NO314553B1 - Device for 4-stroke internal combustion engine - Google Patents
Device for 4-stroke internal combustion engine Download PDFInfo
- Publication number
- NO314553B1 NO314553B1 NO20014040A NO20014040A NO314553B1 NO 314553 B1 NO314553 B1 NO 314553B1 NO 20014040 A NO20014040 A NO 20014040A NO 20014040 A NO20014040 A NO 20014040A NO 314553 B1 NO314553 B1 NO 314553B1
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- Norway
- Prior art keywords
- piston
- valve
- intake
- cylinder
- stroke
- Prior art date
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- 238000002485 combustion reaction Methods 0.000 title claims description 13
- 239000000446 fuel Substances 0.000 claims description 12
- 239000000203 mixture Substances 0.000 claims description 8
- 239000000567 combustion gas Substances 0.000 claims description 5
- 235000014676 Phragmites communis Nutrition 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 210000002105 tongue Anatomy 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 238000011010 flushing procedure Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 229920000271 Kevlar® Polymers 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000004761 kevlar Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 239000000523 sample Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
- F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
- F01L3/205—Reed valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
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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
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
-
- 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
-
- 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
- F02B2720/00—Engines with liquid fuel
- F02B2720/22—Four stroke engines
- F02B2720/226—Four stroke engines with measures for improving combustion
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
Foreliggende oppfinnelse vedrører en anordning ved en 4-takt forbrenningsmotor som angitt i innledningen til patentkravet. The present invention relates to a device for a 4-stroke internal combustion engine as stated in the introduction to the patent claim.
En forbrenningsmotor av den nevnte type er en varmekraftmaskin hvor forbrenningen av en brennstoffblanding foregår i en sylinder. Varmeenergien omsettes til mekanisk arbeid ved at forbrenningsgassens trykk virker på et bevegelig stempel i sylinderen- Stemplet har en rettlinjet vekslende bevegelse, som overføres til en roterende bevegelse ved hjelp av en veivmekanisme. Akselen i veivmekanismen er også motorens energiuttak. An internal combustion engine of the aforementioned type is a thermal power machine where the combustion of a fuel mixture takes place in a cylinder. The heat energy is converted into mechanical work by the pressure of the combustion gas acting on a moving piston in the cylinder - The piston has a rectilinear alternating movement, which is transferred to a rotating movement by means of a crank mechanism. The shaft in the crank mechanism is also the engine's energy outlet.
Prosessene inne i sylinderen foregår i serier, som omfatter luft- og brennstoffitlførsel, kompresjon, forbrenning, ekspansjon og utstøting av forbrenningsgass. Hvert stempelslag i serien representerer en takt. Forbrenningsmotorene inndeles etter takttypen, nemlig 2-takt og 4-takt-motorer. Som nevnt vedrører oppfinnelsen 4-takt-motorer. The processes inside the cylinder take place in series, which include air and fuel intake, compression, combustion, expansion and expulsion of combustion gas. Each piston stroke in the series represents a measure. Internal combustion engines are divided according to stroke type, namely 2-stroke and 4-stroke engines. As mentioned, the invention relates to 4-stroke engines.
For inntak og utstøting av henholdsvis brennstoffblanding og forbrenningsgass i 4-takt-motorer er det anordnet ventilstyrte topplaserte eller sideplasserte inntaks- og utstøtsporter eller -åpninger i sylinderen. For intake and exhaust respectively of fuel mixture and combustion gas in 4-stroke engines, there are valve-controlled top lasered or side-located intake and exhaust ports or openings in the cylinder.
Inntaksventiler og utstøtsventiler styres med en ventilstyring. Slike ventilstyringer innbefatter kamaksler som virker direkte eller indirekte (løftestenger) på ventilene. Kamakselen/e drives fra motorakselen. Intake valves and exhaust valves are controlled with a valve control. Such valve controls include camshafts that act directly or indirectly (lift rods) on the valves. The camshaft(s) are driven from the engine shaft.
Det finnes en rekke avanserte ventilstyringer, men felles for disse er at de krever et relativt stort antall komponenter og at ventilene er utsatt for store påkjenninger med tilhørende slitasje. Plassen i en sylinder setter også grenser for ventilportenes størrelse, idet man eksempelvis ved topplaserte ventiler bare har et begrenset areal (sylinderflaten) til rådighet. Sideplasserte ventiler gir bedre plassforhold, men felles for alle ventilarrangementer er at kamaksel, ventilfjærer, ventilstyringer etc er plasskrevende og er beheftet med indre friksjon. Særlig ventilfjærene virker turtallbegrensende. Et problem er også varmeutvikling og vibrasjoner. There are a number of advanced valve controls, but what these have in common is that they require a relatively large number of components and that the valves are exposed to great stress with associated wear and tear. The space in a cylinder also sets limits for the size of the valve ports, as, for example, with top lasered valves, you only have a limited area (the cylinder surface) at your disposal. Side-placed valves provide better space, but common to all valve arrangements is that camshafts, valve springs, valve guides etc take up space and are subject to internal friction. The valve springs in particular act as rev limiters. Heat generation and vibrations are also a problem.
Fra US 4331118 er det kjent en 4-takt motor med en tilbakeslagsventil i form av en bladtungeventil i en inntaksåpning som er anordnet i sylinderveggen og vekselvis dekkes av stempelet. From US 4331118, a 4-stroke engine is known with a non-return valve in the form of a reed valve in an intake opening which is arranged in the cylinder wall and alternately covered by the piston.
Fra EP 382063 Al er det kjent en 2-takt motor hvor det er anordnet en dreieventil i utløpsåpningen i tillegg til den vanlige utløpsåpningen i sylinderveggen. Dreieventilen er anordnet under stempelringområdet på stempelet når stempelet er i stempelets øvre dødpunkt. From EP 382063 Al, a 2-stroke engine is known where a rotary valve is arranged in the outlet opening in addition to the usual outlet opening in the cylinder wall. The rotary valve is arranged under the piston ring area of the piston when the piston is at the top dead center of the piston.
Fra DE 4118254 Al er det kjent bruk av en dreieventil i forbindelse med en 2-takt motor. From DE 4118254 Al the use of a rotary valve in connection with a 2-stroke engine is known.
Hensikten med foreliggende oppfinnelse er å tilveiebringe en 4-takt motor som er lettere (mindre vekt), kan gjøres mindre (mer kompakt) og kan produseres billigere enn hittil kjente 4-takt-motorer. The purpose of the present invention is to provide a 4-stroke engine which is lighter (less weight), can be made smaller (more compact) and can be produced more cheaply than previously known 4-stroke engines.
Ifølge oppfinnelsen foreslås det derfor en anordning som definert i patentkravet. According to the invention, a device as defined in the patent claim is therefore proposed.
Det skal nevnes at stempelstyrte porter er kjent for 2-takt-motorer og likeledes er det kjent å bruke tilbakeslagsventiler, også i form av bladventiler, i 2-taktmotorer, i innsugings-/spylesystemet. Disse kjente tilbakeslagsventiler inngår imidlertid som nevnt i det spylesystem som er typisk nettopp for 2-taktmotorer, hvor veivhuset utnyttes som blandekammer for luft og brennstoff før denne går inn i sylinderrommet over stempelet, idet tilbakeslagsventilen da lukker mot forgasseren. It should be mentioned that piston-operated gates are known for 2-stroke engines and it is likewise known to use non-return valves, also in the form of leaf valves, in 2-stroke engines, in the intake/flushing system. However, as mentioned, these known non-return valves are included in the flushing system which is typical precisely for 2-stroke engines, where the crankcase is used as a mixing chamber for air and fuel before this enters the cylinder space above the piston, as the non-return valve then closes against the carburettor.
Oppfinnelsen tilveiebringer en 4-takt motor med færre mekanisk drevne deler. Motoren vil derfor arbeide med mindre friksjon (energiforbruk) enn de kjente 4-takt motorer. Færre mekanisk drevne deler og mindre friksjon gir høyere effekt og lavere drivstofforbruk. The invention provides a 4-stroke engine with fewer mechanically driven parts. The engine will therefore work with less friction (energy consumption) than the known 4-stroke engines. Fewer mechanically driven parts and less friction result in higher power and lower fuel consumption.
Spesielle trekk ved oppfinnelsen og dens fordeler vil bli belyst nærmere nedenfor, i forbindelse med en beskrivelse av et utførelseseksempel av oppfinnelsen, under henvisning til tegningene hvor Figur la-e rent skjematisk viser en anordning ifølge oppfinnelsen og dens virkemåte, og Special features of the invention and its advantages will be elucidated in more detail below, in connection with a description of an embodiment of the invention, with reference to the drawings where Figure la-e schematically shows a device according to the invention and its mode of operation, and
Figur 2 viser et utsnitt av det øvre motorområde, i større målestokk. Figure 2 shows a section of the upper engine area, on a larger scale.
De bare rent skjematiske figurer viser bare de for forståelse av oppfinnelsen vesentlige deler. Ikke viste detaljer er velkjente for fagmannen og skiller seg ikke fra for 4-takt forbrenningsmotorer anvendte konstruktive detaljer. The purely schematic figures only show the essential parts for understanding the invention. Details not shown are well known to the person skilled in the art and do not differ from constructive details used for 4-stroke internal combustion engines.
I figur 1 er det vist en 4-takt forbrenningsmotor som innbefatter en sylinder 1, et veivhus 2 og et topplokk 3.1 sylinderen 1 er det anordnet et resiproserbart stempel 4, som med en veivstang 5 er forbundet med den i veivhuset 2 opplagrede veivaksel 6, på tegningen antydet med en sirkel. Et inntak for brennstoffblanding er antydet ved 7, og en utstøtventil er antydet ved 8. Figure 1 shows a 4-stroke internal combustion engine which includes a cylinder 1, a crankcase 2 and a cylinder head 3. 1 cylinder 1 is fitted with a reciprocating piston 4, which is connected by a crank rod 5 to the crankshaft 6 stored in the crankcase 2, in the drawing indicated by a circle. An intake for fuel mixture is indicated at 7, and an exhaust valve is indicated at 8.
I topplokket 3 er det her bare antydet en åpning 9 for plassering av en tennplugg/glødeelement (ikke vist). In the cylinder head 3, an opening 9 for the placement of a spark plug/glowing element (not shown) is only indicated here.
Den viste forbrenningsmotor arbeider på kjent måte for en 4-takt motor: I et inntaksslag The internal combustion engine shown works in a known way for a 4-stroke engine: In an intake stroke
trekker veivmekanismen stempelet fra topp- til bunnstilling. Luft og brennstoff suges da inn gjennom inntaket. I den neste takt, kompresjonsslaget, presser veivmekanismen stempelet fra bunn- til toppstilling. Inntaksventilen er stengt og brennstoffblandingen komprimeres. I tredje takt, arbeidsslaget, vil den antente brennstoffblanding utvide seg og presse stempelet fra toppstilling til bunnstilling. Like før slutten av slaget åpner utstøtventilen. I fjerde takt, utstøtsslaget, fører veivmekanismen stempelet fra bunnstillingen til toppstillingen. Utstøtventilen er åpen. Forbrenningsgassen skyves da ut av sylinderen. Deretter følger nytt inntaksslag osv. the crank mechanism pulls the piston from top to bottom position. Air and fuel are then sucked in through the intake. In the next stroke, the compression stroke, the crank mechanism pushes the piston from bottom to top position. The intake valve is closed and the fuel mixture is compressed. In the third stroke, the working stroke, the ignited fuel mixture will expand and push the piston from top position to bottom position. Just before the end of the stroke, the exhaust valve opens. In the fourth stroke, the exhaust stroke, the crank mechanism moves the piston from the bottom position to the top position. The exhaust valve is open. The combustion gas is then pushed out of the cylinder. This is followed by a new intake stroke, etc.
Ifølge oppfinnelsen har motoren et nytt og fordelaktig inntakssystem 7. According to the invention, the engine has a new and advantageous intake system 7.
I sylinderveggen i sylinderen 1 er det utformet en åpning eller port 10, se særlig figur 2. Denne port 10 er gjennom en her bare antydet kanal 11 forbundet med en forgasser (ikke vist). I kanalen/porten 10/11 er det anordnet en tilbakeslagsventil 12, i form av to bladtunger 13 og 14, som samvirker med et ventilsete 15. An opening or port 10 is formed in the cylinder wall of cylinder 1, see in particular figure 2. This port 10 is connected to a carburettor (not shown) through a channel 11 only indicated here. In the channel/port 10/11, a non-return valve 12 is arranged, in the form of two blade tongues 13 and 14, which cooperates with a valve seat 15.
Utstøtsventilen 8 er i utførelseseksempelet i form av en dreieventil, med et dreielegeme 16 som har en diametral kanal 17, som kan bringes til flukt med en utstøtsport 18 i sylinderen 1 og en eksosledning 19. Dreielegemet 16 roterer med veivakselen ved hjelp av en her ikke vist tannrem, med et overføringsforhold 1:4. Dreieventilen, dvs. dreielegemet 16 går således med halve turtallet av en vanlig kamaksel. Fordelen med en slik dreieventil ligger bl. a. i det reduserte turtall, med mindre spenninger i og lengre levetid for tannremmen. The exhaust valve 8 is in the design example in the form of a rotary valve, with a rotary body 16 which has a diametrical channel 17, which can be brought flush with an exhaust port 18 in the cylinder 1 and an exhaust line 19. The rotary body 16 rotates with the crankshaft by means of a timing belt shown, with a transmission ratio of 1:4. The rotary valve, i.e. the rotary body 16, thus runs at half the speed of a normal camshaft. The advantage of such a rotary valve is, among other things, a. in the reduced speed, with less tension in and longer service life for the toothed belt.
Slike dreieventiler er kjent brukt i motorer og dreieventilen i seg selv representerer derfor ingen nyhet. Dens plassering i sylinderveggen, under stempelets tetningsringer 20 i stempelets 4 øvre stilling, medfører imidlertid en vesentlig fordel. Den avsluttende kompresjon og eksplosjon (forbrenning) skjer da nemlig mot topplokket 3 og mot stempelet 4, og ikke direkte mot dreieventilen 9,16. Inntaksventilen 7 vil heller ikke påvirkes, da den er plassert i sylinderveggen, under stempelringområdet 12 i det begynnende arbeidsslag. Such rotary valves are known to be used in engines and the rotary valve in itself therefore does not represent anything new. However, its location in the cylinder wall, below the piston's sealing rings 20 in the upper position of the piston 4, entails a significant advantage. The final compression and explosion (combustion) then takes place namely against the cylinder head 3 and against the piston 4, and not directly against the rotary valve 9,16. The intake valve 7 will not be affected either, as it is located in the cylinder wall, below the piston ring area 12 in the beginning working stroke.
Tetningsringene 20, dvs. stempelfjærer og oljefjæren, låses (ikke vist) slik at fjæråpningene ikke kommer i portene 10,18 når stempelet 4 passerer disse. The sealing rings 20, i.e. the piston springs and the oil spring, are locked (not shown) so that the spring openings do not enter the ports 10,18 when the piston 4 passes through them.
Virkemåten til den nye anordning ifølge oppfinnelsen skal nå forklares nærmere, under henvisning til figurene. The operation of the new device according to the invention will now be explained in more detail, with reference to the figures.
I figur la er stempelet 4 vist på vei ned i arbeidsslaget. Utstøtsventilen 8 er lukket. Inntaksventilen 7 er også lukket, idet bladtungene 13,14 er i anlegg mot ventilsetet 15 og stempelet også dekker inntaksporten 10. Derved hindres inntak av olje fra veivhuset. In figure la, the piston 4 is shown on its way down in the working stroke. Exhaust valve 8 is closed. The intake valve 7 is also closed, as the blade tongues 13,14 are in contact with the valve seat 15 and the piston also covers the intake port 10. This prevents intake of oil from the crankcase.
I figur lb er stempelet 4 på vei opp i utstøtslaget, etter å ha passert nedre dødpunkt. Utstøtsventilen 8 er åpen. Inntaksventilen 7 er fortsatt lukket. In Figure 1b, the piston 4 is on its way up the exhaust stroke, after passing bottom dead center. Exhaust valve 8 is open. The intake valve 7 is still closed.
I figur lc er stempelet 4 på vei ned i innsugingsslaget. Så vel utstøtventil 8 som inntaksventil 7 er stengt. I figur Id er stempelet 4 vist i nedre dødpunkt, i avsluttet innsugningsslag. Inntaksventilen 7 er åpen, den åpner seg så snart undertrykket i sylinderrommet kommer til virkning, ved stempelets 4 begynnende avdekking av porten 10, idet bladtungene da svinger ut fra setet 15. Brennstoffblanding strømmer inn i sylinderen 1 over stempelet 4. In Figure 1c, the piston 4 is on its way down in the intake stroke. Both exhaust valve 8 and intake valve 7 are closed. In figure Id, the piston 4 is shown at bottom dead center, at the end of the intake stroke. The intake valve 7 is open, it opens as soon as the negative pressure in the cylinder space takes effect, when the piston 4 begins to cover the port 10, as the blade tongues then swing out from the seat 15. Fuel mixture flows into the cylinder 1 above the piston 4.
I figur le har stempelet 4 nådd øvre dødpunkt i kompresjonsslaget. Inntaksventilen lukkes som følge av trykkstigningen og stempelet 4 dekker også porten 10. Utstøtsventilen 8 er lukket. Etter at stempelet har passert øvre dødpunkt initieres tenning på kjent måte og stempelet begynner sitt arbeidsslag (figur la). In figure le, the piston 4 has reached top dead center in the compression stroke. The intake valve is closed as a result of the pressure rise and the piston 4 also covers the port 10. The exhaust valve 8 is closed. After the piston has passed top dead center, ignition is initiated in a known manner and the piston begins its working stroke (figure la).
Det har overraskende vist seg at den relativt sene åpning av inntaket 7 ikke representerer noen ulempe. Den kompenseres også lett for ved at det ved plasseringen av inntaksportenlO i sylinderveggen nå gis mulighet for større portåpning (tverrsnittsareal), med øket fyllingsgrad. Det kan også tenkes mer enn en port 10 i sylinderveggen. Tilbakeslagsventilen 12 arbeider raskt og selvstendig og krever ingen mekanisk eller hydraulisk ventilstyring. It has surprisingly turned out that the relatively late opening of the intake 7 does not represent any disadvantage. It is also easily compensated for by the fact that the placement of the intake port 10 in the cylinder wall now allows for a larger port opening (cross-sectional area), with an increased degree of filling. It is also conceivable to have more than one port 10 in the cylinder wall. The non-return valve 12 works quickly and independently and requires no mechanical or hydraulic valve control.
Det er ikke vist, men den stempelstyrte inntaksåpning kan også brukes uten membran eller tilbakeslagsventil, da med en kompressor som sørger for at det står et overtrykk i inntakskanalen. It is not shown, but the piston-controlled intake opening can also be used without a membrane or non-return valve, then with a compressor which ensures that there is an overpressure in the intake channel.
Tilbakeslagsventilen må plasseres i inntakskanalen så nær stempelet som mulig, for å unngå effekttap. The non-return valve must be placed in the intake duct as close to the piston as possible, to avoid loss of power.
Inntakssystemet har ingen innvirking på elektroniske styringsenheter som benyttes i moderne motorer, så som lambdasondekatalysatorer. The intake system has no influence on electronic control units used in modern engines, such as lambda probe catalysts.
I sum oppnås en lettere, mindre plasskrevende og billigere 4-takt motor. Motorens forbrenning begrenses ikke som i en vanlig toppventilert motor, der ventilenes størrelser vil være begrenset av diameteren i sylinderen. Resultatet er bedre forbrenning/effekt og renere avgass. In sum, a lighter, less space-consuming and cheaper 4-stroke engine is achieved. The engine's combustion is not limited as in a normal top-ventilated engine, where the valve sizes will be limited by the diameter in the cylinder. The result is better combustion/power and cleaner exhaust gas.
Som materiale i tilbakeslagsventilen, dvs. i bladtungene 13,14, kan det eksempelvis benyttes vanlig kjente metallmaterialer egnet for slike ventilmiljøer. Et mulig materiale er et Kevlar-basert materiale. As material in the non-return valve, i.e. in the blade tongues 13,14, commonly known metal materials suitable for such valve environments can for example be used. One possible material is a Kevlar-based material.
Claims (1)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO20014040A NO314553B1 (en) | 2001-08-20 | 2001-08-20 | Device for 4-stroke internal combustion engine |
PCT/NO2002/000295 WO2004018853A1 (en) | 2001-08-20 | 2002-08-23 | Improvement in a 4-stroke internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO20014040A NO314553B1 (en) | 2001-08-20 | 2001-08-20 | Device for 4-stroke internal combustion engine |
PCT/NO2002/000295 WO2004018853A1 (en) | 2001-08-20 | 2002-08-23 | Improvement in a 4-stroke internal combustion engine |
Publications (3)
Publication Number | Publication Date |
---|---|
NO20014040D0 NO20014040D0 (en) | 2001-08-20 |
NO20014040L NO20014040L (en) | 2003-02-21 |
NO314553B1 true NO314553B1 (en) | 2003-04-07 |
Family
ID=32684356
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
NO20014040A NO314553B1 (en) | 2001-08-20 | 2001-08-20 | Device for 4-stroke internal combustion engine |
Country Status (2)
Country | Link |
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NO (1) | NO314553B1 (en) |
WO (1) | WO2004018853A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITVE20040002U1 (en) * | 2004-01-19 | 2004-04-19 | Euromotor Spa | TWO STROKE INTERNAL COMBUSTION ENGINE, IN PARTICULAR FOR PORTABLE EQUIPMENT SUCH AS CHAINSAWS, BRUSHCUTTERS, ETC. |
IT201600085519A1 (en) * | 2016-08-16 | 2018-02-16 | Daniele Orzi | Internal combustion engine, supercharged, with rotary valve distribution |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4864984A (en) * | 1986-09-02 | 1989-09-12 | Blish Nelson A | Rotary valve internal combustion engine |
US5931134A (en) * | 1997-05-05 | 1999-08-03 | Devik International, Inc. | Internal combustion engine with improved combustion |
-
2001
- 2001-08-20 NO NO20014040A patent/NO314553B1/en not_active IP Right Cessation
-
2002
- 2002-08-23 WO PCT/NO2002/000295 patent/WO2004018853A1/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
NO20014040D0 (en) | 2001-08-20 |
NO20014040L (en) | 2003-02-21 |
WO2004018853A1 (en) | 2004-03-04 |
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