WO2000040843A1 - Zweitaktmotor mit ladungsschichtung - Google Patents
Zweitaktmotor mit ladungsschichtung Download PDFInfo
- Publication number
- WO2000040843A1 WO2000040843A1 PCT/EP2000/000067 EP0000067W WO0040843A1 WO 2000040843 A1 WO2000040843 A1 WO 2000040843A1 EP 0000067 W EP0000067 W EP 0000067W WO 0040843 A1 WO0040843 A1 WO 0040843A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- air
- outlet
- channel
- crankcase
- stroke engine
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 claims abstract description 46
- 239000007789 gas Substances 0.000 claims abstract description 37
- 239000000203 mixture Substances 0.000 claims abstract description 29
- 239000000446 fuel Substances 0.000 claims abstract description 26
- 238000002360 preparation method Methods 0.000 claims description 6
- 238000011010 flushing procedure Methods 0.000 claims description 4
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 230000000903 blocking effect Effects 0.000 claims description 3
- 239000012528 membrane Substances 0.000 claims 2
- 238000000034 method Methods 0.000 abstract 1
- 230000002000 scavenging effect Effects 0.000 abstract 1
- 239000002912 waste gas Substances 0.000 abstract 1
- 238000011161 development Methods 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 239000003344 environmental pollutant Substances 0.000 description 2
- 231100000719 pollutant Toxicity 0.000 description 2
- 238000010926 purge Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- 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
- F02B25/20—Means for reducing the mixing of charge and combustion residues or for preventing escape of fresh charge through outlet ports not provided for in, or of interest apart from, subgroups F02B25/02 - F02B25/18
- F02B25/22—Means for reducing the mixing of charge and combustion residues or for preventing escape of fresh charge through outlet ports not provided for in, or of interest apart from, subgroups F02B25/02 - F02B25/18 by forming air cushion between charge and combustion residues
-
- 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
- F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
- F02B63/02—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for hand-held tools
-
- 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 invention relates to a two-stroke engine, in particular as a drive motor in a portable, hand-held working device according to the preamble of claim 1.
- two-stroke engines are particularly suitable as drive motors in hand-held, portable work tools such as chain saws, cut-off machines, blowers, brush cutters or the like.
- the invention has for its object to develop a two-stroke engine of the generic type in such a way that the flushing losses are reduced and the exhaust gas quality is improved with little design effort.
- the object is achieved according to the characterizing features of claim 1.
- the essentially fuel-free gas expediently flows in in the area near the outlet via channels near the outlet, while the fuel-rich gas required for the operation of the internal combustion engine is expediently supplied via channels far from the outlet.
- the fuel-free gas can shield the outlet in the manner of an air curtain, so that the fuel-rich gas cannot flow out through the outlet. It is essential for this that essentially only fuel-free gas flows in over the entire duration of the flushing cycle, advantageously over the entire opening time of the channel near the outlet, and the fuel / air mixture for operating the internal combustion engine flows exclusively out of the crankcase via the channels remote from the outlet.
- the gas components flowing out via the outlet are predominantly provided by the essentially fuel-free gas, which is why good exhaust gas qualities can be achieved with low HC components.
- the air supply channels close to the outlet are large-volume, in particular several times larger in volume than the channels remote from the outlet and supply the fuel-rich gas.
- the volume of the air-supplying channels is so large in construction that they can accommodate the entire volume of air flowing into the combustion chamber during a gas change. In this way it will be Gas change from the crankcase entering the air supply channel fuel / air mixture used only as a drive means to push the air upstream in the air supply channel close to the outlet into the combustion chamber.
- the valve via which the air flows from an air intake into the channel near the outlet, is expediently a diaphragm valve, but can also be a shut-off valve controlled by the crankcase pressure.
- a slot-controlled auxiliary window is arranged in the cylinder wall as a valve, such that it is constantly covered by the piston skirt.
- a connecting channel is provided in the piston skirt itself, which connects the auxiliary window on the one hand and the inlet window of an overflow channel near the outlet on the other hand in a predetermined stroke position of the piston. It is thereby achieved that air supplied to the auxiliary window via the air intake port flows into the overflow channel near the outlet via the connecting channel in the piston jacket, that is to say the overflow channel is completely filled with air from the combustion chamber in the direction of the crankcase.
- the overflow channel near the outlet is opened, the pure air will flow into the area near the outlet and form a curtain shielding the outlet, which prevents the outflow of the fuel-rich gas flowing in from the outlet.
- the channels close to the outlet are advantageously connected to a pressure accumulator, which is expediently supplied with air via a diaphragm pump driven by the fluctuating crankcase pressure.
- a pressure accumulator which is expediently supplied with air via a diaphragm pump driven by the fluctuating crankcase pressure.
- control valve actuated by the crankcase pressure to be arranged in the desired gas channel.
- the control valve is in particular a pressure-actuated valve slide, which is acted upon by a spring in its blocking position.
- 1 is a schematic section through a two-stroke engine with four gas supply channels
- FIG. 3 shows a schematic representation of the charge stratification in the combustion chamber of the two-stroke engine according to the invention
- FIG. 4 shows a schematic view of a piston with a connecting channel formed in the piston skirt for supplying fuel-free gas
- FIG. 5 shows a partial section through a cylinder for a piston according to FIG. 4
- 6 shows a schematic representation of a partial development of the cylinder wall according to FIG. 5 with pistons at top dead center
- FIG. 7 is a schematic representation of a partial development of the cylinder wall according to FIG. 5 with pistons at bottom dead center
- FIG. 8 shows a schematic representation of an internal combustion engine according to the invention with air supplied under pressure for the channels near the outlet
- FIG. 9 is a schematic representation of an inlet channel or overflow channel with a control valve installed in the channel
- Fig. 10 shows a schematic representation of an arrangement for branching clean air at a mixture processing device.
- the two-stroke engine shown in FIGS. 1 and 2 can be used advantageously in particular as a drive motor in a portable, hand-held work tool such as a motor chain saw, a cut-off saw, a brush cutter, a hedge trimmer, a blower or the like.
- the two-stroke engine 1 consists of a combustion chamber 3 formed in a cylinder 2, which is delimited to form a crankcase 4 by an up and down piston 5.
- the piston 5 is connected via a connecting rod 6 to a crankshaft 7 rotatably mounted in the crankcase 4 and drives it.
- the combustion chamber 3 is assigned an outlet 10 through which the exhaust gases flow.
- the fuel / air mixture required for operating the internal combustion engine is processed in a mixture preparation device 8, for example a diaphragm carburetor, and fed to the crankcase 4 via an inlet channel 9 and an inlet 11.
- the crankcase 4 is connected to the combustion chamber 3 by at least two overflow channels 12.
- the inlet windows 13 of the overflow channels 12 opening into the combustion chamber 3 lie approximately diametrically opposite one another with respect to an axis of symmetry 14.
- the axis of symmetry 14 divides the outlet duct 10 into two identical parts in a top view according to FIG. 2; insofar as the axis of symmetry 14 in the exemplary embodiment corresponds approximately to the longitudinal central axis of the outlet.
- the overflow channels 12 are arranged such that a fuel / air mixture flowing in the direction of the arrow 17 enters the combustion chamber 3 in a plan view according to FIG. 2 at an angle less than or equal to 90 ° to the axis of symmetry 14.
- the gas entering through the channels 15 in the direction of the arrow 18 has a direction of flow which, with the axis of symmetry 14, forms an angle 19 which is open to the outlet 10 and which is less than 90 °, in particular approximately 60 °.
- the combustion chamber 3 thus has four supply gas channels 12 and 15 and an outlet 10.
- more gas-supplying channels can also be provided, whereby there should be a symmetry to the axis 14. That too is Arrangement of a further gas channel between the overflow channels 12 opposite the outlet 10 is expedient.
- the described invention can be used advantageously in n-channel two-stroke engines.
- the channels 15 are expediently open towards the crankcase 4, an air intake 20 opening in the region of the end on the combustion chamber side, advantageously near the inlet window 16.
- the air intake 20 advantageously opens into the channel 15 near the outlet via a diaphragm valve 21 designed as a check valve between the crankcase 4 and the inlet window 16.
- the volume of the channels 15 close to the outlet is expediently larger, in particular several times larger than the volume of the channels 12 remote from the outlet corresponds approximately to the overflow volume of air flowing from the duct 15 into the combustion chamber 3 during a gas change.
- the volume of the channel section is preferably greater than the overflow volume, in order to ensure that essentially only air flows in during the entire duration of a gas change, that is to say the opening time of the inlet window 16.
- the piston 5 controls - in a known manner - the inlet 11, the outlet 10 and the inlet windows 13 and 16 of the transfer Flow channels 12 and 15. With an upward movement of the piston 5, all channels opening into the combustion chamber 3 are closed, while the inlet 11 of the mixture preparation device 8 is opened towards the crankcase 4. Due to the upward-moving piston 5, a negative pressure is created in the crankcase 4, which is compensated for by suction of a fuel / air mixture via the inlet 11. Since the channels 15 to the crankcase 4 are advantageously open, the negative pressure present in the crankcase 4 simultaneously causes air to be sucked in via the air intake ports 20 and the diaphragm valves 21 which are now open due to the pressure conditions.
- the large-volume, near-outlet channels 15 fill completely with air, whereby with increasing pressure equalization in the crankcase, the diaphragm valves 21 close and a further inflow of air is prevented. There is now essentially pure air in the volumes of the channels 15 near the outlet.
- the piston 5 After the ignition in the area of the top dead center in the combustion chamber 3, the piston 5 will travel downwards by the explosion pressure towards the crankcase 4, whereby - due to the position of the inlet windows 13 and 16 - the outlet 10 is first opened and part of the bottom Exhaust gases under pressure flow out. With a further downward movement of the piston 5, the inlet windows 13 and 16 of the channels 12 and 15 open, in the exemplary embodiment simultaneously, with only fuel / air mixture flowing in via the overflow channels 12.
- a partial cylinder development and the piston 5 of a multi-channel engine are shown in a schematic representation.
- the combustion chamber 3 of the cylinder 2 has an outlet 10 and overflow channels 12 and 15 on both sides of the axis of symmetry 14.
- the inlet channel 9 opens into the crankcase 4 via the inlet 11. All the windows lying in the cylinder wall 44 are slot-controlled by the piston 5.
- an auxiliary window 50 is provided in the cylinder wall 44, the height of which is clearly below the outlet 10.
- the auxiliary window 50 is therefore completely in the piston path, that is to say the auxiliary window 50 is covered by the piston jacket 30 in every position of the piston 5.
- the auxiliary window 50 lies in the circumferential direction of the cylinder wall 44 between the outlet 10 and the overflow channel 15; other layers can also be advantageous.
- An approximately Z-shaped U-shaped groove 31 is formed in the piston skirt 30 of the piston 5, which extends in the circumferential direction over an angle 32 which corresponds to the maximum distance of the vertical edges of the extension measured in the circumferential direction.
- window 16 of the air channel 15 and the auxiliary window 50 corresponds (Fig. 5).
- the auxiliary channel 49 adjoining the auxiliary window 50 near the outlet is designed to be smaller in volume than the overflow channel 15 in the exemplary embodiment according to FIGS. 4 to 7.
- the auxiliary window 50 of the auxiliary channel 49 near the outlet is accordingly smaller than the inlet window 16 of the overflow channel 15.
- the auxiliary channel 49 is connected to the air intake 20 which supplies pure air. The connection is expediently provided so that there is no throttling of the air flowing into the duct 15 near the outlet.
- the connecting channel in the piston skirt 30 designed as a circumferential groove 31 connects the air-supplying auxiliary window 50 of the auxiliary channel 49 to the inlet window 16 of the outlet-side overflow channel 15 connected to the crankcase 4 approximately at the top dead center TDC of the piston 5.
- the auxiliary channels 49 are opposite the crankcase 4 is closed and can be connected, for example, to a pressure accumulator 24 according to FIG. 4, so that at top dead center TDC air enters through the auxiliary channel 49 and the auxiliary window 50 into the circumferential groove 31 and from there via the inlet window 16 into the overflow channel 15 streams.
- the volumetric overflow duct 15 thus fills itself completely from the combustion chamber 3 in the direction of the crankcase 4 with pure air, so that - when the piston 5 moves down towards bottom dead center UT - that from the crankcase 4 into the overflow duct 15 overflowing fuel / air mixture the channel volume is preceded by pure air. Since on the way to the bottom dead center UT the connection between the channels 49 and 15 is first interrupted and the downward channel 5 leads to an increase in pressure in the crankcase 4, this is also carried out in the overflow channel 12. stored air volume compressed. When the inlet window 16 of the overflow channels 15 is opened, the compressed air therefore enters the combustion chamber 3 under pressure and displaces the exhaust gases from the combustion chamber 3.
- the Z-shaped connecting channel 31 provided in the piston skirt 30 for air storage is designed such that the inlet windows 16 and 50 open into the circumferential groove 31 over their entire cross-section, that is to say a restriction in the passage of air from the air intake 20 to the overflow channel 15 is largely avoided.
- the air pre-storage in an overflow channel 15 leading from the crankcase 4 to the combustion chamber is explained in FIGS. 4 to 7 using the example of a four-channel engine.
- the inventive idea of storing clean air in the direction of the combustion chamber 3 in an overflow channel can be used in the same way for a total of three, five or more overflow channels, the channels near the outlet supplying the combustion chamber with clean air during the entire gas exchange.
- the piston 5 advantageously has a plurality of circumferential grooves 31 in order to store air in each channel near the outlet. Two circumferential grooves 31 are expediently provided, one of which lies on a longitudinal side of the axis of symmetry 14.
- auxiliary channels 49 are connected to the clean air side of an air filter, the auxiliary channel 49 is connected to the overflow channel 15 at a point in time when vacuum is present in the crankcase. Then the crankcase 4 Via the overflow channel 15, the connecting channel 31 and the auxiliary channel 49, pure air is sucked in, which is upstream in the overflow channel 15.
- the air intake connector 20 is connected to a pressure accumulator 24, which is constantly charged during operation of the internal combustion engine 1 via an air pump which is advantageously designed as a diaphragm pump 25.
- the diaphragm pump 25 is driven by the fluctuating crankcase pressure;
- the working space 26 of the pump 25 is connected to the crankcase 4.
- the pump chamber 27 is connected to an air intake line via a suction valve 28 designed as a non-return valve and to the pressure accumulator 24 via a pressure valve 29 also designed as a non-return valve.
- the inlet 11, the outlet 10 and the inlet windows 13 and 16 of the channels 12 and 15 are controlled by the piston 5 or its piston skirt 30.
- a control valve 33 in the air-guiding channel 15, the mixture-guiding overflow channel 12 and / or the inlet channel 9, which can be actuated differently from the position of the piston 5.
- a valve member 34 is in one Valve housing 35 provided.
- the valve member 34 is provided as a valve slide which is acted upon by the crankcase pressure on its end face 36.
- the valve member 34 is acted upon by force in the blocking position shown in FIG. 9.
- a spring 37 is arranged on the side opposite the end face 36, against the force of which the valve member 34 can be displaced into the release division.
- the spring preload is expediently adjustable, the spring 37 being a helical spring loaded under tension.
- an orifice ring 40 is arranged on the mixture preparation device in the flow direction in front of the venturi section 38, which has an inner circumferential groove 39 from which the air line 41 branches off.
- the circumferential groove 39 is partially circular in cross section, preferably with a circumferential angle of approximately 270 °.
- the air line 41 can be connected directly to the air intake 20 of the channels 15 near the outlet.
- a throttle valve 46 is arranged, which are advantageously coupled to one another in a manner that is not shown in detail, via adjusting levers 47.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE50003096T DE50003096D1 (de) | 1999-01-08 | 2000-01-07 | Zweitaktmotor mit ladungsschichtung |
EP00902568A EP1141529B1 (de) | 1999-01-08 | 2000-01-07 | Zweitaktmotor mit ladungsschichtung |
US09/889,065 US6571756B1 (en) | 1999-01-08 | 2000-01-07 | Two-cycle engine with a stratified charge |
JP2000592526A JP2002534630A (ja) | 1999-01-08 | 2000-01-07 | 成層給気を用いた2サイクル機関 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19900445.5 | 1999-01-08 | ||
DE19900445A DE19900445A1 (de) | 1999-01-08 | 1999-01-08 | Zweitaktmotor mit Spülvorlage |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000040843A1 true WO2000040843A1 (de) | 2000-07-13 |
Family
ID=7893776
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2000/000067 WO2000040843A1 (de) | 1999-01-08 | 2000-01-07 | Zweitaktmotor mit ladungsschichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US6571756B1 (de) |
EP (1) | EP1141529B1 (de) |
JP (1) | JP2002534630A (de) |
DE (2) | DE19900445A1 (de) |
WO (1) | WO2000040843A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2391263A (en) * | 2002-07-30 | 2004-02-04 | Julian George Daniel Branston | Reciprocating piston engine |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10139700B4 (de) | 2000-10-11 | 2013-01-03 | Andreas Stihl Ag & Co. | Verbrennungsmotor als Antriebsmotor in einem tragbaren, handgeführten Arbeitsgerät |
DE10064719B4 (de) * | 2000-12-22 | 2013-12-12 | Andreas Stihl Ag & Co. | Zweitaktmotor mit Ladungsschichtung |
DE10104445A1 (de) | 2001-02-01 | 2002-08-08 | Stihl Maschf Andreas | Verbrennungsmotor mit Membranvergaser und einstellbarem CO |
DE10104446A1 (de) | 2001-02-01 | 2002-08-08 | Stihl Maschf Andreas | Verbrennungsmotor mit einstellbarer CO-Kennlinie |
DE60108886D1 (de) * | 2001-11-21 | 2005-03-17 | Morini Franco Motori S P A | Verbesserte Zweitakt-Brennkraftmaschine |
DE10160539B4 (de) | 2001-12-10 | 2017-06-08 | Andreas Stihl Ag & Co. | Zweitaktmotor mit Spülvorlage und einflutigem Vergaser |
DE10201967A1 (de) | 2002-01-19 | 2003-07-31 | Stihl Maschf Andreas | Zweitaktmotor mit Spülvorlage |
FR2840019B1 (fr) * | 2002-05-24 | 2005-08-19 | Stihl Ag & Co Kg Andreas | Moteur a deux temps, avec piston mobile, a balayage ameliore |
DE10223070B4 (de) * | 2002-05-24 | 2015-10-08 | Andreas Stihl Ag & Co. | Zweitaktmotor |
DE10223069A1 (de) * | 2002-05-24 | 2003-12-11 | Stihl Maschf Andreas | Zweitaktmotor |
DE10241213A1 (de) * | 2002-09-06 | 2004-03-18 | Andreas Stihl Ag & Co. | Verfahren zum Betrieb eines Zweitaktmotors mit Gemischansaugung |
DE10341230B4 (de) * | 2003-09-08 | 2022-10-13 | Andreas Stihl Ag & Co. Kg | Ansaugvorrichtung |
DE10349641A1 (de) * | 2003-10-24 | 2005-05-19 | Man Nutzfahrzeuge Ag | Motorstaubremsvorrichtung einer 4-Takt-Hubkolbenbrennkraftmaschine |
US7021252B2 (en) * | 2004-03-04 | 2006-04-04 | Electrolux Home Products, Inc. | Sas piston channel for optimum air scavenging |
DE102005014575A1 (de) * | 2005-03-31 | 2006-10-05 | Andreas Stihl Ag & Co. Kg | Verbrennungsmotor mit Spülvorlage |
US7267326B2 (en) * | 2005-05-05 | 2007-09-11 | Tecumseh Products Company | Automatic priming system |
JP4606966B2 (ja) * | 2005-08-05 | 2011-01-05 | 株式会社やまびこ | 層状掃気2サイクル内燃エンジン |
JP4309418B2 (ja) * | 2006-10-27 | 2009-08-05 | 株式会社共立 | 2サイクル内燃エンジン |
US9938926B2 (en) * | 2014-10-07 | 2018-04-10 | Yamabiko Corporation | Air leading-type stratified scavenging two-stroke internal-combustion engine |
JP6549031B2 (ja) * | 2015-12-21 | 2019-07-24 | 株式会社やまびこ | 空気先導式2ストローク空冷エンジン |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2151941A1 (de) * | 1971-10-19 | 1973-04-26 | Blume Geb Schroedet Helga | Gemischspuelung mit spuelvorlage |
DE2650834A1 (de) * | 1975-12-22 | 1977-06-30 | Thaelmann Fahrzeug Jagdwaffen | Gemischgespuelte zweitakt-brennkraftmaschine |
US4075985A (en) * | 1975-06-20 | 1978-02-28 | Yamaha Hatsudoki Kabushiki Kaisha | Two cycle internal combustion engines |
GB2022699A (en) * | 1978-05-12 | 1979-12-19 | Univ Belfast | A crankcase scavenged two-stroke internal combustion engine |
JPS57183520A (en) * | 1981-05-06 | 1982-11-11 | Isao Oda | Device for preventing mixture from blowing through two-cycle engine |
US4481911A (en) * | 1983-12-29 | 1984-11-13 | Brunswick Corporation | Stratified-charge cross-flow scavenged two-stroke cycle engine |
JPS6196129A (ja) * | 1984-10-16 | 1986-05-14 | Nippon Clean Engine Res | 2サイクル内燃機関 |
DE3722424A1 (de) * | 1986-07-08 | 1988-01-14 | Bombardier Rotax Gmbh | Zweitakt-brennkraftmaschine mit einer kurbelkastenspuelung |
AT397837B (de) * | 1988-03-21 | 1994-07-25 | Yamaha Motor Europ | Zweitakt-brennkraftmaschine mit kurbelgehäusespülung |
US5425346A (en) * | 1993-09-14 | 1995-06-20 | Mavinahally; Nagesh S. | Performance improvement design for two-stroke engines |
WO1998017902A1 (fr) * | 1996-10-17 | 1998-04-30 | Komatsu Zenoah Co. | Moteur a deux cycles, a balayage et a charges stratifiees |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4000723A (en) * | 1972-08-22 | 1977-01-04 | Performance Industries, Inc. | Engine valve means and porting |
DE4219955B4 (de) * | 1992-06-18 | 2007-01-04 | Fa. Andreas Stihl | Zweitaktbrennkraftmaschine für Motorkettensägen |
-
1999
- 1999-01-08 DE DE19900445A patent/DE19900445A1/de not_active Ceased
-
2000
- 2000-01-07 WO PCT/EP2000/000067 patent/WO2000040843A1/de active IP Right Grant
- 2000-01-07 JP JP2000592526A patent/JP2002534630A/ja active Pending
- 2000-01-07 DE DE50003096T patent/DE50003096D1/de not_active Expired - Lifetime
- 2000-01-07 US US09/889,065 patent/US6571756B1/en not_active Expired - Lifetime
- 2000-01-07 EP EP00902568A patent/EP1141529B1/de not_active Expired - Lifetime
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2151941A1 (de) * | 1971-10-19 | 1973-04-26 | Blume Geb Schroedet Helga | Gemischspuelung mit spuelvorlage |
US4075985A (en) * | 1975-06-20 | 1978-02-28 | Yamaha Hatsudoki Kabushiki Kaisha | Two cycle internal combustion engines |
DE2650834A1 (de) * | 1975-12-22 | 1977-06-30 | Thaelmann Fahrzeug Jagdwaffen | Gemischgespuelte zweitakt-brennkraftmaschine |
GB2022699A (en) * | 1978-05-12 | 1979-12-19 | Univ Belfast | A crankcase scavenged two-stroke internal combustion engine |
JPS57183520A (en) * | 1981-05-06 | 1982-11-11 | Isao Oda | Device for preventing mixture from blowing through two-cycle engine |
US4481911A (en) * | 1983-12-29 | 1984-11-13 | Brunswick Corporation | Stratified-charge cross-flow scavenged two-stroke cycle engine |
JPS6196129A (ja) * | 1984-10-16 | 1986-05-14 | Nippon Clean Engine Res | 2サイクル内燃機関 |
DE3722424A1 (de) * | 1986-07-08 | 1988-01-14 | Bombardier Rotax Gmbh | Zweitakt-brennkraftmaschine mit einer kurbelkastenspuelung |
AT397837B (de) * | 1988-03-21 | 1994-07-25 | Yamaha Motor Europ | Zweitakt-brennkraftmaschine mit kurbelgehäusespülung |
US5425346A (en) * | 1993-09-14 | 1995-06-20 | Mavinahally; Nagesh S. | Performance improvement design for two-stroke engines |
WO1998017902A1 (fr) * | 1996-10-17 | 1998-04-30 | Komatsu Zenoah Co. | Moteur a deux cycles, a balayage et a charges stratifiees |
Non-Patent Citations (2)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 10, no. 273 (M - 518) 17 September 1986 (1986-09-17) * |
PATENT ABSTRACTS OF JAPAN vol. 7, no. 29 (M - 191)<1174> 5 February 1983 (1983-02-05) * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2391263A (en) * | 2002-07-30 | 2004-02-04 | Julian George Daniel Branston | Reciprocating piston engine |
Also Published As
Publication number | Publication date |
---|---|
DE19900445A1 (de) | 2000-07-13 |
JP2002534630A (ja) | 2002-10-15 |
EP1141529B1 (de) | 2003-07-30 |
US6571756B1 (en) | 2003-06-03 |
EP1141529A1 (de) | 2001-10-10 |
DE50003096D1 (de) | 2003-09-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1141529B1 (de) | Zweitaktmotor mit ladungsschichtung | |
DE10160539B4 (de) | Zweitaktmotor mit Spülvorlage und einflutigem Vergaser | |
DE69917345T2 (de) | Vergaser für Zweitaktbrennkraftmaschinen | |
DE10197237B4 (de) | Motor mit innerer Verbrennung und Kurbelgehäusespülung | |
DE2850809C2 (de) | Zweitakt-Otto-Brennkraftmaschine | |
DE102009030593B4 (de) | Vergaser und Zweitaktmotor mit einem Vergaser | |
DE19860391A1 (de) | Tragbares Arbeitsgerät mit einem Viertaktmotor | |
DE102007051171A1 (de) | Zweitakt-Verbrennungsmotor | |
EP3284938B1 (de) | Kolben für einen mit spülvorlage arbeitenden zweitaktmotor und zweitaktmotor | |
DE2308127B2 (de) | Zweitakt-Brennkraftmaschine mit zwei bzw. drei Kompressionsräumen | |
DE10139700A1 (de) | Verbrennungsmotor als Antriebsmotor in einem tragbaren, handgeführten Arbeitsgerät | |
DE10064719B4 (de) | Zweitaktmotor mit Ladungsschichtung | |
DE10041547A1 (de) | Zweitaktmotor mit belüftetem Überströmkanal | |
DE102007054929B4 (de) | Handgeführtes Arbeitsgerät | |
DE10321571A1 (de) | Zweitaktmotor mit Spülvorlage | |
DE10241213A1 (de) | Verfahren zum Betrieb eines Zweitaktmotors mit Gemischansaugung | |
DE102006001570B4 (de) | Arbeitsgerät | |
DE10009796B4 (de) | Verbrennungsmotor mit im Luftfiltergehäuse angeordneter Chokeklappe | |
DE102010045017B4 (de) | Zweitaktmotor | |
DE102005019520A1 (de) | Zylinder für einen Zweitaktmotor | |
WO2003100229A1 (de) | Zweitaktmotor | |
DE10211404A1 (de) | Tragbares, handgeführtes Arbeitsgerät | |
DE19804639B4 (de) | Zweitakt-Verbrennungsmotor | |
DE10104446A1 (de) | Verbrennungsmotor mit einstellbarer CO-Kennlinie | |
DE10319216B4 (de) | Zweitaktmotor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): JP US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2000902568 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref country code: JP Ref document number: 2000 592526 Kind code of ref document: A Format of ref document f/p: F |
|
WWE | Wipo information: entry into national phase |
Ref document number: 09889065 Country of ref document: US |
|
WWP | Wipo information: published in national office |
Ref document number: 2000902568 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 2000902568 Country of ref document: EP |