EP0250497B1 - Moteur a combustion interne fonctionnant selon un procede a deux temps - Google Patents

Moteur a combustion interne fonctionnant selon un procede a deux temps Download PDF

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Publication number
EP0250497B1
EP0250497B1 EP87900055A EP87900055A EP0250497B1 EP 0250497 B1 EP0250497 B1 EP 0250497B1 EP 87900055 A EP87900055 A EP 87900055A EP 87900055 A EP87900055 A EP 87900055A EP 0250497 B1 EP0250497 B1 EP 0250497B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
internal combustion
combustion engine
engine according
scavenging
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.)
Expired - Lifetime
Application number
EP87900055A
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German (de)
English (en)
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EP0250497A1 (fr
Inventor
Christian Bartsch
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Individual
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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
Priority to AT87900055T priority Critical patent/ATE55173T1/de
Publication of EP0250497A1 publication Critical patent/EP0250497A1/fr
Application granted granted Critical
Publication of EP0250497B1 publication Critical patent/EP0250497B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F01L7/12—Rotary or oscillatory slide valve-gear or valve arrangements specially for two-stroke engines
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • 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 a two-stroke internal combustion engine, comprising at least one cylinder defining a combustion chamber, each with a piston sliding therein, a single flushing slot, an outlet slot arranged next to the flushing slot on the same cylinder side as this, and a flushing channel opening into the flushing slot, which is designed in this way is that the fresh gases supplied therein enter the cylinder tangentially and obliquely to the cylinder axis in the direction away from the piston, the fresh gases reaching the flushing channel instead of via a crankcase pump via a separate charging device.
  • a two-stroke internal combustion engine is the subject of US-A-2,840,062.
  • GB-A-464 750 shows, it is also known in two-stroke internal combustion engines to arrange the flushing slots higher than the outlet slots. In order to allow as few exhaust gases as possible to get into the flushing slots during the downward stroke of the piston, these are designed in such a way that their cross section only gradually increases with the downward moving piston. In contrast, the outlet slots very suddenly reveal a large cross section. The possibility of setbacks is thus reduced in the internal combustion engine according to this GB-A-464 750, but not excluded.
  • the invention has for its object to provide a two-stroke internal combustion engine of the type mentioned in such a way that it can work with a particularly high efficiency, without the risk of backfiring of burned gases from the cylinder into the charging device.
  • a rotary valve driven by the crankshaft is inserted, which rotates at single or double crankshaft speed and is provided with an adjusting device which is adjustable directly or via an electronic control unit such that the Rotary slide valve works as a throttle valve and at the same time prevents burnt gases from returning from the cylinder to the charging device to prevent the flushing slot from being opened over a larger crank angle than the outlet slot and the bottom edge of the flushing slot relative to the upper piston edge at bottom dead center being higher than the bottom edge of the outlet slot.
  • the rotary slide valve provided according to the invention makes it possible to take full advantage of the effect of a flushing slot located at the top and to let it begin with a large cross section from the start.
  • the rotary valve is designed in a known manner so that the fresh gases enter the tube at one end and flow through it to the control openings.
  • the rotary valve can be driven by a toothed belt, chain or gear wheels.
  • the adjustment device provided between the rotary valve and the drive enables the air volume delivered to be optimally adapted to the particular requirements of the engine.
  • a conventional throttle valve can therefore be omitted.
  • the adjustment is done fully automatically by the electronic control unit, from which the load, speed, pressure and temperature are processed.
  • the control unit can be combined with that for ignition timing and fuel injection, so that the air quantity and air mass are then also available as an influencing variable.
  • the replacement of the usual throttle valve with the control edge of the rotary valve ensures that when the rotary valve control edge is opened, the full boost pressure always ensures high fresh gas velocity in the overflow channel.
  • the electronics can also ensure higher air throughput and, thanks to higher compression work in the cylinder and in the supercharger, for faster braking of the engine speed.
  • the flushing slot is opened over a larger crank angle than the outlet slot and the bottom edge of the flushing slot is higher than the controlling piston top edge at the bottom dead center, the fresh gas can flow unaffected from the top piston edge into the cylinder over a longer period of time.
  • the flow losses in the rinsing channels are particularly low if, according to an advantageous embodiment of the invention, these are largely rectilinear and taper towards the cylinder run fairly. Furthermore, a particularly high rotational speed of the fresh gas roller is achieved by this design.
  • the rotary valve is particularly easy to drive if the rotary valve is arranged parallel to the crankshaft.
  • combustion chamber as an annular channel leads to a structurally simple construction of the internal combustion engine and prevents undesirably high thermal loads.
  • combustion chamber can also be designed in the form of a disk or as an intermediate shape.
  • an injection nozzle is arranged on the outside of the circumference of the combustion chamber and its injection jet is directed approximately horizontally through the cylinder axis to the other cylinder axis.
  • the spark plug is provided on the outside of the combustion chamber circumference, since a mixture which is particularly easily ignitable rotates there, so that reliable ignition occurs even at low engine speeds.
  • Ignition is particularly reliable if, according to another embodiment of the invention, two spark plugs are provided on the outside of the combustion chamber circumference, offset by 180 degrees.
  • the rotary valve can also be designed as a balancer shaft.
  • FIG. 1 shows a cylinder 1 of an internal combustion engine, into which a rectilinear flushing channel 3, which tapers towards the cylinder 1, tangentially leads through a flushing slot 2.
  • a flushing slot 2 is provided, via which burned gases leave the cylinder 1 in order to reach the exhaust, not shown, via an outlet channel 5.
  • a spark plug 6 is shown in dashed lines, which sits in the cylinder head and is therefore actually not visible in the sectional view.
  • a charging device is not shown, from which fresh gas enters the cylinder 1 via the purge channel 3 in order to form a fresh gas roller indicated by an arrow 7.
  • the flushing slot 2 is arranged higher than the outlet slot 4, so that both its upper edge 15 and its lower edge 17 are higher in relation to the upper edge 14 of the piston than the corresponding upper edge 16 and Lower edge 18 of the outlet slot 4.
  • the combustion chamber 19 is designed as an annular channel.
  • FIG. 4 shows that a rotary slide valve 21 is arranged in the flushing channel 3 parallel to the crankshaft, not shown. This rotary valve 21 is driven by the crankshaft and controls the incoming purge gas via a control opening 22. It can also be seen that the flushing slot 2 is arranged higher than the outlet slot 4. Shown and positioned in FIG. 5 are also the outlet channel 5 and the piston 13 with the piston top edge 14, which is in the piston position shown in the bottom dead center.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Un moteur à combustion interne comprend un seul canal à écoulement rapide (3) qui s'ouvre asymétriquement et unilatéralement dans un canal d'échappement (5) et qui s'étend tangentiellement dans le cylindre (1), transversalement à la culasse. Un écoulement rotatif est ainsi obtenu dans le cylindre, le long de sa paroi intérieure, ce qui assure l'allumage complet et fiable même avec une basse vitesse de rotation, une consommation minime de carburant et une teneur minime en matières toxiques dans les gaz d'échappement.

Claims (8)

1. Machine à combustion interne à deux temps, comprenant au moins un cylindre (1) délimitant une chambre de combustion avec à chaque fois un piston (13) coulissant dans celui-ci, avec une lumière de balayage unique (2), avec une fente d'échappement (4) disposée à proximité de la lumière de balayage sr le même côté du cylindre que celle-ci et avec un canal à écoulement (3) débouchant dans la lumière de balayage (2), ladite machine étant conçue de manière telle que les gaz frais qui y sont introduits pénétrent dans le cylindre (1) tangentiellement et en oblique par rapport à l'axe du cylindre dans la direction opposée au piston (13), les gaz frais parvenant dans le canal à écoulement par un dispositif de suralimentation séparé au lieu d'une pompe à surcompression, caractérisée en en ce que entre le dispositif de suralimentation et le cylindre (1) est introduit un tiroir rotatif (21) entrainé par le vilebrequin, qui tourne selon un nombre de tours de vilebrequin simple ou double et qui est muni d'un dispositif de réglage, qui peut être réglé directement ou au moyen d'un dispositif de commande électronique de manière telle que le tiroir rotatif (21) fonctionne en soupape d'étranglement et que en même temps il empêche le retour de gaz brûlés hors du cylindre (1) dans le dispositif de suralimentation, que la lumière de balayage (2) est ouverte selon un angle de vilebrequin plus grand que la fente d'échappement (4) et que le chant inférieur (17) de la lumière de balayage par rapport au chant supérieur (14) du piston commandant en son point mort inférieur est situé plus haut que le chant inférieur (18) de la fente d'échappement.
2. Machine à combustion interne selon la revendication 1, caractérisée en ce que le canal à écoulement (3) est largement rectiligne et qu'il va en se rétrécissant en direction du cylindre (1).
3. Machine à combustion interne selon les revendications 1 ou 2, caractérisée en ce que le tiroir rotatif (21) est disposé parallèlement au vilebrequin.
4. Machine à combustion interne selon une ou plusieurs des revendications précedentes, caractérisée en ce que la chambre de combustion (19) est conformée en canal annulaire.
5. Machine à combustion interne selon une ou plusieurs des revendications précédentes, caractérisée en ce qu'un injecteur (20) est disposé à l'extérieur sur la périphérie de la chambre de combustion et que son jet d'injection est dirigé au travers de l'axe du cylindre sensiblement horizontalement par rapport à l'autre côté du cylindre.
6. Machine à combustion interne selon une ou plusieurs des revendications précédentes, caractérisée en ce qu'une bougie d'allumage (6) est disposée à l'extérieur sur la périphérie de la chambre de combustion.
7. Machine à combustion interne selon une ou plusieurs des revendications précédentes, caractérisée en ce que deux bougies d'allumage (6) décalées de 180° sont disposées à l'extérieur sur la périphérie de la chambre de combustion.
8. Machine à combustion interne selon une ou plusieurs des revendications précédentes, caractérisée en ce que le tiroir rotatif (21) est conformé simultanément comme arbre de compensation pour l'élimination de balourds résiduels.
EP87900055A 1985-12-23 1986-12-15 Moteur a combustion interne fonctionnant selon un procede a deux temps Expired - Lifetime EP0250497B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87900055T ATE55173T1 (de) 1985-12-23 1986-12-15 Nach dem zweitaktverfahren arbeitende verbrennungskraftmaschine.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE8536426 1985-12-23
DE8536426U 1985-12-23
DE3618797 1986-06-04
DE3618797 1986-06-04

Publications (2)

Publication Number Publication Date
EP0250497A1 EP0250497A1 (fr) 1988-01-07
EP0250497B1 true EP0250497B1 (fr) 1990-08-01

Family

ID=25844338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87900055A Expired - Lifetime EP0250497B1 (fr) 1985-12-23 1986-12-15 Moteur a combustion interne fonctionnant selon un procede a deux temps

Country Status (4)

Country Link
US (1) US4815420A (fr)
EP (1) EP0250497B1 (fr)
DE (1) DE3673163D1 (fr)
WO (1) WO1987003931A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4219236A1 (de) * 1992-06-12 1993-12-16 Christian Bartsch Nach dem Otto- oder Dieselverfahren arbeitende Zweitakt-Verbrennungskraftmaschine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6564759B2 (en) * 2001-08-28 2003-05-20 Homelite Technologies, Inc. Injection port for internal combustion engine
US6796395B1 (en) 2001-09-07 2004-09-28 Polaris Industries Inc. Snowmobile
US7059440B1 (en) 2001-09-07 2006-06-13 Polaris Industries Inc. Snowmobile
CA2411311A1 (fr) * 2002-11-07 2004-05-07 Arctic Cat, Inc. Vehicule a moteur incline

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1429078A (en) * 1920-03-30 1922-09-12 Hutchinson Job Two-cycle internal-combustion engine
GB179628A (en) * 1921-02-07 1922-05-08 Achille Macchioni Improvements in or relating to two stroke cycle internal combustion engines for actuating locomotives and the like
US1688767A (en) * 1921-06-24 1928-10-23 Webb Cecil Internal-combustion engine
US1605381A (en) * 1923-03-22 1926-11-02 Int Motor Co Combustion chamber for internal-combustion engines
FR628587A (fr) * 1926-04-12 1927-10-26 Perfectionnements aux moteurs à combustion interne à deux temps
US1750201A (en) * 1927-07-23 1930-03-11 Gardner A B Spencer Two-cycle engine
US1952275A (en) * 1929-12-02 1934-03-27 Fried Krupp Germaniawerft Ag Internal-combustion engine
US2071125A (en) * 1930-05-29 1937-02-16 White Motor Co Internal combustion engine
CH154285A (de) * 1931-01-07 1932-04-30 Sulzer Ag Zylinder für Zweitakt-Brennkraftmaschinen.
US2075232A (en) * 1932-10-24 1937-03-30 Fairbanks Morse & Co Method and means for scavenging
US2111282A (en) * 1934-06-07 1938-03-15 Packard Motor Car Co Internal combustion engine
GB464750A (en) * 1935-10-14 1937-04-23 Messerschmitt Boelkow Blohm Improvements in and relating to the scavenging and charging of the cylinders of two-stroke internal combustion engines
US2110754A (en) * 1935-11-30 1938-03-08 Alston Charles Henry Thomas Combustion engine
US2169652A (en) * 1937-12-20 1939-08-15 Ljungstrom Olof Internal combustion engine
US2504243A (en) * 1946-09-18 1950-04-18 Nordberg Manufacturing Co Control for internal-combustion engines
NL84721C (fr) * 1950-04-28 1900-01-01
US2724372A (en) * 1952-08-05 1955-11-22 Fairbanks Morse & Co Engine cylinder scavenging
US2840062A (en) * 1955-05-17 1958-06-24 Raymond J Classen Internal combustion engine system
US3203409A (en) * 1963-07-09 1965-08-31 Georgia Tech Res Inst Apparatus for controlling the air taken into the combustion chambers of a spark ignition internal combustion engine
US3815558A (en) * 1972-08-07 1974-06-11 W Tenney Scavenge porting system
DE2620408A1 (de) * 1976-05-08 1977-11-24 Turner Research Inc Verbrennungsmotor
JPS5632036A (en) * 1979-08-22 1981-04-01 Yamaha Motor Co Ltd Combustion chamber for two-stroke-cycle gasoline engine
SU1174576A1 (ru) * 1983-08-23 1985-08-23 Минский Мотоциклетный И Велосипедный Завод Двигатель внутреннего сгорани
FR2566459B1 (fr) * 1984-06-20 1988-01-29 Hazera Patrick Procede d'amelioration du fonctionnement d'un moteur a combustion interne et moteur a combustion interne a fonctionnement ameliore et structure simplifiee

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4219236A1 (de) * 1992-06-12 1993-12-16 Christian Bartsch Nach dem Otto- oder Dieselverfahren arbeitende Zweitakt-Verbrennungskraftmaschine

Also Published As

Publication number Publication date
DE3673163D1 (de) 1990-09-06
EP0250497A1 (fr) 1988-01-07
US4815420A (en) 1989-03-28
WO1987003931A1 (fr) 1987-07-02

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