09-11 1999-10-19 Kutlucinar; Iskender Rotary valve system
US6006714A (en) * 1997-05-13 1999-12-28 Griffin; Bill E. Self-sealing rotary aspiration system for internal combustion engines
DE29920719U1 (de) * 1999-11-25 2001-04-05 Dolmar Gmbh Viertakt-Verbrennungsmotor mit Drehschiebersteuerung
DE10034679A1 (de) * 2000-07-17 2002-01-31 Bayerische Motoren Werke Ag Dichtungsanordnung für einen insbesondere zur Ladungssteuerung bei Brennkraftmaschinen dienenden Drehschieber
US7213546B2 (en) 2001-03-21 2007-05-08 Steven Vermeer Engine airflow management system
US6578538B2 (en) 2001-04-02 2003-06-17 O. Paul Trentham Rotary valve for piston engine
US6595177B1 (en) 2002-02-27 2003-07-22 Kramer Jewelers, Inc. #2 Rotary sleeve port for an internal combustion engine
ES2249068B1 (es) * 2002-06-10 2007-06-01 Antonio Ferreres Lopez Valvula de distribucion rotativa.
US6880511B1 (en) * 2003-10-27 2005-04-19 George J. Coates Valve seal assembly for rotary valve engine
WO2006069503A1 (fr) * 2004-12-31 2006-07-06 Yamin Liu Moteur a deux temps a chambres de combustion multiples
US7255082B2 (en) * 2005-03-09 2007-08-14 Zajac Optimum Output Motors, Inc. Rotary valve system and engine using the same
US8714119B2 (en) * 2008-06-05 2014-05-06 Stuart B. Pett, Jr. Parallel cycle internal combustion engine with double headed, double sided piston arrangement
US8499727B1 (en) 2008-06-05 2013-08-06 Stuart B. Pett, Jr. Parallel cycle internal combustion engine
EP2261470A1 (de) * 2009-06-08 2010-12-15 Léon Crosset Verbrennungsmotor mit sphärischem Drehventil
IT1401026B1 (it) * 2010-07-28 2013-07-12 E2F Di Esposti Federici Ettore Gruppo valvola di scarico per motore a due tempi, raffreddata con tenuta senza contatto e autopulente.
US10914205B2 (en) * 2017-03-14 2021-02-09 Onur Gurler Rotational valve for two stroke engine

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FR405464A (fr) * 1909-07-26 1909-12-31 Howard Earl Coffin Moteur à explosion
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Also Published As

Publication number Publication date
DE3367651D1 (en) 1987-01-02
US4506636A (en) 1985-03-26
BE897345A (fr) 1984-01-20
EP0100713A1 (de) 1984-02-15

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