EP0337768A2 - Brennkraftmaschine - Google Patents

Brennkraftmaschine Download PDF

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Publication number
EP0337768A2
EP0337768A2 EP89303626A EP89303626A EP0337768A2 EP 0337768 A2 EP0337768 A2 EP 0337768A2 EP 89303626 A EP89303626 A EP 89303626A EP 89303626 A EP89303626 A EP 89303626A EP 0337768 A2 EP0337768 A2 EP 0337768A2
Authority
EP
European Patent Office
Prior art keywords
air
piston
engine according
cylinder
port
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Withdrawn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
EP89303626A
Other languages
English (en)
French (fr)
Other versions
EP0337768A3 (de
Inventor
Robert John Tait
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0337768A2 publication Critical patent/EP0337768A2/de
Publication of EP0337768A3 publication Critical patent/EP0337768A3/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Withdrawn legal-status Critical Current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
    • F02B25/20—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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/04—Engines with reciprocating-piston pumps; Engines with crankcase pumps with simple crankcase pumps, i.e. with the rear face of a non-stepped working piston acting as sole pumping member in co-operation with the crankcase
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • F02B33/10—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
    • F02B33/12—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder the rear face of working piston acting as pumping member and co-operating with a pumping chamber isolated from crankcase, the connecting-rod passing through the chamber and co-operating with movable isolating member
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/28—Component parts, details or accessories of crankcase pumps, not provided for in, or of interest apart from, subgroups F02B33/02 - F02B33/26
    • F02B33/30—Control of inlet or outlet ports
    • 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 invention relates to an internal combustion engine of the reciprocating piston type.
  • Two stroke cycle internal combustion engines have been proposed hitherto comprising first and second cylinders in which respective first and second portions of a piston are reciprocable.
  • Such pistons are known as “duplex pistons”.
  • An engine utilising a duplex piston arrangement is known from an article entitled “Top Hat Piston Cleans Up Two Stroke Power” appearing in "The Engineer” dated 6th September 1979.
  • An object of the present invention is to provide an improved internal combustion engine of the duplex piston type.
  • a two stroke internal combustion engine including first and second cylinders in which respective first and second portions of a duplex piston are reciprocable, one only of said cylinders being a combustion cylinder, wherein the piston portions are co-axial and one piston portion lies partially within the other.
  • the piston has a common crown and co-axial depending skirts.
  • the outer cylinder is the combustion cylinder.
  • the engine comprises inner and outer cylinders in which respective first and second portions of the duplex piston are reciprocable whereby movement of the piston in one axial direction will cause said first and second portions of the piston to transfer charges in respective first and second chambers of the engine to a combustion cylinder of the engine.
  • the charge in one said chamber may be an air/fuel mixture whilst the charge in the other chamber may be air.
  • exhaust from the combustion chamber passes through an exhaust port which is uncovered by the piston in advance of ports leading from said first and second chambers during a power stroke of the engine.
  • a port leading from the chamber containing air opens shortly before a further port leading from the chamber containing the fuel and air mixture.
  • a buffer volume of air is introduced between the outgoing exhaust gases and the incoming fresh charge of fuel and air from said other chamber.
  • the first and second cylinders overlap in the axial direction, the overlap of the cylinders being around 90% of the piston stroke.
  • the inner portion of the piston is preferably spaced from the outer and a cylinder defining section of the engine may extend into the space to form a cylinder for the inner portion of the piston.
  • An outer cylinder defining section of the engine is arranged spaced from the inner cylinder defining section to form a cylinder for the outer portion of the piston.
  • the outer portion of the piston preferably extends into a space between the outer and inner cylinder defining sections of the engine.
  • the inner cylinder is defined by the crankcase and the outer cylinder is defined by the cylinder head.
  • the inner cylinder section also defines at least part of a first chamber for receiving a charge which is transferred to the combustion cylinder during use.
  • the space between the inner and outer cylinder defining sections may define a second chamber for receiving a charge which is transferred to the combustion cylinder during use.
  • the first chamber may include part of the crank case of the engine into which may be drawn a charge comprising the aforesaid air/fuel mixture; a charge of air may be drawn into the second chamber during use.
  • the inner cylinder defining section may include an opening therein which communicates with one or more transfer passages in the engine for transferring the charge from the first chamber to the combustion cylinder.
  • the upward movement of the piston will create suction in both chambers the suction in the chambers being different, preferably the suction in the second chamber and also its compression ratio will be higher than the first chamber.
  • Non-return valve means may be provided in an inlet for air/fuel mixture and preferably in a further inlet for air.
  • Such valve means may be of the reed-­valve type.
  • the engine may include a plurality of pistons arranged in respective cylinders.
  • an internal combustion engine comprising first and second cylinders in which respective first and second portions of a duplex piston are reciprocable, the engine including a combustion chamber having therein respective ports through which exhaust gas passes and through which first and second incoming charges, at least one of which comprises a mixture of air and fuel, can enter the combustion chamber as a result of movement of the piston in said cylinders.
  • the exhaust is preferably opened before the other ports.
  • the next port to open is preferably the port through which the charge of air is delivered.
  • the port through which air is delivered is preferably uncovered slightly before the port through which the charge of air/fuel mixture is delivered.
  • the air/fuel charge and the air charge are drawn sequentially into one of the chambers so that on transfer to the combustion cylinder, the air charge is released first followed by the air/fuel mixture.
  • the buffer of air helps to scavenge the combustion cylinder of exhaust gases and prevents unburnt fuel from passing to exhaust.
  • a single transfer passage or set of passages connects the charge chamber to the combustion cylinder and a plurality of transfer ports may be provided; no air ports are necessary in this embodiment.
  • the space between the first and second piston portions is connected to the source of air/fuel mixture and the transfer passage is connected to a source of air.
  • the invention also encompasses a duplex piston for a two stroke internal combustion engine in which the piston has reciprocable first and second portions, the portions being co-axial and lying partially one within the other.
  • the piston has a common crown and co-axial depending skirts.
  • the engine comprises a crankcase 10 rotatably supporting a crankshaft 12 in bearings 13.
  • the crankshaft is sealed against the crankcase by means of oil seals 14.
  • the crankcase has an inlet 15 provided with a reed-­valve 16.
  • the inlet 15 is connected to a carburettor (not shown).
  • the crankcase 10 is formed with an upstanding tubular section 17 having an inner bore defining a first cylinder 18.
  • the crankcase is formed with a passage 19 which extends through the tubular section 17 to form an orifice 20 therein.
  • the lower portion of tubular section 17 as viewed in the drawings is formed with a tapered lead-in 22.
  • the upper outer edge of the tubular section 17 is formed with a chamfer 23.
  • the crankcase is formed with a cylindrical register surface 24 which spigotally locates a cylinder head 25.
  • a seal between the cylinder head and crank case may be achieved by using a gasket between a base surface 26 on the crankcase and an adjacent surface 27 on the cylinder head 25.
  • the cylinder head defines a second cylinder 28 which is co-axial with cylinder 18. It will be noted that the cylinder 28 and the cylinder 18 overlap axially by approximately 90% of piston stroke (the piston being described below).
  • the cylinder head is formed with an inlet passage 29 for air.
  • the inlet passage 29 is provided with a reed-valve 30 and communicates through passages 31 with two air inlet ports 32.
  • the cylinder head is formed with passages 33 which at their upper end communicate with two transfer ports 34 for a mixture of fuel and air transferred from the crankcase.
  • the passage 19 and passages 33 together form transfer passages indicated generally at 35.
  • the cylinder head is formed with an exhaust outlet 36 leading from an exhaust port 37 in the cylinder 28.
  • the usual spark plug 38 is provided and the cylinder head is formed with galleries 39 for cooling water.
  • the cylinder head defines a combustion chamber 51.
  • the crankshaft 12 has the big end of a connecting rod 40 mounted on its throw 42 through needle roller bearings 43.
  • the little end of the connecting rod is rotatably connected to a gudgeon pin 44 through needle roller bearings 45.
  • the gudgeon pin is mounted in bosses 46 formed on a first piston portion 47 of a duplex piston 48.
  • the first portion 47 of the piston 48 fits slidably in the first cylinder 18 and is formed with a window 41 (Fig.2) which enables the interior of the crankcase 10 and the transfer passage 35 to communicate during reciprocation of the piston.
  • the piston 48 also includes a second portion 49 which fits slidably within the second cylinder 28. It will be noted that the first portion 47 of the piston lies coaxially within the second portion 49 so as to define an annular chamber 50 therebetween which has a substantially toroidal upper end 52 as viewed in Figs.1 and 2.
  • the tubular section 17 of the crankcase extends into the annular space 50.
  • the wall of second piston portion 49 is cut away as indicated at 54 so that the passages 31 can communicate with the annular space 50.
  • the second portion 49 of the piston 48 carries two piston rings 55, 56, the upper piston ring being of L-shaped cross-section as shown.
  • the descending piston causes the air in annular chamber 50 to pass to the inlets 32 via passages 31 and into the combustion chamber 51.
  • the combustion chamber 51 is, therefore, occupied by air from inlets 32 and an air/fuel mixture from inlets 34.
  • the piston then passes the bottom dead centre position and begins to move upwardly eventually covering ports 32, 34 and exhaust port 37.
  • the charge in the combustion chamber is compressed as the piston moves towards its top dead centre position and slightly in advance of top dead centre the spark plug 38 produces spark to ignite the mixture.
  • the piston passes top dead centre and is forced downwardly by the expanding gases. As the piston begins to uncover exhaust port 37, exhaust gases pass into the exhaust outlet 36.
  • Incoming air again passes through inlets 32 due to the descending piston so as to begin scavenging the combustion chamber followed by introduction of the air/fuel mixture through transfer ports 34 to provide a fresh charge in the combustion chamber 51.
  • the incoming air forms a buffer between the air/fuel mixture entering through transfer ports 34 and helps to provide a cleaner environment within the combustion chamber for subsequent combustion.
  • the amounts of air and air/fuel mixture entering the engine through the inlet passages 15 and 29 are controlled by the respective reed-valves 16 and 30.
  • the engine can be made shorter and more compact than the engine which is described in the aforementioned article in "The Engineer".
  • the carburettor could feed air/fuel mixture to ports 29 whereas air alone would be drawn in through inlet 15; the ports 37,32,34 would be re-arranged to ensure the buffer of air between exhaust and unburnt mixture, and transfer ports 34 would be arranged to open slightly after inlet ports 32 during descent of the piston.
  • FIG. 4 and 5 A second preferred embodiment is shown in Figs 4 and 5 which correspond to Figs 2 and 1 of the first embodiment.
  • the crankcase is not used for charge compression and the crankshaft and connecting rod assembly may therefore be lubricated under pressure according to normal four-­stroke practice using dry or wet sump methods.
  • the second embodiment has an inlet tract 61 for the passage of air/fuel mixture from a carburettor (not shown), through a reed valve 62 to an inlet port 63.
  • An exhaust port 64 opens into an exhaust tract 65 as before.
  • Transfer passages 66 connect the toroidal second chamber 67 with transfer ports 68 opening into the cylinder bore. Also opening into passages 66 are air inlets 69 normally closed by reed valves 70. In operation, as the piston approaches top dead centre, the air/fuel mixture will be drawn into the second chamber 67. At the same time reed valves 70 will open to allow air to be drawn into the transfer passages 66.
  • Oil may be sprayed on the walls of the inner piston bore to give lubrication and cooling; oil control rings 71 may be fitted to the skirt of the inner piston portion 72 to wipe off any excess.
  • the rings 71 will help keep exhaust gases and combustion productions out of the crankcase and sump. Any exhaust gases which pass the rings 74 of the working piston 73 will recirculate with the next fresh charge and therefore not contaminate oil in the crankcase/ sump.

Landscapes

  • 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)
EP89303626A 1988-04-14 1989-04-12 Brennkraftmaschine Withdrawn EP0337768A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB888808855A GB8808855D0 (en) 1988-04-14 1988-04-14 I c engine
GB8808855 1988-04-14

Publications (2)

Publication Number Publication Date
EP0337768A2 true EP0337768A2 (de) 1989-10-18
EP0337768A3 EP0337768A3 (de) 1990-04-25

Family

ID=10635202

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89303626A Withdrawn EP0337768A3 (de) 1988-04-14 1989-04-12 Brennkraftmaschine

Country Status (2)

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EP (1) EP0337768A3 (de)
GB (1) GB8808855D0 (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4030116A1 (de) * 1990-09-23 1992-03-26 Koepke Guenter Dr Ing Zweitaktbrennkraftmaschine
GB2246168B (en) * 1989-03-18 1993-08-18 Bernard Hooper Internal combustion engine
WO1998029648A1 (en) * 1996-12-31 1998-07-09 Douglas Ayres Internal combustion engines utilizing variable compression complete unit charge air/fuel injection or transference
EP0916822A3 (de) * 1997-11-18 2000-01-26 Toshiji Kishita Luftgesteuerte Zweitakt Brennkraftmaschine
WO2000043660A1 (en) * 1999-01-19 2000-07-27 Aktiebolaget Electrolux Cylinder for internal combustion engine
WO2001051783A1 (en) * 2000-01-14 2001-07-19 Aktiebolaget Electrolux Two-stroke internal combustion engine
WO2001051785A1 (en) * 2000-01-14 2001-07-19 Aktiebolaget Electrolux Two-stroke internal combustion engine
WO2001051784A1 (en) * 2000-01-14 2001-07-19 Aktiebolaget Electrolux Two-stroke internal combustion engine
WO2001081739A1 (en) * 2000-04-27 2001-11-01 Aktiebolaget Electrolux Two-stroke internal combustion engine
FR2840019A1 (fr) * 2002-05-24 2003-11-28 Stihl Ag & Co Kg Andreas Moteur a deux temps, avec piston mobile, a balayage ameliore
US6877723B2 (en) 2000-01-14 2005-04-12 Aktiebolaget Electrolux Valve for control of additional air for a two-stroke engine
US7082910B2 (en) 1999-01-19 2006-08-01 Aktiebolaget Electrolux Two-stroke internal combustion engine
CN1328488C (zh) * 2002-04-24 2007-07-25 安德烈亚斯斯蒂尔股份两合公司 二冲程发动机
EP2327864A1 (de) * 2008-09-24 2011-06-01 Makita Corporation Zweitaktmotor mit schichtspülung
US9206736B2 (en) 2012-12-28 2015-12-08 Makita Corporation Stratified scavenging two-stroke engine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR340142A (fr) * 1904-02-03 1904-06-27 Auguste Eugene Brillie Moteur à deux temps
CH152982A (de) * 1930-11-17 1932-02-29 Sollers Hans Zweitaktexplosionsmotor mit Vergaser und Kurbelkastenladepumpe.
DE659313C (de) * 1935-10-19 1938-04-30 Oswald Kuhnast Zweitaktbrennkraftmaschine
DE2943496A1 (de) * 1978-12-13 1980-06-26 Zschopau Motorrad Veb Zweitakt-brennkraftmaschine mit kurbelgehaeusepumpe
EP0020806A1 (de) * 1979-06-29 1981-01-07 Christian Vialette Dreitaktmotor
JPS60108530A (ja) * 1983-11-17 1985-06-14 Iwao Maeyama ２サイクルエンジン
US4598673A (en) * 1985-02-06 1986-07-08 Outboard Marine Corporation Air-scavenged two-cycle internal combustion engine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR340142A (fr) * 1904-02-03 1904-06-27 Auguste Eugene Brillie Moteur à deux temps
CH152982A (de) * 1930-11-17 1932-02-29 Sollers Hans Zweitaktexplosionsmotor mit Vergaser und Kurbelkastenladepumpe.
DE659313C (de) * 1935-10-19 1938-04-30 Oswald Kuhnast Zweitaktbrennkraftmaschine
DE2943496A1 (de) * 1978-12-13 1980-06-26 Zschopau Motorrad Veb Zweitakt-brennkraftmaschine mit kurbelgehaeusepumpe
EP0020806A1 (de) * 1979-06-29 1981-01-07 Christian Vialette Dreitaktmotor
JPS60108530A (ja) * 1983-11-17 1985-06-14 Iwao Maeyama ２サイクルエンジン
US4598673A (en) * 1985-02-06 1986-07-08 Outboard Marine Corporation Air-scavenged two-cycle internal combustion engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 261 (M-422)(1984) 18 October 1985, & JP-A-60 108530 (IWAO MAEYAMA) 14 June 1985, *

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2246168B (en) * 1989-03-18 1993-08-18 Bernard Hooper Internal combustion engine
DE4030116A1 (de) * 1990-09-23 1992-03-26 Koepke Guenter Dr Ing Zweitaktbrennkraftmaschine
WO1998029648A1 (en) * 1996-12-31 1998-07-09 Douglas Ayres Internal combustion engines utilizing variable compression complete unit charge air/fuel injection or transference
EP0916822A3 (de) * 1997-11-18 2000-01-26 Toshiji Kishita Luftgesteuerte Zweitakt Brennkraftmaschine
US6135072A (en) * 1997-11-18 2000-10-24 Kishita; Toshiji Air regulated two cycle engine
US6712029B1 (en) 1999-01-19 2004-03-30 Lars Andersson Cylinder for an internal combustion engine
WO2000043660A1 (en) * 1999-01-19 2000-07-27 Aktiebolaget Electrolux Cylinder for 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
WO2001051785A1 (en) * 2000-01-14 2001-07-19 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
US6668771B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6668770B2 (en) 2000-01-14 2003-12-30 Aktiebolaget Electrolux Two-stroke interal combustion engine
WO2001051783A1 (en) * 2000-01-14 2001-07-19 Aktiebolaget Electrolux Two-stroke internal combustion engine
WO2001051784A1 (en) * 2000-01-14 2001-07-19 Aktiebolaget Electrolux Two-stroke internal combustion engine
US6718917B2 (en) 2000-04-27 2004-04-13 Aktiebolaget Electrolux Two-stroke internal combustion engine
WO2001081739A1 (en) * 2000-04-27 2001-11-01 Aktiebolaget Electrolux Two-stroke internal combustion engine
CN100386511C (zh) * 2000-04-27 2008-05-07 哈斯科瓦那股份公司 两冲程内燃机
CN1328488C (zh) * 2002-04-24 2007-07-25 安德烈亚斯斯蒂尔股份两合公司 二冲程发动机
US6945203B2 (en) 2002-05-24 2005-09-20 Andreas Stihl Ag & Co Kg Two-cycle engine
WO2003100229A1 (de) * 2002-05-24 2003-12-04 Andreas Stihl Ag & Co. Kg Zweitaktmotor
FR2840019A1 (fr) * 2002-05-24 2003-11-28 Stihl Ag & Co Kg Andreas Moteur a deux temps, avec piston mobile, a balayage ameliore
EP2327864A1 (de) * 2008-09-24 2011-06-01 Makita Corporation Zweitaktmotor mit schichtspülung
EP2327864A4 (de) * 2008-09-24 2011-12-14 Makita Corp Zweitaktmotor mit schichtspülung
US8770159B2 (en) 2008-09-24 2014-07-08 Makita Corporation Stratified scavenging two-stroke engine
US9249716B2 (en) 2008-09-24 2016-02-02 Makita Corporation Stratified scavenging two-stroke engine
US9206736B2 (en) 2012-12-28 2015-12-08 Makita Corporation Stratified scavenging two-stroke engine
US9869235B2 (en) 2012-12-28 2018-01-16 Makita Corporation Stratified scavenging two-stroke engine

Also Published As

Publication number Publication date
GB8808855D0 (en) 1988-05-18
EP0337768A3 (de) 1990-04-25

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