US3817227A - Two-cycle internal combustion engine - Google Patents

Two-cycle internal combustion engine Download PDF

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Publication number
US3817227A
US3817227A US00232325A US23232572A US3817227A US 3817227 A US3817227 A US 3817227A US 00232325 A US00232325 A US 00232325A US 23232572 A US23232572 A US 23232572A US 3817227 A US3817227 A US 3817227A
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United States
Prior art keywords
exhaust
recess
supply
gas
cylinder
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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
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US00232325A
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English (en)
Inventor
S Onishi
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Nippon Clean Engine Res Inst Co Ltd
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S Onishi
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Assigned to NIPPON CLEAN ENGINE RESEARCH INSTITUTE CO., LTD reassignment NIPPON CLEAN ENGINE RESEARCH INSTITUTE CO., LTD ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ONISHI, SHIGERU
Anticipated expiration legal-status Critical
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    • 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
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/14—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • 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

Definitions

  • cmbusfion l having [58] Field of Search 1213/65 R 65 w 65 W A electric ignltlon system and characterized in that a 123 73 R 73 98 suitably shaped recess is disposed inside the cylinder head, thereby forming a combustion chamber.
  • a de- [56] References Cited vice for controlling the quantity of fuel supply and a device for controlling the flow of exhaust gas are oper UNITED STATES PATENTS ated relatively to each other in such a way that the 13 5 lsmdefson flow of exhaust gas is increased or decreased in repencer 2 L 5/1936 Harper-m.
  • the conventional two-cycle internal combustion engine of loop or cross-scavenging type, particularly of crank case compression type is structurally simple and can be manufactured at a low cost.
  • misfire often takes place even if an easily combustible mixture with a high fuel-air ratio is used in the no-load or part-load operating condition.
  • This results in an irregular combustion state involving unpleasant exhaust sounds and rough vibration.
  • the specific fuel consumption is raised and the noxious component in the exhaust gas is increased.
  • the exhaust pipeline is designed to be suitable as to size and shape so that the negative pressure wave produced in the pipe due to the flow of exhaust gas is reversely introduced into the cylinder.
  • This arrangement is effective during high load operation, while it serves as a significant factor causing misfire, because, at a light load where a small amount of gas mixture is applied, the supplied gas mixture is unnecessarily mixed with the residual gas.
  • the present invention has, as its principal aim, the provision of an improved twocycle internal combustion engine operable at a high combustion efficiency in each cycle even at a relatively low fuel-air ratio, and capable of preventing misfire irrespective of operating condition, minimizing vibration and noise of engine, decreasing the specific fuel consumption, i.e., increasing the thermal efficiency, and purifying the exhaust gas.
  • an object of this invention is to provide a two-cycle internal combustion engine in which a suitably shaped recess is disposed inside the cylinder head, thereby forming a combustion chamber, an exhaust gas control part disposed in the exhaust pipeline and a fuel supply control part are relatively operated in such a way that at a part-load operation the gas mixture flow into the cylinder is reasonably slowed and stratified and the mixture is securely sent in said recess space whereby stable combustion is maintained in each cycle even at a low fuel-air ratio, misfire is prevented, and the exhaust gas is purified.
  • Another object of this invention is to provide a twocycle internal combustion engine in which the squish effect is brought about in the vicinity of the top dead center whereby a higher ignitability is maintained and combustion is accelerated.
  • Still another object of this invention is to provide a twofcycle internal combustion engine in which an ingition plug is disposed in a specific position and said recess part whereby a higher ignitability is achieved.
  • FIG. I is a schematic sectional side view showing the overall construction
  • FIG. 2 is an enlarged view of the cylinder portion, showing the state of distribution of the fuel particles in the injected mixture gas
  • FIG. 3 is a schematic sectional view taken along line 1-1 of FIG. 2 in the direction of the arrows;
  • FIGS. 4 and 5 are schematic sectional views taken along lines 2-2 and 3-3, respectively, of FIG. 3, in the direction of the arrows and showing the state of squish flow;
  • FIG. 6 is a graphic representation showing the relationship between the exhaust control valve and the throttle valve with respect to valve opening.
  • FIG. 7 is a diagrammatic representation of a valvecontrolling linkage.
  • FIG. 1 there is schematically illustrated a Schnuerle scavenging type two-cycle internal com bustion engine having a crank case compression systern, wherein a scavenging port 3 and an exhaust port 4 are opened/closed by the motion of a piston 2 reciprocatively disposed in a cylinder 1.
  • An exhaust control valve 6 is provided in an exhaust pipe 5 connected to exhaust port 4. This exhaust control valve is located at a small distance from said exhaust port 4 whereby a prechamber 20 is formed.
  • a carbureter 26 is disposed in an intake pipe 7 communicating with a crank case 12.
  • a control lever 9 of a throttle valve 8 of a fuel-supply control means which is to control the fuel supply and a control lever 10 of exhaust control valve 6 of an exhaust-gas control means are interlocked by way of a link mechanism 11, as shown schematically in FIG. 1.
  • a one-way, flexible, springer leaf valve (not shown) which serves to stop the back flow from the crank case 12 is provided in a part 19 where said intake pipe is connected to the crank case 12.
  • the gas mixture compressed in the crank case 12 by the motion of piston 2 is supplied to the cylinder 1 from the scavenging port 3 by way of scavenging passages 13, which are located opposite to each other on the both sides of the cylinder respectively.
  • FIGS. 2 and 3 show a recess 15 formed in the neighborhood of the center of the cylinder head. More specifically, the recess is formed to become gradually deeper in the direction of the gas flow in the cylinder, in which the gas stream turns from the upward to downward direction in the vicinity of the cylinder head.
  • the deepest part of the recess 15 is located on the front side of the direction along which the stream advances, and the space of the recess is wide enough so that the stream turning round in the axial direction of the cylinder makes a swirling motion.
  • The: inside of the recess has no part wider than its open end so that the shape of the recess does not become constricted at its open end.
  • the inner surface 17 of the cylinder head 14 around the recess 15 is shaped corresponding to the top surface' 18 of the piston, and the gases held between the surface 17 and the top of the cylinder head produce a squish stream near the top dead center.
  • This squish stream can be strengthened or weakened by changing the relative relationship between the surface 17 and the top surface 18. Namely, the strength of the squish stream can be determined by the distance between surfaces 17 and 18 at the point of the top dead center, the shapes of surfaces 17 and 18, etc.
  • This engine of the invention is operated in the following manner:
  • the gas mixture sucked into the crank case 12 by the motion of the piston 2 by way of the throttle valve 8 of carbureter 26 and the intake pipe 7 is compressed and pressurized by the down motion of the piston 2.
  • the pressurized gas burnt in the cylinder is expanded by the down motion of the piston.
  • the exhaust control valve 6 also is throttled by the interlocking link mechanism l1, and valve 6 becomes nearly closed.
  • the exhaust gas is subjected to resistance at the valve 6, and the pressure in the prechamber 20 is increased. Therefore, the pressure in the cylinder 1 is not rapidly lowered, and flowing of the scavenged (or supplied) gas into the chamber 1 by the opening of the scavenging port 3 is slowed. In other words, the subsequently supplied gas mixture is mixed and diffused into the residual exhaust gas only to a small extent.
  • the gas mixture is fed into the recess of the cylinder head without sacrificing the combustibility even if the air-fuel ratio is determined to be larger than the stoichiometric value.
  • the supplied gas is stratified in the form of an are or sphere in the cylinder as indicated by the dot group in FIG. 2 before the gas is appreciably mixed with the residual burnt gas, and there is formed a pattern of stream of the supplied gas flowing moderately into the recess 15.
  • the purpose of the exhaust valve 6 in its nearly closed position is to reflect the interfering wave reversely propagated from the exhaust passage 5 (positioned after the valve 6) into the cylinder 1, keep the stream in the cylinder 1 from being disturbed, and minimize the disturbing influence which may be introduced into the cylinder from the exhaust pipeline. This function contributes largely to perfecting said stratified gas supply.
  • the mean effective pressure is gradually reduced under the condition that the throttle valve 'is kept opened at a certain opening, the interlocking link 11 is released, and only the opening of the exhaust control valve 6 is gradually reduced from its full opening.
  • a similar result can be obtained under the condition that the exhaust control valve is kept opened at a certain opening, and the throttle valve is closed from its full opening.
  • FIG. 7 it will be seen that between the levers 9 and 10 there is a cam 11a having a camming edge 11b and supported for free swinging movement about a pivot pin 11b.
  • An elongated link is pivotally connected at its opposite ends to the lever 9 and the cam 11a.
  • the lever 10 is urged in a counter clockwise direction, as viewed in FIG. 7, toward the cam 110 by a spring 10b, and the lever 10 carries a camfollower roller 10a engaging the camming edge 11b.
  • the lever 9 can be swung in the opening and closing directions as indicated by the double-headed arrow, and the lever 10 will be correspondingly swung in opening and closing directions through the linkage means 11 of FIG. 7. Because of the shape of the camming edge 11b the extent of opening and closing of the valve 6 by turning of the lever 10 will have with respect to the opening and closing of the valve 8 by the lever 9 the relationship shown in FIG. 6.
  • the gas supplied to the cylinder 1 relatively slowly and in the stratified form is introduced to the recess 15 of the cylinder head round about the central zone 22 in the cylinder 1.
  • the stream of this gas is in spherical form and subjected to a centrifugal force and, hence,
  • the recess is shaped to become gradually deeper so that the supplied gas flows therein smoothly.
  • the recess is deepest on the side of the front of the gas stream. in this deepest portion the supplied gas is securely re ceived and temporarily held.
  • a spark plug 16 is mounted in a deep part 21 so that the spark plug is positioned in a quiet atmosphere inside the recess and is beyond the gas stream in the cylinder. This facilitates ignition and spread of the initial flame.
  • a squish stream is produced near the top dead center due to the top 18 of the piston and the inner surface 17 of the cylinder head.
  • the squish stream 23 due to the top surface of the shallow portion of the recess 15 and the top of the piston serves to drive the supplied mixture into the deep part of the recess.
  • the squish stream 25 opposite to the squish stream 23 acts to keep the supplied gas mixture from flowing out of the recess.
  • the function of the squish streams from the both sides of the recess is to press and spread the supplied gas mixture over the wall of the recess.
  • the engine of this invention can be driven with a thin gas mixture whose airfuel ratio is, for example, 15 to 18, by suitably determining the correlation between the exhaust control valve 6 and the shape of the recess 15 of the cylinder head. Especially under part-load and no-load operating conditions, misfire and irregular cycle are minimized or eliminated. This makes it possible to reduce the number of rotations set for idling and to minize the fuel consumption during idling rotation.
  • stable combustion is maintained at a large air-fuel ratio.
  • This in turn increases the efficiency of purifying the exhaust gas.
  • concentration of carbon monoxide (CO) is reduced below 1/10 compared with that in the prior art.
  • the component of unburnt hydrocarbon is also reduced to about half that in the prior art by the use of exhaust control valve 6, thereby preventing ineffective dispersion of fuel gas due to stratification and thus minimizing bypass gas flow out to the exterior.
  • NOx nitrogen oxide
  • the combustibility at a large air-fuel ratio and the minimized fuel bypass escape contribute to improvement on the specific fuel consumption, i.e., on the thermal efficiency.
  • stable combustion having a small cycle variation is realized and the engine vibration and noise are reduced.
  • the peak value of the exhaust jet velocity during idling and part-load operation is suppressed and smoothed by virtue of the exhaust control valve and, hence, the exhaust sound from the end of the exhaust pipe is reduced to permit quiet engine drive.
  • an engine using a carbureter has been described.
  • a suitable injection system may be employed instead of carbureter.
  • an intake pipe injection, crank case injection, injection into the cylinder from the scavenging port, injection into the cylinder from the cylinder or from the cylinder head, etc. may be used.
  • the invention permits use of various fuels, for example, gaseous fuel such as LPG, and low quality fuel such as kerosene oil.
  • the device for controlling the amount of fuel injection into the cylinder, and the device for controlling the flow of the exhaust gas are relatively operated whereby the flow of the exhaust gas is decreased or increased in response to decrease or increase in the fuel supply.
  • This concept can be applied to Diesel compression ignition engines. ln this case, during no loador part-load operation where a small amount of fuel is injected therein, it is necessary to throttle the exhaust control valve so that a suitable amount of air corresponding to the existing load is supplied to the combustion chamber in the stratified form. By this arrangement, it becomes possible not only to reduce the pump loss for air supply but also to hold a relatively large amount of residual gas.
  • the compression initial temperature i.e., the compression end temperature
  • the compression end temperature can be raised, thus making available a sufficient temperature rise necessary for the engine operable at a low compression ratio, and the fuel ignition delay time can be reduced.
  • the Diesel knocking phenomenon can be almost perfectly eliminated.
  • the component of nitrogen oxide (NOx) which is a typical problem of Diesel engines can be largely reduced to about 200 ppm at the full load. it is apparent that the invention, when applied to Diesel engines, is particularly useful and practical.
  • elongated cylinder means having a cylinder axis and formed in its interior at one end region with a combustion recess which becomes gradually deeper in the direction of gas flow in the cylinder up to a deepest portion of said recess situated at that side of said axis toward which the gas stream flows after crossing said axis, the direction of gas flow changing beyond said deepest portion of said recess and said recess having its maximum cross sectionin a plane normal to said axis at that part of said recess which is most distant from the deepest portion of said recess, so that said recess is not constricted at its entrance end, exhaust port means and scavenging port means communieating with said cylinder means, piston means reciprocating in said cylinder means for opening and closing said exhaust port means and said scavenging port means, a crank case situated beneath said cylinder means and receiving fuel to be compressed by said piston means while the latter moves
  • each of said control means including a duct and a tiltable valve therein, and said means interconnecting both of said control means including a mechanical transmission means extending between and operatively connected to said tiltable valves for providing for each angular position of said tiltable valve for said fuelsupply control means a predetermined angular position for said tiltable valve of said exhaust-gas control means, said mechanical transmission means including a pair of levers respectively connected with said tiltable valves for respectively swinging the latter when said levers turn, a cam swingably mounted between said levers, a link interconnecting the lever which is connected to said tiltable valve of said fuel-supply control means with said cam, a cam follower fixedly carried
US00232325A 1971-02-25 1972-02-22 Two-cycle internal combustion engine Expired - Lifetime US3817227A (en)

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JP46009703A JPS5014681B1 (it) 1971-02-25 1971-02-25

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JP (1) JPS5014681B1 (it)
CA (1) CA962603A (it)
DE (2) DE7206510U (it)
FR (1) FR2127825A5 (it)
GB (1) GB1386363A (it)
IT (1) IT951033B (it)
SE (1) SE377707B (it)
SU (1) SU556737A3 (it)

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3969895A (en) * 1974-06-24 1976-07-20 John Krizman Power control valve attachment for two cycle motorcycle type engine exhaust systems
US3978839A (en) * 1974-12-18 1976-09-07 Outboard Marine Corporation Primer system for internal combustion engine
US4062331A (en) * 1972-08-22 1977-12-13 Performance Industries, Inc. Two cycle internal combustion engine
US4121552A (en) * 1974-09-17 1978-10-24 Yamaha Hatsudoki Kabushiki Kaisha Exhaust means for two cycle engines
US4180029A (en) * 1976-12-29 1979-12-25 Toyota Jidosha Kogyo Kabushiki Kaisha 2-Cycle engine of an active thermoatmosphere combustion
US4185598A (en) * 1976-08-25 1980-01-29 Toyota Jidosha Kogyo Kabushiki Kaisha Internal combustion engine
US4237831A (en) * 1977-11-18 1980-12-09 Nippon Soken, Inc. Two-cycle engine
US4250856A (en) * 1980-01-25 1981-02-17 Abbey Harold Fuel-air ratio automatic control system using variable venturi structure
US4445468A (en) * 1981-10-23 1984-05-01 Nippon Clean Engine Research Institute Co., Ltd. 2-Stroke internal combustion engine and an ignition-combustion method of an internal combustion engine
DE3617317A1 (de) * 1985-05-24 1986-12-11 Orbital Engine Co. Pty. Ltd., Balcatta, Westaustralien Zweitaktverbrennungsmaschine
US4660514A (en) * 1980-04-21 1987-04-28 Outboard Marine Corporation Two-cycle internal combustion engine including means for varying cylinder port timing
US4765137A (en) * 1986-03-07 1988-08-23 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4785626A (en) * 1986-10-27 1988-11-22 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
USRE32802E (en) * 1984-12-31 1988-12-20 Cummins Engine Company, Inc. Two-cycle engine with improved scavenging
US4795420A (en) * 1986-03-07 1989-01-03 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4817374A (en) * 1986-09-13 1989-04-04 Yamaha Hatsudoki Kabushiki Kaisha Exhaust control device of engine
US4831823A (en) * 1987-02-24 1989-05-23 Yamada Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
US4840029A (en) * 1986-03-07 1989-06-20 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4860538A (en) * 1988-02-23 1989-08-29 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
US4896504A (en) * 1986-12-03 1990-01-30 Yamaha Matsudoki Kabushiki Kaisha Exhaust gas control device for engines
US4909033A (en) * 1985-11-26 1990-03-20 Yamaha Hatsudoki Kabushiki Kaisha High performance exhaust system for internal combustion engine
US4912930A (en) * 1985-11-26 1990-04-03 Yamaha Hatsudoki Kabushiki Kaisha High performance exhaust system for internal combustion engine
US4995349A (en) * 1988-02-08 1991-02-26 Walbro Corporation Stratified air scavenging in two-stroke engine
US4999999A (en) * 1987-09-14 1991-03-19 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control device for motorcycles
US5027758A (en) * 1990-07-09 1991-07-02 Frederick Siegler Fuel system for crankcase scavenged two cycle spark ignition engines
DE4241429A1 (de) * 1992-12-09 1994-06-30 Svein Wieneke Opto-Elektronische Steuerung des Auslass-Kanals für Zweitakt-Verbrennungsmotoren
US5692468A (en) * 1995-07-25 1997-12-02 Outboard Marine Corporation Fuel-injected internal combustion engine with improved combustion
US6435159B1 (en) 2000-05-10 2002-08-20 Bombardier Motor Corporation Of America Fuel injected internal combustion engine with reduced squish factor
DE102008038915A1 (de) * 2008-08-13 2010-02-18 3W-Modellmotoren Gmbh Zweitaktmotor und Verfahren zum Betreiben eines Zweitaktmotors
US20100038805A1 (en) * 2008-08-13 2010-02-18 3W-Modellmotoren Gmbh Two-stroke engine and method for operating a two-stroke engine
US20100095671A1 (en) * 2007-02-07 2010-04-22 Hajime Takagawa Cylinder head of internal-combustion engine
US20120234293A1 (en) * 2009-12-01 2012-09-20 Ueki Kaneyuki Internal combustion engine and method of producing the same

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5091891U (it) * 1973-12-21 1975-08-02
GB1591050A (en) * 1976-08-25 1981-06-10 Onishi S Internal combustion engine
US4766854A (en) * 1987-06-19 1988-08-30 Brunswick Corporation Exhaust valve throttling mechanism for two-stroke engine

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DE17176C (de) * F. CHEESWRIGHT in London Neuerungen an Eisenbahn-Signal-Apparaten
US1299895A (en) * 1918-05-01 1919-04-08 William F Fischer Internal-combustion engine.
FR572529A (fr) * 1922-11-22 1924-06-07 Perfectionnements dans les moteurs à combustion interne à deux temps
US1780635A (en) * 1929-03-21 1930-11-04 Owen H Spencer Choke means for two-cycle engines
US2041708A (en) * 1931-01-20 1936-05-26 H B Motor Corp Combustion engine
US2064983A (en) * 1934-06-08 1936-12-22 Lesage Alfred Two stroke piston-controlled engine
GB605610A (en) * 1945-03-24 1948-07-27 Saurer Ag Adolph Improvements in and relating to the control of two-stroke internal combustion engines of the fuel injection type
DE865233C (de) * 1940-06-21 1953-02-02 Auto Union A G Gemischverdichtende Zweitaktbrennkraftmaschine
FR67520E (fr) * 1955-02-02 1958-03-13 Auto Union Gmbh Moteur à combustion interne à deux temps, en particulier pour des véhicules automobiles
US3400702A (en) * 1966-04-28 1968-09-10 Outboard Marine Corp Idling arrangement for internal combustion engine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE17176C (de) * F. CHEESWRIGHT in London Neuerungen an Eisenbahn-Signal-Apparaten
US1299895A (en) * 1918-05-01 1919-04-08 William F Fischer Internal-combustion engine.
FR572529A (fr) * 1922-11-22 1924-06-07 Perfectionnements dans les moteurs à combustion interne à deux temps
US1780635A (en) * 1929-03-21 1930-11-04 Owen H Spencer Choke means for two-cycle engines
US2041708A (en) * 1931-01-20 1936-05-26 H B Motor Corp Combustion engine
US2064983A (en) * 1934-06-08 1936-12-22 Lesage Alfred Two stroke piston-controlled engine
DE865233C (de) * 1940-06-21 1953-02-02 Auto Union A G Gemischverdichtende Zweitaktbrennkraftmaschine
GB605610A (en) * 1945-03-24 1948-07-27 Saurer Ag Adolph Improvements in and relating to the control of two-stroke internal combustion engines of the fuel injection type
FR67520E (fr) * 1955-02-02 1958-03-13 Auto Union Gmbh Moteur à combustion interne à deux temps, en particulier pour des véhicules automobiles
US3400702A (en) * 1966-04-28 1968-09-10 Outboard Marine Corp Idling arrangement for internal combustion engine

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062331A (en) * 1972-08-22 1977-12-13 Performance Industries, Inc. Two cycle internal combustion engine
US3969895A (en) * 1974-06-24 1976-07-20 John Krizman Power control valve attachment for two cycle motorcycle type engine exhaust systems
US4121552A (en) * 1974-09-17 1978-10-24 Yamaha Hatsudoki Kabushiki Kaisha Exhaust means for two cycle engines
US3978839A (en) * 1974-12-18 1976-09-07 Outboard Marine Corporation Primer system for internal combustion engine
US4185598A (en) * 1976-08-25 1980-01-29 Toyota Jidosha Kogyo Kabushiki Kaisha Internal combustion engine
US4180029A (en) * 1976-12-29 1979-12-25 Toyota Jidosha Kogyo Kabushiki Kaisha 2-Cycle engine of an active thermoatmosphere combustion
US4237831A (en) * 1977-11-18 1980-12-09 Nippon Soken, Inc. Two-cycle engine
US4250856A (en) * 1980-01-25 1981-02-17 Abbey Harold Fuel-air ratio automatic control system using variable venturi structure
US4660514A (en) * 1980-04-21 1987-04-28 Outboard Marine Corporation Two-cycle internal combustion engine including means for varying cylinder port timing
US4445468A (en) * 1981-10-23 1984-05-01 Nippon Clean Engine Research Institute Co., Ltd. 2-Stroke internal combustion engine and an ignition-combustion method of an internal combustion engine
USRE32802E (en) * 1984-12-31 1988-12-20 Cummins Engine Company, Inc. Two-cycle engine with improved scavenging
DE3617317A1 (de) * 1985-05-24 1986-12-11 Orbital Engine Co. Pty. Ltd., Balcatta, Westaustralien Zweitaktverbrennungsmaschine
US4719880A (en) * 1985-05-24 1988-01-19 Orbital Engine Company Pty. Ltd. Two stroke cycle internal combustion engines
AU595199B2 (en) * 1985-05-24 1990-03-29 Orbital Engine Company Proprietary Limited Improvements relating to two stroke cycle internal combustion engines
US4912930A (en) * 1985-11-26 1990-04-03 Yamaha Hatsudoki Kabushiki Kaisha High performance exhaust system for internal combustion engine
US4909033A (en) * 1985-11-26 1990-03-20 Yamaha Hatsudoki Kabushiki Kaisha High performance exhaust system for internal combustion engine
US4840029A (en) * 1986-03-07 1989-06-20 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4869063A (en) * 1986-03-07 1989-09-26 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4795420A (en) * 1986-03-07 1989-01-03 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4765137A (en) * 1986-03-07 1988-08-23 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for engine
US4817374A (en) * 1986-09-13 1989-04-04 Yamaha Hatsudoki Kabushiki Kaisha Exhaust control device of engine
US4785626A (en) * 1986-10-27 1988-11-22 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
US4896504A (en) * 1986-12-03 1990-01-30 Yamaha Matsudoki Kabushiki Kaisha Exhaust gas control device for engines
US4831823A (en) * 1987-02-24 1989-05-23 Yamada Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
US4999999A (en) * 1987-09-14 1991-03-19 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control device for motorcycles
US4995349A (en) * 1988-02-08 1991-02-26 Walbro Corporation Stratified air scavenging in two-stroke engine
US4860538A (en) * 1988-02-23 1989-08-29 Yamaha Hatsudoki Kabushiki Kaisha Exhaust gas control means for motorcycle and the like
US5027758A (en) * 1990-07-09 1991-07-02 Frederick Siegler Fuel system for crankcase scavenged two cycle spark ignition engines
DE4241429A1 (de) * 1992-12-09 1994-06-30 Svein Wieneke Opto-Elektronische Steuerung des Auslass-Kanals für Zweitakt-Verbrennungsmotoren
US5692468A (en) * 1995-07-25 1997-12-02 Outboard Marine Corporation Fuel-injected internal combustion engine with improved combustion
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DE102008038915B4 (de) * 2008-08-13 2011-05-19 3W-Modellmotoren Gmbh Zweitaktmotor und Verfahren zum Betreiben eines Zweitaktmotors
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Also Published As

Publication number Publication date
GB1386363A (en) 1975-03-05
FR2127825A5 (it) 1972-10-13
DE2208200A1 (de) 1972-10-26
JPS5014681B1 (it) 1975-05-29
SE377707B (it) 1975-07-21
CA962603A (en) 1975-02-11
DE7206510U (de) 1976-11-04
IT951033B (it) 1973-06-30
SU556737A3 (ru) 1977-04-30

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