EP0971110A1 - Zweitaktmotor mit schichtspülung - Google Patents

Zweitaktmotor mit schichtspülung Download PDF

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Publication number
EP0971110A1
EP0971110A1 EP98944286A EP98944286A EP0971110A1 EP 0971110 A1 EP0971110 A1 EP 0971110A1 EP 98944286 A EP98944286 A EP 98944286A EP 98944286 A EP98944286 A EP 98944286A EP 0971110 A1 EP0971110 A1 EP 0971110A1
Authority
EP
European Patent Office
Prior art keywords
flow passage
scavenging
mixture
air
crank chamber
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.)
Withdrawn
Application number
EP98944286A
Other languages
English (en)
French (fr)
Other versions
EP0971110A4 (de
Inventor
Toshiharu Komatsu Zenoah Co. SAWADA
Masanori Komatsu Zenoah Co. NOGUCHI
Buhei Komatsu Zenoah Co. KOBAYASHI
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.)
Komatsu Zenoah Co
Japan Petroleum Energy Center JPEC
Original Assignee
Petroleum Energy Center PEC
Komatsu Zenoah Co
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
Application filed by Petroleum Energy Center PEC, Komatsu Zenoah Co filed Critical Petroleum Energy Center PEC
Publication of EP0971110A1 publication Critical patent/EP0971110A1/de
Publication of EP0971110A4 publication Critical patent/EP0971110A4/de
Withdrawn legal-status Critical Current

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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
    • F02B25/14—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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • 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

  • the present invention relates to a stratified scavenging two-cycle engine and, more particularly, to a stratified scavenging two-cycle engine which includes an air supply flow passage for supplying air and a mixture supply flow passage for supplying mixture separately and conducts the purification of exhaust gas by setting the ratio of flow rates flowing through the two flow passages at a predetermined ratio.
  • Japanese Utility Model Publication No. 55-4518 is proposed.
  • a variable valve is provided, the variable valve making an extremely small quantity of air including zero flow in a state of low rotation and low load operation of an engine and increasing a flow rate of air in states other than the aforesaid operation state.
  • aforesaid air supply quantity is zero or very small at the time of low rotation and low load operation of the engine, thus preventing excessive rarefaction of fuel mixture, eliminating poor ignition, and stabilizing combustion operation.
  • the aforesaid air supply quantity into the cylinder increases at the time of low rotation and low load operation of the engine, thus effectively fulfilling the aforesaid operation of preventing blow-by of mixture.
  • Japanese Laid-open Patent No. 58-5423 is proposed.
  • a crank chamber compression two-cycle internal combustion engine has an exhaust port and a scavenging port in a wall on the side of a cylinder, and the exhaust port and the scavenging port are opened and closed by a wall on the side of a piston. Air is sucked into a scavenging flow passage connected to the scavenging port through an air supply flow passage due to negative pressure in the crank chamber, and sucked air is fed into the cylinder prior to fuel mixture which is sent from the crank chamber at the beginning of a scavenging stroke in which the scavenging port is opened.
  • the scavenging port is not opened to the crank chamber by the wall on the piston side even at an lower dead center, and that the scavenging flow passage connected to the scavenging port is at least more than twice as long as that of the conventional crank chamber compression two-cycle internal combustion engine.
  • the total volume of the scavenging port and the scavenging flow passage is designed to be 20 % or more of stroke volume.
  • the quantity of an initial scavenge which is not mixed with fuel mixture in a crankcase can be selected so as to be optimum value according to the volume of the scavenging flow passage.
  • liquid fuel such as gasoline or the like
  • a large quantity of liquid fuel adhering to the wall surface of the scavenging flow passage evaporates by high speed flow of sucked air accompanied by pulsation, is mixed in the initial part of scavenge and blown to exhaust with scavenge, thereby significantly reducing the stratified scavenging effect of this system. It is described, however, that the use of fuel gas almost prevents mixing of fuel into sucked air in the scavenging flow passage.
  • the quantity of air supply is zero or very small at the time of low rotation and low load operation of the engine, thus preventing excessive rarefaction of fuel mixture, eliminating poor ignition, and stabilizing combustion operation.
  • the aforesaid quantity of air supply into the cylinder increases at the time of low rotation and low load operation of the engine, thus effectively fulfilling the aforesaid operation of preventing blow-by of mixture.
  • a demand for purification of exhaust gas is increasing more and more, emission regulation is tightened up, and purification of exhaust gas at the time of the whole range of rotation of the engine as well as at the time of low rotation and low load operation of the engine is desired.
  • THC total hydrocarbon
  • the scavenging flow, passage is designed to be at least more than twice as long as that of the conventional crank chamber compression two-cycle internal combustion engine, and the total volume of the scavenging port and the scavenging flow passage is designed to be 20 % or more of stroke volume.
  • this is an art applied only to fuel gas. In the use of fuel gas, blow-by is prevented.
  • an object of the present invention is to provide a stratified scavenging two-cycle engine which includes an air supply flow passage for supplying air and a mixture supply flow passage for supplying mixture separately and whose simple configuration can satisfy the regulation of emission rate of THC in exhaust gas by setting the ratio of flow rates flowing through the two flow passages at a predetermined ratio.
  • pressure in the crank chamber becomes negative with upward movement of the piston, and pressure in the scavenging flow passage connected to the crank chamber and pressure in the air supply flow passage also become negative.
  • air is sucked into the scavenging flow passage connected with the check valve in the air supply flow passage and the crank chamber, and hence a predetermined quantity of fresh air is supplied.
  • mixture to which fuel is supplied through the mixture supply passage is sucked into the crank chamber, and thus a predetermined quantity of mixture is supplied to the crank chamber.
  • the supply quantity ratio R of the supply quantity qa of air supplied to the scavenging flow passage and the crank chamber to the supply quantity Qf of mixture supplied to the crank chamber is set to be 0.7 ⁇ R ⁇ 1.4, and more preferably 0.8 ⁇ R ⁇ 1.2.
  • the supply quantity ratio R supplied to the cylinder is less than 0.7, blow-by of fuel to the exhaust port increases, thereby deteriorating the THC emission rate.
  • the supply quantity ratio R supplied to the cylinder is more than 1.4, the time when mixture in the crank chamber flows into a cylinder chamber is delayed and the ratio of fuel in mixture inside the crank chamber needs to be increased.
  • the second aspect of a stratified scavenging two-cycle engine according to the present invention is characterized in that in a stratified scavenging two-cycle engine including a piston, a cylinder housing the piston to be vertically slidable and having an exhaust port and a scavenging port in a side wall, a crankcase connected to the cylinder, a scavenging flow passage for connection between a crank chamber provided in the crankcase and the scavenging port, an air supply flow passage connected to the scavenging flow passage and supplying air through a check valve, and a mixture supply flow passage supplying mixture, to which fuel from a fuel supply means is supplied, to the crank chamber, the scavenging flow passage is provided in the cylinder, or in the cylinder and the crankcase, and volume Vs of the scavenging flow passage from an end portion on the crank chamber side to the check valve in the air supply flow passage is 70 % or more of a supply quantity qa of air flowing through the air supply flow passage
  • Liquid fuel adhering to the scavenging flow passage is taken into the crank chamber with fresh air which is early sucked into the scavenging flow passage. Therefore, it is confirmed that liquid fuel taken into the cylinder chamber from the scavenging flow passage at the beginning of a scavenging stroke decreases, whereby blow-by to exhaust with scavenge reduces and the emission rate of THC in exhaust gas exhausted from the stratified scavenging two-cycle engine is not more than 40 [g / HP ⁇ h].
  • a configuration is suitable in which a predetermined quantity of fresh air is supplied to the scavenging flow passage and the crank chamber during a suction stroke in which pressure in the crank chamber is negative, a predetermined quantity of mixture to which fuel is supplied is supplied to the crank chamber, the supply quantity ratio R is 0.7 ⁇ R ⁇ 1.4 and more preferably 0.8 ⁇ R ⁇ 1.2, and the scavenging flow passage volume Vs is 70 % or more and more preferably 80 % or more of the air supply quantity qa at full load rated power engine speed.
  • blow-by of fuel reduces and uniform mixture is formed in the cylinder, thus raising combustion efficiency. Since pressure in the crank chamber becomes negative with upward movement of the piston, a predetermined quantity of fresh air is supplied to the scavenging flow passage and fresh air also enters the crank chamber. Therefore, liquid fuel adhering to the scavenging flow passage is taken into the crank chamber and fresh air in the scavenging flow passage pushes out combustion gas in the cylinder chamber, whereby the inside of the cylinder chamber is filled with the remnant of the fresh air and mixture and blow-by of fuel is reduced.
  • the scavenging flow passage volume Vs is 70 % or more and more preferably 80 % or more of the air supply quantity qa, mixture in the crank chamber uniformly enters the cylinder chamber, thus improving combustion efficiency. Contrary to this, if the scavenging flow passage volume Vs is not more than 70 %, the air supply quantity qa is excessively mixed with mixture in the crank chamber, thereby increasing blow-by of fuel to the exhaust port and deteriorating the THC emission rate. It is confirmed from the aforesaid results that the emission rate of THC in emitted exhaust gas is not more than 50 [g / HP ⁇ h] if the scavenging flow passage volume Vs is 70 % or more.
  • Fig. 1 shows the entire configuration of the stratified scavenging two-cycle engine 1.
  • a piston 2 is tightly housed in a cylinder 4 so as to be vertically slidable.
  • a crankcase 6 is connected to the underside of the cylinder 4, and a crank chamber 8 is formed in the crankcase 6.
  • a cylinder head 10 is connected to the upside of the cylinder 4.
  • the piston 2, the cylinder 4, and the cylinder head 10 form a cylinder chamber 12 to which mixture is fed to burn and explode.
  • an exhaust port 14 for exhausting combustion gas after combustion and explosion and a scavenging port 16 for supplying air to the cylinder chamber 12 at the beginning of a scavenging stroke and supplying mixture thereto after combustion gas is pressed out.
  • the scavenging port 16 is disposed opposite the exhaust port 14 and three scavenging ports in all are disposed in a circumferential direction.
  • the exhaust port 14 is connected to a silencer 34 with an exhaust pipe 18, and the combustion gas is exhausted as exhaust gas from the silencer 34 into the atmosphere.
  • the scavenging port 16 is connected to the crankcase 6 through a scavenging flow passage 22.
  • three scavenging flow passages 22 are provided in the cylinder 4 and the crankcase 6.
  • the scavenging flow passage 22 of this embodiment is composed of a flow passage 22a provided in the cylinder 4 and a port 22b.
  • the port 22b is connected to the flow passage 22a in the cylinder 4 and surrounded by a slot provided in the crankcase 6 and the cylinder 4 extending downward.
  • the scavenging flow passage 22 may be formed only by the cylinder 4.
  • An air supply flow passage 24 is connected to the scavenging flow passage 22 for connection between the cylinder 4 and the crankcase 6. Disposed in a connecting portion 24a of the scavenging flow passage 22 and the air supply flow passage 24 is a check valve 26 which permits the air flow from the air supply flow passage 24 to the scavenging flow passage 22 and impedes the reverse flow.
  • the connecting portion 24a is connected to the upper portion shown of the scavenging flow passage 22 so that the scavenging flow passage 22 can be filled with supplied air.
  • Scavenging flow passage volume Vs formed in the scavenging flow passage 22 of the present invention consists of the volume surrounded by the flow passage 22a in the cylinder 4, the port 22b enclosed by the slot provided in the crankcase 6 and the cylinder 4 extending downward, and the check valve 26 formed in the air supply flow passage 24.
  • the check valve 26 is disposed in the connecting portion 24a in the aforesaid embodiment, but may be disposed in the air supply flow passage 24.
  • An air flow rate control valve may be provided to control a suction flow rate of air to be sucked in the air supply flow passage 24, although the drawing thereof is omitted.
  • a crank 28 is rotatably housed through a connecting rod 29 connected to the piston 2 and the crank chamber 8 is formed.
  • a mixture supply port 8a to which a mixture supply flow passage 20 is connected.
  • a fuel supply system 30 for supplying liquid fuel such as gasoline or the like to form air-fuel mixture is provided.
  • a check valve 32 Disposed in a connecting portion of the mixture supply flow passage 20 and the crank chamber 8 is a check valve 32 for mixture which permits only the flow from the mixture supply flow passage 20 to the crank chamber 8 and impedes the reverse flow.
  • an air cleaner which is not shown is disposed at the uppermost stream of the mixture supply flow passage 20.
  • a predetermined quantity of fresh air is supplied to the scavenging flow passage 22 and the nearby crank chamber 8 connected to the scavenging flow passage 22, and moreover a predetermined quantity of mixture, to which fuel is supplied, is supplied to the crank chamber 8.
  • the suction stroke is generally a period from a lower dead center to an upper dead center. In the stratified scavenging two-cycle engine 1, however, even when the piston 2 passes the upper dead center and starts to descend, pressure in the crank chamber 8 is negative and thus air and fuel are sucked into the crank chamber 8.
  • the supply quantity ratio R is 0.8 ⁇ R ⁇ 1.2.
  • scavenging flow passage volume Vs [cm 3 ] of the scavenging flow passage 22 is 70 % or more of the air supply quantity qa [cm 3 ].
  • the air supply flow passage 24 is filled with air which is supplied thereafter, and the communication portion of the scavenging flow passage 22 at the upper portion in the crank chamber 8 is also filled with air.
  • the scavenging flow passage volume Vs is 80 % or more of the air supply quantity qa.
  • the ratio of the sectional area of the air supply flow passage 24 through which air passes to the sectional area of the mixture supply flow passage 20 through which mixture passes is set so that the aforesaid range can be obtained.
  • it is possible to obtain the aforesaid range by controlling an air flow rate control valve which is not shown and a mixture flow rate control valve provided in the fuel supply system 30.
  • crank chamber 8 and the scavenging flow passage 22 are pressurized so that air stored in the scavenging flow passage 22 is jetted from the scavenging port 16 into the cylinder chamber 12 and combustion gas remaining in the cylinder chamber 12 is forcibly exhausted from the exhaust port 14 by air. Thereafter, mixture in the crank chamber 8 goes into the cylinder chamber 12 from the scavenging port 16 through the scavenging flow passage 22, thus completing scavenge and preparing for next combustion and explosion.
  • the inside of the cylinder 12 can be scavenged by a predetermined quantity of air stored in the scavenging flow passage 22, which enables great decrease in blow-by in a scavenging stroke of mixture. Consequently there is an advantage that exhaust gas is made clearer.
  • a full line Pa shows the THC emission rate relative to the supply quantity ratio R when the scavenging flow passage volume Vs [cm 3 ] is 100 % of the air supply quantity qa [cm 3 ].
  • a broken line Ma shows the THC emission rate relative to the supply quantity ratio R when the scavenging flow passage volume Vs [cm 3 ] is 60 % of the air supply quantity qa [cm 3 ].
  • a full line Sa shows the THC emission rate relative to the scavenging flow passage volume ratio S.
  • Fig. 6 shows a second embodiment of the stratified scavenging two-cycle engine 1 of the present invention.
  • the mixture supply flow passage 20 is connected to the crank chamber 8 in the first embodiment shown in Fig. 1, while a mixture supply flow passage 35 is connected to the cylinder chamber 12 in the second embodiment. Opening and closing of the mixture supply flow passage 35 is conducted by upward and downward movement of the piston 2. It is confirmed that it is effective also in the stratified scavenging engine 1 in the second embodiment as is the case with the first embodiment.
  • the present invention is useful as a stratified scavenging two-cycle engine whose simple configuration can satisfy the regulation of emission rate of THC in exhaust gas.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Supercharger (AREA)
EP98944286A 1997-10-03 1998-09-29 Zweitaktmotor mit schichtspülung Withdrawn EP0971110A4 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP28783097A JPH11107761A (ja) 1997-10-03 1997-10-03 層状掃気２サイクルエンジン
JP28783097 1997-10-03
PCT/JP1998/004360 WO1999018338A1 (fr) 1997-10-03 1998-09-29 Moteur a deux temps a balayage stratifie

Publications (2)

Publication Number Publication Date
EP0971110A1 true EP0971110A1 (de) 2000-01-12
EP0971110A4 EP0971110A4 (de) 2000-09-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98944286A Withdrawn EP0971110A4 (de) 1997-10-03 1998-09-29 Zweitaktmotor mit schichtspülung

Country Status (4)

Country Link
EP (1) EP0971110A4 (de)
JP (1) JPH11107761A (de)
AU (1) AU9186898A (de)
WO (1) WO1999018338A1 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2810693A1 (fr) * 2000-06-24 2001-12-28 Stihl Maschf Andreas Moteur a deux temps a alimentation primaire de balayage
FR2840021A1 (fr) * 2002-05-24 2003-11-28 Stihl Ag & Co Kg Andreas Moteur a deux temps commande par fente avec balayage prealable
US6668770B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke interal combustion engine
US6668771B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6708958B1 (en) 2002-10-04 2004-03-23 Electrolux Home Products, Inc. Air valve mechanism for two-cycle engine
US6712029B1 (en) 1999-01-19 2004-03-30 Lars Andersson Cylinder for an internal combustion engine
US6718917B2 (en) 2000-04-27 2004-04-13 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6848399B2 (en) 2003-05-30 2005-02-01 Electrolux Home Products, Inc. Scavenging insert for an engine
US6877723B2 (en) 2000-01-14 2005-04-12 Aktiebolaget Electrolux Valve for control of additional air for a two-stroke engine
US6957633B2 (en) 2003-08-11 2005-10-25 Zama Japan Carburetor for two-cycle engine
US7082910B2 (en) 1999-01-19 2006-08-01 Aktiebolaget Electrolux Two-stroke internal combustion engine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001098934A (ja) 1999-10-04 2001-04-10 Komatsu Zenoah Co 触媒付層状掃気２サイクルエンジン
DE10009621A1 (de) * 2000-03-01 2001-09-06 Stihl Maschf Andreas Zweiaktmotor mit Ladungsschichtung
RU2466281C1 (ru) 2008-09-24 2012-11-10 Макита Корпорейшн Двухтактный двигатель с послойной продувкой
JP5922569B2 (ja) 2012-12-28 2016-05-24 株式会社マキタ 層状掃気２ストロークエンジン

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075985A (en) * 1975-06-20 1978-02-28 Yamaha Hatsudoki Kabushiki Kaisha Two cycle internal combustion engines
JPS57183520A (en) * 1981-05-06 1982-11-11 Isao Oda Device for preventing mixture from blowing through two-cycle engine
DE4007466A1 (de) * 1990-03-09 1991-02-14 Franz Josef Knott Spuel- und schmierverfahren fuer hubkolbenmotoren
FR2678682A1 (fr) * 1991-07-03 1993-01-08 Thery Georges Pompe alternative d'alimentation, notamment d'un moteur deux temps et moteur auquel elle est associee.
DE19520944A1 (de) * 1995-06-05 1996-01-11 Seebeck Norbert Dipl Ing Luftspülung für Verbrennungsmotoren
JPH09125966A (ja) * 1995-10-27 1997-05-13 Komatsu Zenoah Co 層状掃気２サイクルエンジン

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5819304Y2 (ja) * 1975-06-14 1983-04-20 スズキ株式会社 ２ サイクルエンジン
JPS5382615U (de) * 1976-12-11 1978-07-08
JPS554518U (de) 1978-06-23 1980-01-12
JPS585423A (ja) 1981-06-30 1983-01-12 Nippon Clean Engine Res クランク室圧縮２サイクル内燃機関
JPS6153520U (de) * 1984-09-11 1986-04-10
JPS61147330U (de) * 1985-03-06 1986-09-11
JP3024072B2 (ja) * 1996-10-17 2000-03-21 財団法人石油産業活性化センター 層状掃気２サイクルエンジン

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075985A (en) * 1975-06-20 1978-02-28 Yamaha Hatsudoki Kabushiki Kaisha Two cycle internal combustion engines
JPS57183520A (en) * 1981-05-06 1982-11-11 Isao Oda Device for preventing mixture from blowing through two-cycle engine
DE4007466A1 (de) * 1990-03-09 1991-02-14 Franz Josef Knott Spuel- und schmierverfahren fuer hubkolbenmotoren
FR2678682A1 (fr) * 1991-07-03 1993-01-08 Thery Georges Pompe alternative d'alimentation, notamment d'un moteur deux temps et moteur auquel elle est associee.
DE19520944A1 (de) * 1995-06-05 1996-01-11 Seebeck Norbert Dipl Ing Luftspülung für Verbrennungsmotoren
JPH09125966A (ja) * 1995-10-27 1997-05-13 Komatsu Zenoah Co 層状掃気２サイクルエンジン

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 007, no. 029 (M-191), 5 February 1983 (1983-02-05) & JP 57 183520 A (ISAO ODA), 11 November 1982 (1982-11-11) *
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 09, 30 September 1997 (1997-09-30) -& JP 09 125966 A (KOMATSU ZENOAH CO), 13 May 1997 (1997-05-13) *
See also references of WO9918338A1 *

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6712029B1 (en) 1999-01-19 2004-03-30 Lars Andersson Cylinder for an internal combustion engine
US7574984B2 (en) 1999-01-19 2009-08-18 Husqvarna Ab Two-stroke internal combustion engine
US7082910B2 (en) 1999-01-19 2006-08-01 Aktiebolaget Electrolux Two-stroke internal combustion engine
US7025021B1 (en) 1999-01-19 2006-04-11 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6668771B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6877723B2 (en) 2000-01-14 2005-04-12 Aktiebolaget Electrolux Valve for control of additional air for a two-stroke engine
US6668770B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke interal combustion engine
US6718917B2 (en) 2000-04-27 2004-04-13 Aktiebolaget Electrolux Two-stroke internal combustion engine
FR2810693A1 (fr) * 2000-06-24 2001-12-28 Stihl Maschf Andreas Moteur a deux temps a alimentation primaire de balayage
US6513466B2 (en) 2000-06-24 2003-02-04 Andreas Stihl Ag & Co. Two-stroke engine
DE10030969B4 (de) * 2000-06-24 2014-07-03 Andreas Stihl Ag & Co Zweitaktmotor mit Spülvorlage
US6880503B2 (en) 2002-05-24 2005-04-19 Andreas Stihl Ag & Co. Kg Port-controlled two-cycle engine having scavenging
FR2840021A1 (fr) * 2002-05-24 2003-11-28 Stihl Ag & Co Kg Andreas Moteur a deux temps commande par fente avec balayage prealable
US6708958B1 (en) 2002-10-04 2004-03-23 Electrolux Home Products, Inc. Air valve mechanism for two-cycle engine
US6848399B2 (en) 2003-05-30 2005-02-01 Electrolux Home Products, Inc. Scavenging insert for an engine
US6957633B2 (en) 2003-08-11 2005-10-25 Zama Japan Carburetor for two-cycle engine
US7377496B2 (en) 2003-08-11 2008-05-27 Zama Japan Kabushiki Kaisha Carburetor for two-cycle engine

Also Published As

Publication number Publication date
EP0971110A4 (de) 2000-09-06
WO1999018338A1 (fr) 1999-04-15
JPH11107761A (ja) 1999-04-20
AU9186898A (en) 1999-04-27

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