EP0507648A1 - Zweitaktmotor mit selektiver Steuerung für die in der Brennkammer eingeführte Ladung - Google Patents

Zweitaktmotor mit selektiver Steuerung für die in der Brennkammer eingeführte Ladung Download PDF

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Publication number
EP0507648A1
EP0507648A1 EP92400763A EP92400763A EP0507648A1 EP 0507648 A1 EP0507648 A1 EP 0507648A1 EP 92400763 A EP92400763 A EP 92400763A EP 92400763 A EP92400763 A EP 92400763A EP 0507648 A1 EP0507648 A1 EP 0507648A1
Authority
EP
European Patent Office
Prior art keywords
stroke engine
engine according
cylinder
openings
load
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.)
Granted
Application number
EP92400763A
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English (en)
French (fr)
Other versions
EP0507648B1 (de
Inventor
Pierre Duret
Gaétan Monnier
Thierry Colliou
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IFP Energies Nouvelles IFPEN
Original Assignee
IFP Energies Nouvelles IFPEN
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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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/0291—Throttle control device for throttle being disposed in a two-stroke engine transfer passage

Definitions

  • the invention relates to a two-stroke internal combustion engine in which selective control of the charge introduced into the combustion chamber by one or more intake ports is achieved, depending on the operating conditions of the engine.
  • the intake ducts will be "fluffed" differently from each other depending on the operating conditions of the engine.
  • the selective control of the introduction of the load according to the invention is preferably carried out on two-stroke engines of the transverse scanning type, as defined below.
  • the control can be applied to cases where the load introduced does not contain fuel, this being then introduced by a separate arrival.
  • the pressure source used for supplying air or a fuel mixture to the cylinder may be constituted by a source of pressure external to the engine, such as a compressor, a blower or any other pressurized capacity, or by an internal source such as than the pump housing.
  • two-stroke engines have at least one cylinder in the upper part and a lower part, also called pump housing, given its main function, which ensures the introduction of fresh gas into the cylinder by means of one or more specific so-called “transfer” conduits. Lights or transfer openings in the cylinder allow this introduction.
  • the piston which moves alternately in the cylinder ensures the suction in the casing and the compression of the fresh gases in the cylinder.
  • Fresh gases are generally introduced at the pump housing through an opening provided for example with a non-return valve.
  • the movement of the piston towards the upper part of the cylinder causes the suction of fresh gases in the pump housing while the reverse movement of the piston causes the compression of these gases which, when the transfer lights are released by the piston, are then injected under a certain pressure into the cylinder, which produces a sweep of fresh gases which then expel burnt gases.
  • burnt gases can escape through so-called exhaust openings made in the cylinder, slightly offset in height with respect to the transfer ports.
  • “Fresh gas” generally means a mixture of air, fueled or not.
  • the concept behind most of the improvements proposed consists in delaying the introduction of the fuel, which is done, for example, when the exhaust light is almost closed.
  • delaying the introduction of fuel it must be introduced and vaporized in a very short time (of the order of 2 to 3 milli-seconds at high engine speed), which can be problematic.
  • the charge of fresh gas does not contain fuel. It can be compressed, either by an external mechanical compressor, or by a source of compression supplied, for example, by the pump housing itself.
  • the fuel is then injected directly into the combustion chamber, at high pressure, a pressure generally greater than 30 bars.
  • Another type of two-stroke engine capable of delaying the introduction of fuel is based on the principle of pneumatic injection of the mixture.
  • compressed air is used to help atomize and vaporize the fuel very quickly in the cylinder.
  • the object of the present invention is in particular to provide an improvement in this type of control means since it relates to a motor of the transverse scanning type, comprising a cylinder in which a piston moves, a means making it possible to admit a charge under pressure in said cylinder and at least two inlet ports in the wall of said cylinder, said ports cooperating with said load inlet means.
  • the motor comprises in accordance with the invention, a means for selectively closing the passage section of said load admission means in the combustion chamber, as a function of at least one operating parameter of the engine.
  • This means may, for example, consist of a part that can move in rotation about an axis substantially perpendicular to the axis of the cylinder and provided with at least one extension.
  • the means for selectively closing said passage section may also consist, without departing from the scope of the invention, of a rotary plug comprising several through openings, said plug being placed opposite said inlet port (s) in the cylinder. .
  • the rotary plug can be provided for example with four through openings of different section two by two.
  • the rotary plug may include three through openings not spaced from each other.
  • the charge introduced may or may not contain fuel.
  • the pressure source can be constituted by the pump housing or by a pressure source external to the engine such as a compressor or any other means known per se.
  • FIG. 1 represents a classic example of embodiment of such an engine.
  • the sweep is said to be transverse because the inlet port (s) 20 are grouped together on the same side of the cylinder, all the exhaust openings 3 being grouped on the other side of the cylinder, and these two groups of openings being arranged on either side of an axial plane of symmetry of the cylinder in substantially symmetrical positions.
  • the sweeping gas which in the case of the engine of FIG. 1 comes from the pump housing, but which can also come from another pressure source, therefore describes a movement approximately defined by the arrows 11.
  • Figure 2 shows how the invention can be applied to this type of two-stroke engine.
  • a selective closure means 30 is placed in the intake duct 21 of the cylinder.
  • This means 30 may be in the form of a rotary plug with an axis 31 perpendicular to the axis 1 of the exhaust duct.
  • the plug 30 is provided with at least one through opening 32 whose shape and / or arrangement meet the intended application.
  • the plug 30 can be provided with through openings 32 as shown in FIGS. 3 and 4.
  • This configuration creates a swirling movement of gases in the combustion chamber.
  • This swirling movement asymmetrical with respect to the axial plane of symmetry of the cylinder, can be advantageous in the case of engines with direct fuel injection. Indeed, this movement substantially in the form of a helix can help to mix and vaporize the liquid fuel introduced directly into the combustion chamber, thus creating better combustion conditions.
  • FIG. 4 shows another example of a rotary plug 30 which is particularly suitable for transverse scanning motors.
  • the plug 30 shown in this figure is provided with large through openings arranged in the central part, and smaller openings located at the periphery, on either side of the central openings.
  • This arrangement makes it possible, when the admitted flow rate is low, to better center the intake gases around the axis of the exhaust duct on which the spark plug is generally located. This is achieved by first sealing the intake ducts at the periphery before those located in the central part.
  • the low charge is used optimally in terms of scanning the combustion zone.
  • the gas flow passing through the plug is adjusted as a function for example of the engine load, the engine speed or another engine operating parameter.
  • a rotation of the plug 30 around its axis 31 can in fact vary the flow rate of the admitted gases.
  • a certain rotation can prevent any flow in the lateral openings and force all the gases to pass through the central openings.
  • the load can be pressurized by the pump housing or by any other means.
  • This means 60 is able to rotate about an axis 61 which may be perpendicular to the axis 1 of the exhaust duct and which belongs to a cross section of the duct d 'intake 21.
  • the means 60 is located near the intake lumen 20 and is provided with as many extensions 62 as there are lights or divisions in the intake lumen. Each extension 62 in fact more or less partially covers the inlet lumen 20 according to the angle of rotation of the means 60 around the axis 61.
  • the rotation is preferably limited by two stops, one 63 being defined for example through the upper part of the opening 20, the other stop 64 can be defined by the cylinder block itself.
  • the position (a) in which the means 60 discovers the most light 20 is given in solid lines in FIG. 6 while the dotted lines represent the means 60 in its position of maximum overlap (b).
  • the means 60 by modifying the same section of the lumen 20 makes it possible to vary the duration of opening of the intake duct (s). In addition, by modifying each light differently (or each light division), it creates a certain aerodynamics of the gases inside the combustion chamber.
  • Figure 6 shows in a section perpendicular to the previous one, the variations in the opening of the intake lumen 20, where the "high" position (a) of the means 60 corresponds to the line 71 while the "low” position (b) of the means 60 is defined by the curve 72. It appears that in the "low” position (b), the closure is not identical at all the points of the transfer light (s) 20: the points those furthest from the axis of the intake duct A and E for example, cover the light 20 more than the points B, C and D closest to the axis. This difference is due to the fact that the displacement radius of the points is different.
  • the means 60 therefore allows a selective reduction of the section in combination with the reduction of the angular duration of opening.
  • an equivalent closure means can be used in the case where the intake duct 21 is divided at the level of the intake lumen 20 in three parts located for example not symmetrically with respect to the axial plane of symmetry of the cylinder containing the exhaust axis 1.
  • This arrangement of the lights 20 creates an asymmetrical, for example helical, movement of the gases as represented by the arrows 80 in FIG. 7 when the means 60 is in the high position, that is to say for the full opening of the lights 20 .
  • FIG. 9 shows by arrow 100, the movement of the gases inside the combustion zone when the shutter means 60 are in the low position. Balancing of the scanning is thus obtained.
  • a low position of the extensions at low load will be chosen while the high position, with full opening, will correspond to a high load setting.
  • the profile of the part 60 is very important both for the duration of angular opening and for the internal aerodynamics of the gases in the combustion chamber.
  • Any means known per se can be used to control the rotation of the means 60 as a function of at least one operating parameter of the engine.
  • the pressure source can be constituted by the pump housing or by another means.

Landscapes

  • 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)
  • Supercharger (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP92400763A 1991-04-03 1992-03-20 Zweitaktmotor mit selektiver Steuerung für die in der Brennkammer eingeführte Ladung Expired - Lifetime EP0507648B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9104006A FR2674906A1 (fr) 1991-04-03 1991-04-03 Moteur a deux temps a controle selectif de la charge introduite dans la chambre de combustion.
FR9104006 1991-04-03

Publications (2)

Publication Number Publication Date
EP0507648A1 true EP0507648A1 (de) 1992-10-07
EP0507648B1 EP0507648B1 (de) 1994-10-19

Family

ID=9411391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92400763A Expired - Lifetime EP0507648B1 (de) 1991-04-03 1992-03-20 Zweitaktmotor mit selektiver Steuerung für die in der Brennkammer eingeführte Ladung

Country Status (5)

Country Link
US (1) US5285753A (de)
EP (1) EP0507648B1 (de)
JP (1) JPH0681658A (de)
DE (1) DE69200532T2 (de)
FR (1) FR2674906A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4303496A1 (de) * 1993-02-06 1994-08-11 Christian Bartsch Zweitakt-Brennkraftmaschine
WO2009047566A1 (en) * 2007-10-12 2009-04-16 Gordon Mcnally Seal for a rotary valve for an internal combustion engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6079379A (en) * 1998-04-23 2000-06-27 Design & Manufacturing Solutions, Inc. Pneumatically controlled compressed air assisted fuel injection system
US6273037B1 (en) 1998-08-21 2001-08-14 Design & Manufacturing Solutions, Inc. Compressed air assisted fuel injection system
US6293235B1 (en) 1998-08-21 2001-09-25 Design & Manufacturing Solutions, Inc. Compressed air assisted fuel injection system with variable effective reflection length

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE865233C (de) * 1940-06-21 1953-02-02 Auto Union A G Gemischverdichtende Zweitaktbrennkraftmaschine
DE932639C (de) * 1934-12-02 1955-09-05 Daimler Benz Ag Zweitaktbrennkraftmaschine
DE3933105A1 (de) * 1988-10-13 1990-04-19 Volkswagen Ag Zweitakt-brennkraftmaschine mit einer ladungswechselsteuerung nach art einer rueckschiebesteuerung
EP0400338A2 (de) * 1989-05-30 1990-12-05 Cagiva Motor Italia S.P.A. Einrichtung für das Wechseln der Einspritzrichtung des Brennstoffes in einem Zweitakt-Brennkraft-Maschinenzylinder
EP0404338A1 (de) * 1989-06-21 1990-12-27 General Motors Corporation Wärmeregelung an der Spülung einer Zweitaktmotors
EP0460820A1 (de) * 1990-06-02 1991-12-11 Jaguar Cars Limited Zweitaktmotoren

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2473164A (en) * 1949-06-14 Two-cycle engine
US2675789A (en) * 1954-04-20 Internal-combustion engine
US2113979A (en) * 1934-12-01 1938-04-12 Whitworth & Co Scavenging of two-stroke internal combustion engines
US2110754A (en) * 1935-11-30 1938-03-08 Alston Charles Henry Thomas Combustion engine
US2214047A (en) * 1938-11-14 1940-09-10 John F Tulloch Throttle control in internal combustion engine
US2474879A (en) * 1945-10-02 1949-07-05 Edward A Winfield Internal-combustion engine
US2440726A (en) * 1945-10-15 1948-05-04 Karl K Probst Internal-combustion engine
US2797672A (en) * 1953-10-23 1957-07-02 Technical Engineering Service Two-stroke-cycle internal combustion engine
JPS58101207A (ja) * 1981-12-11 1983-06-16 Mitsubishi Heavy Ind Ltd ２サイクル内燃機関の掃気管制装置
JPS58178822A (ja) * 1982-04-13 1983-10-19 Nippon Clean Engine Res ２サイクル内燃機関
JPS6235019A (ja) * 1985-08-06 1987-02-16 Yamaha Motor Co Ltd ２サイクルエンジンの吸気装置
JPS63309717A (ja) * 1987-06-12 1988-12-16 Kawasaki Heavy Ind Ltd ２サイクルエンジンの吸気部の構造
JPH02169818A (ja) * 1988-12-21 1990-06-29 Fuji Heavy Ind Ltd 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
DE932639C (de) * 1934-12-02 1955-09-05 Daimler Benz Ag Zweitaktbrennkraftmaschine
DE865233C (de) * 1940-06-21 1953-02-02 Auto Union A G Gemischverdichtende Zweitaktbrennkraftmaschine
DE3933105A1 (de) * 1988-10-13 1990-04-19 Volkswagen Ag Zweitakt-brennkraftmaschine mit einer ladungswechselsteuerung nach art einer rueckschiebesteuerung
EP0400338A2 (de) * 1989-05-30 1990-12-05 Cagiva Motor Italia S.P.A. Einrichtung für das Wechseln der Einspritzrichtung des Brennstoffes in einem Zweitakt-Brennkraft-Maschinenzylinder
EP0404338A1 (de) * 1989-06-21 1990-12-27 General Motors Corporation Wärmeregelung an der Spülung einer Zweitaktmotors
EP0460820A1 (de) * 1990-06-02 1991-12-11 Jaguar Cars Limited Zweitaktmotoren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 8, no. 20 (M-271)(1457) 27 Janvier 1984 & JP-A-58 178 822 ( NIHON KURINENJIN KENKYUSHO K.K. ) 19 Octobre 1983 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4303496A1 (de) * 1993-02-06 1994-08-11 Christian Bartsch Zweitakt-Brennkraftmaschine
WO2009047566A1 (en) * 2007-10-12 2009-04-16 Gordon Mcnally Seal for a rotary valve for an internal combustion engine

Also Published As

Publication number Publication date
EP0507648B1 (de) 1994-10-19
DE69200532T2 (de) 1995-02-23
FR2674906B1 (de) 1995-01-13
JPH0681658A (ja) 1994-03-22
FR2674906A1 (fr) 1992-10-09
US5285753A (en) 1994-02-15
DE69200532D1 (de) 1994-11-24

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