EP0346188B1 - Device and method for the introduction of a pressurized air-fuel mixture into the cylinder of an engine - Google Patents

Device and method for the introduction of a pressurized air-fuel mixture into the cylinder of an engine Download PDF

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Publication number
EP0346188B1
EP0346188B1 EP89401497A EP89401497A EP0346188B1 EP 0346188 B1 EP0346188 B1 EP 0346188B1 EP 89401497 A EP89401497 A EP 89401497A EP 89401497 A EP89401497 A EP 89401497A EP 0346188 B1 EP0346188 B1 EP 0346188B1
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EP
European Patent Office
Prior art keywords
cylinder
pressure
transfer
pump casing
pipe
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
EP89401497A
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German (de)
French (fr)
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EP0346188A1 (en
Inventor
Jean-Pierre Maissant
Jean-Luc Blanchard
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IFP Energies Nouvelles IFPEN
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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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/08—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by the fuel being carried by compressed air into main stream of combustion-air
    • 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
    • F02B13/00—Engines characterised by the introduction of liquid fuel into cylinders by use of auxiliary fluid
    • 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
    • F02B25/26—Multi-cylinder engines other than those provided for in, or of interest apart from, groups F02B25/02 - F02B25/24
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/10—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel peculiar to scavenged two-stroke engines, e.g. injecting into crankcase-pump chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the present invention relates to a method and devices improving the introduction under pressure of a fuel mixture at the end of air sweeping in a 2-stroke engine cylinder.
  • the pressure source used is supplied by the pressure prevailing in the cylinder crankcase which is 120 ° behind the crankshaft (in the case of a 3, 6, ..., 3n cylinder engine) or by the cylinder crankcase 90 ° behind the crankshaft (in the case of a 4, 8, ..., 4n cylinder engine) with respect to the cylinder in question where the fuel mixture takes place, as well as by the return flow (generally designated by the Anglo-Saxon term of "back-flow") which is caused in a transfer duct of the late cylinder, this transfer duct connecting this cylinder to its pump casing (back-flow cylinder-casing ).
  • the introduction of a fuel mixture under pressure occurs on the arrival of gases from this pressure source in the cylinder considered during its end of sweeping phase.
  • the arrival of gas from the pump housing into a fuel metering device prepares a fuel mixture which can be introduced into the cylinder through an orifice.
  • the introduction and optionally the preparation of the fuel mixture into the cylinder in question is prolonged and improved by the use of return gases in the transfer duct coming from the lagging cylinder and which are at a high pressure level. .
  • the opening for introducing the fuel mixture into the cylinder in question may preferably be opened only during the arrival of the gases coming from the pump housing of the late cylinder and of the late cylinder itself. This hole can be in the cylinder head.
  • the device may include a valve controlled to open during the arrival of the gases from this pressure source, or an automatic valve (non-return valve type), the opening of which is controlled by the difference between the pressure from the pressure source and the pressure of the cylinder considered.
  • a valve controlled to open during the arrival of the gases from this pressure source or an automatic valve (non-return valve type), the opening of which is controlled by the difference between the pressure from the pressure source and the pressure of the cylinder considered.
  • the hole can also be in the cylinder. Its opening can then be controlled by the movement of the piston (in the case of a light) combined with a non-return device of the valve type (or with a rotary plug).
  • an embodiment of this type may consist in connecting the cylinder housing delayed by an angle of 120 or 90 ° of the crankshaft relative to the cylinder in question, via a connection conduit opening on the side opposite to the exhaust in the cylinder in question (conduit generally called rear transfer conduit).
  • this metering can be carried out using '' low pressure injectors, but also using simpler devices, such as, for example, a carburetor of the type used for the intake of a two-stroke engine.
  • the present invention relates to a device for introducing under pressure the fuel mixture into a first cylinder of an internal combustion engine, this engine comprising at least one other cylinder having a pump housing, said pump housing communicating with said other cylinder via at least one transfer lumen and of the type comprising a connecting pipe between said pump housing and the first cylinder.
  • a transfer duct connects said transfer lumen to said connecting pipe and said transfer lumen is positioned so that there is a return flow during part of the cycle.
  • the angular offset can be 120 ° and the cycle of the first cylinder can precede the cycle of the other cylinder by 120 °.
  • the angular offset can be 90 ° and the cycle of the first cylinder can precede by 90 ° the cycle of the other cylinder.
  • the device according to the invention applies in particular to engines comprising a number of cylinders multiple of 3 or 4.
  • the pipeline may open into the first cylinder in the vicinity of the cylinder head of the engine.
  • the pipeline may open into the first cylinder on the side wall of this cylinder, substantially at the bottom of this cylinder.
  • the device according to the invention may include a shutter member placed between the pipe and the first cylinder, substantially in the vicinity of the latter.
  • the shutter member may be a valve controlled by a cam, or a rotating plug.
  • the shutter member may be automatic and be adapted to act like a valve.
  • the pipeline may include a fuel introduction and metering device.
  • This fuel introduction device may be a low pressure injector, just as it may include a venturi nozzle associated with said low pressure injector.
  • the fuel introduction device may be a carburetor.
  • the control of this carburetor can be coupled with a control that controls the amount of gas introduced into the pump housing of the first cylinder.
  • the device according to the invention may comprise between the carburetor and the pipe a non-return element such as a valve.
  • the fuel introduction and metering member comprises a diaphragm pump actuated by the pressure pulses of a pump housing.
  • the outlet duct of this diaphragm pump which connects the latter to the pipeline may include a system for adjusting its passage section.
  • This system may include a needle and control means taking into account the average pressure of a casing.
  • Said connecting pipe may advantageously have a common part with the transfer duct which connects the pump housing with said lumen.
  • An aerodynamic profiled part may be placed at the interconnection of the connecting pipe, said transfer duct and said transfer lumen.
  • a non-return valve may be placed on said transfer duct, said valve not allowing flow back to the pump housing.
  • the piston of said other cylinder may be bevelled or scalloped over a part of its surface to allow a return flow through at least one transfer lumen in order to facilitate the return flow.
  • the lumen where the back flow occurs may be positioned so that said flow occurs only after at least one exhaust lumen of said other cylinder has been discovered by said piston of said other cylinder.
  • the present invention also relates to a method of introducing under pressure the fuel mixture into a first cylinder of an internal combustion engine, this engine comprising at least one other cylinder having a pump housing, this pump housing communicating with said other cylinder. by at least one transfer light.
  • the engine preferably comprises a connecting pipe between said pump housing and the first cylinder, and a non-zero angular offset exists between the cycles of the cylinders so that the pressure of the gases contained in said pump housing can be used as pressure source for injecting the fuel mixture into the first cylinder.
  • the method according to the invention is characterized in that a backward flow is caused through said transfer lumen to increase momentarily the pressure in said casing or in a transfer conduit connecting said lumen to said connecting pipe.
  • each of the cylinders may be connected, directly or not, to a pump housing of another cylinder angularly delayed relative to the cylinder considered.
  • each cylinder may be in connection with the pump housing of the cylinder which is 120 ° behind the crankshaft relative to the cylinder considered.
  • Figure 1 shows in solid lines with the reference P1, the pressure variation curve as a function of the angle of rotation of the crankshaft in a cylinder of a two-stroke engine, near the bottom dead center corresponding to a crankshaft angle 180 °.
  • the curve of variation of the pressure of the casing equipping this cylinder is indicated in dotted lines, and bears the reference P2.
  • at least one of the transfer lights which connects this cylinder to the pump housing of this cylinder via a transfer conduit is positioned high enough to open before the pressure of the housing -pump is greater than or equal to the pressure in the cylinder.
  • this reverse flow, or return which is the source of the pressure peak 101 in FIG. 1.
  • This pressure peak can therefore make it possible to extend the duration of the introduction of fuel mixture during the whole part of the operating cycle of the cylinder considered where the pressure difference is sufficient to allow the introduction of fuel into the cylinder.
  • controlled valve automatic valve
  • light more valve or light more rotary valve
  • Figure 2 shows the pressure curve P3 in the cylinder considered as a function of the degree of rotation of the crankshaft, with a pressure source P4 coming from a transfer duct of a cylinder lagging 120 ° crankshaft relative to the cylinder considered . This corresponds in particular to the case of an engine comprising three cylinders.
  • the pressure curves P2 and P4 are close to each other since one P4 is taken in a transfer duct and the other P2 in the pump housing connected to this transfer duct.
  • the pressure peak 102 which corresponds to the pressure peak 101, allows the fuel injection pressure to accompany for a sufficiently long time the pressure curve P3 in the cylinder. It is thus possible to improve the injection.
  • the pressure peak 102 can be chosen to occur during the end of the injection period, at the moment when the cylinder pressure increases (start of compression) and therefore a higher injection pressure is necessary to continue l introduction of the injected mixture in the direction of injection member towards cylinder and avoid reversal of direction at the end of injection, such inversion may be responsible for a loss of compression and cylinder filling.
  • connection conduit between the two external "cylinders" being longer, this disadvantage can be overcome, if necessary, by placing, in the cylinder, the transfer light supplying the connection conduit between the two external cylinders higher than the other transfer lights which supply the connection conduits of the other cylinders.
  • Figures 3, 4, 5, 6, 7 show in solid lines the cylinder considered 1 with its piston 2 at the end of scanning, its exhaust 3, its exhaust light 4 which is about to be closed, its lights lateral transfer 5, and rear transfer 6, its casing 7 with an air intake only, for example by valves 8, its spark plug 9, the rod-crank system 10.
  • the cylinder 11 having a piston 2R whose movement is angularly delayed by 120 ° by means of the rod-crank system 13, relative to the piston 2 of the cylinder considered 1.
  • the piston 2R is in the expansion phase in the cylinder 11 and at the same time of compression in the pump housing 14.
  • the pump housing 14 whose movement of the piston 2R is angularly delayed by 120 ° supplies the source of pressure through the conduit 15.
  • the transfer light 6R of the cylinder 11 is positioned high enough for there to be a return flow.
  • the cylinder 1 in turn serves as a source of pressure for another cylinder.
  • the cylinder 1 is identical in its configuration to the cylinder 11 with regard in particular to the positioning of the lights.
  • the duct 15 is connected to the combustion chamber 16 of the cylinder considered 1.
  • the introduction of the pressurized air from the pump housing 14 into the chamber 16 takes place through an orifice 18, the opening of which is controlled by a valve 19. Upstream of the valve is a device for introducing and low-pressure fuel metering 20.
  • This device can be a low-pressure injector that is commercially available, or a fuel pump actuated by the successive pressures and depressions of a pump housing. A diagram of this latter device will be specified in FIG. 8. The introduction of the liquid fuel can take place in the duct 15, both during the whole time when the valve 19 is closed and during that when it is open.
  • This fuel metering and introduction device 20 can be associated with a venturi nozzle 21 placed in the duct 15, just upstream from the valve 19 and the orifice 18, in accordance with patent EP-189,714, in order to improve the spraying of fuel with air from the pressure source (pump housing 14).
  • a deflector 22 or device for orienting the jet of mixture introduced into the cylinder is for example of the type described in patent EP-189,715.
  • valve 19 is controlled mechanically, for example by a cam 23 driven in rotation at the speed of the motor. This cam controls the movement of the valve 19 by means of a pusher 24. The valve 19 is returned by a spring 25. It will not depart from the scope of the present invention if this valve is controlled by another means, such as electromagnetic means.
  • valve 19 is not controlled. It is simply fitted with a return spring 25. It is left free to move as a function of the upstream and downstream pressure differences. It then acts like a flap or automatic valve.
  • the duct 15 coming from the source of compressed air 14 is connected to an injection light opening into the walls of the cylinder and preferably to a rear injection light 6, so called because it is substantially opposite to the exhaust light.
  • a non-return valve 26 prevents the gases from the cylinder 1 from entering the casing 14 during the vacuum phase of the latter.
  • This fuel metering and introduction device 27 can be a low-pressure injector that is commercially available, or a fuel pump actuated by the successive pressures and depressions of a pump housing (Fig. 8) , or a conventional carburetor actuated by the air flow passing through it. In the latter case, a second external air intake circuit should be provided, for example through this carburetor and through the duct 15. A schematic representation is made of it in FIG. 10.
  • the notch 12 makes it possible to direct the mixture injected into the cylinder 1 as well as to define the timing of the injection. This can also be obtained by making a bevel or a notch on the part of the piston which cooperates with the injection port.
  • the cylinder 1 of FIG. 5 may include a rear transfer light and a rear transfer duct (not represented).
  • the spraying of the fuel mixture may be advantageously improved by a device of the nozzle-venturi type 2B placed just upstream of the valve 26 in accordance with patent FR-2,575,521.
  • valve 26 is replaced by a rotary plug 29 driven by the rotation of the motor and thus preferably controlling the opening of the light 6.
  • FIG. 7 indicates the case of FIG. 6 where the pressure source is provided by the movement in the pump housing 14 of a piston 2R angularly delayed by 90 ° crankshaft relative to the movement of the piston 2 of the cylinder considered 1. It is obvious that the cases of FIGS. 3, 4, 5 could also be described in the same way with this delay of 90 ° crankshaft instead of 120 °.
  • FIG. 8 shows a schematic representation of a fuel metering device which can be used in place of the devices 20 or 27.
  • This device pumps the fuel from the tank 30 via the non-return valve 31 to the duct 34, through the non-return valve 33.
  • the membrane 32 acts as a fuel pump. On the one hand it is in contact with the fuel it pumps. On the other side, its reciprocating movement which allows this pump role is actuated by the pressure pulses coming from a pump casing which can be either casing 7 or casing 14 and which is connected to this side of the membrane via conduit 35.
  • the latter is under vacuum and therefore controls the diaphragm 32 so as to increase the volume 36 thereby sucking fuel through the valve 31 which opens. Then, during the compression phase of the crankcase, the movement of the diaphragm 32 reduces the volume 36 and therefore pumps the fuel into the duct 34 via the valve 33.
  • This device therefore acts as a pump and fuel metering. It is slaved to engine speed, since it provides one pump movement per revolution, and it is also slaved to load, since the amplitude of the pressure pulses in the crankcase is proportional to the load.
  • the pipe 34 is then directly connected to the location in the pipe 15 where the fuel is introduced.
  • the opening of the duct 34 is adjusted as a function of the load by a needle 37 which can be actuated either directly or indirectly by a lever 38 connected to another membrane 39.
  • the other side of the membrane 39 is again in communication with the pressure of a motor crankcase via a conduit 40.
  • the inertia of the assembly constituted by the needle 37, the lever 38 and the membrane 39 is chosen such that it does not allow movement of the membrane 39 according to the pulsations of instantaneous pressure of a casing. It must be studied in order to be controlled only by the average pressure of a crankcase, a pressure which is directly representative of the engine load. This results in a position of the metering needle directly representative of the engine load. At the point of the needle, the fuel thus dosed is guided by the pipe 41 to the place of introduction into the pipe 15.
  • Figure 10 shows another particularly simple embodiment of the metering device.
  • the carburetor is for example a carburetor of the conventional type for 2-stroke engine, with plug and needle correcting the nozzle nozzle with the load.
  • the assembly then forms a true second very rich mixture intake circuit, separated from the intake via the air valve 8 only.
  • the length of the conduit 15 may be studied so as not to allow the fuel mixture thus admitted into this conduit to reach the pump housing 14 before being pushed back into the cylinder 1 by the pressure of the pump housing 14 returned to the compression phase. .
  • Another very advantageous advantage lies in the fact that, in the case of a multi-cylinder engine whose set of cylinders operates according to the principle of the invention, with the suitable combinations of conduits 15, a single carburetor 42 can be used for all of the cylinders. Downstream of the carburetor, the different conduits 44 can be separated to end up at the different cylinders, in order to be able to supply with fuel mixture their respective conduits 15 through their respective valves 43.
  • the carburetor device of FIG. 10 a variant of the case of FIG. 5, can also be adapted to the case of FIGS. 3, 4 and 6.
  • the duct 15 connects the transfer duct 17R of the overdue cylinder 11 to the fuel supply orifice of the cylinder in question, the transfer duct 17R being that in which the flow occurs in return.
  • the conduit 15 is connected to the pump housing so that the effects of the return flow pass through the pump housing.
  • Figures 11 and 12 show the interconnection between the conduit 15, the rear transfer conduit 17R and the rear transfer lumen 6R.
  • a valve 45 (Fig. 12) may be installed in the transfer duct 17R in order to minimize the effects of the flow back from the cylinder 2R to the casing 14 while keeping the advantages of injection at the injection level. cited above.
  • a system having the same purpose can be achieved by playing only on the aerodynamics of the conduits by the interposition of a profiled part 46 (FIG. 11).
  • This profiled part has an edge 47 which is flush with the cylinder 11 at the level of the rear transfer lumen 6R in which the return flow takes place.
  • This edge 47 divides the orifice 6R into two parts, an upper part and a lower part.
  • the orifice 51 serves to facilitate the passage of the gases coming from the conduit 17R.
  • the piston 2R is bevelled at 52 so as to make it possible to anticipate the opening of the light 6R so that a return flow occurs there.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

La présente invention a pour objet un procédé et des dispositifs améliorant l'introduction sous pression de mélange carburé en fin de balayage par l'air dans un cylindre de moteur 2-temps. Selon la présente invention, la source de pression utilisée est fournie par la pression régnant dans le carter-pompe du cylindre qui est en retard de 120° vilebrequin (cas d'un moteur 3, 6, ..., 3n cylindres) ou par le carter du cylindre en retard de 90° vilebrequin (cas d'un moteur 4, 8, ..., 4n cylindres) par rapport au cylindre considéré où a lieu l'introduction de mélange carburé, ainsi que par l'écoulement en retour (généralement désigné par le terme anglo-saxon de "back-flow") que l'on provoque dans un conduit de transfert du cylindre en retard, ce conduit de transfert reliant ce cylindre à son carter-pompe (back-flow cylindre-carter).The present invention relates to a method and devices improving the introduction under pressure of a fuel mixture at the end of air sweeping in a 2-stroke engine cylinder. According to the present invention, the pressure source used is supplied by the pressure prevailing in the cylinder crankcase which is 120 ° behind the crankshaft (in the case of a 3, 6, ..., 3n cylinder engine) or by the cylinder crankcase 90 ° behind the crankshaft (in the case of a 4, 8, ..., 4n cylinder engine) with respect to the cylinder in question where the fuel mixture takes place, as well as by the return flow (generally designated by the Anglo-Saxon term of "back-flow") which is caused in a transfer duct of the late cylinder, this transfer duct connecting this cylinder to its pump casing (back-flow cylinder-casing ).

L'art antérieur est notamment illustré par les documents EP-A-0.192.010 et EP-A-0.296.969 qui divulguent des moteurs multicylindres dont les cycles sont décalés angulairement et pour lesquels la source de pression utilisée dans un cylindre pour l'injection pneumatique de carburant, par exemple, est fournie par la pression régnant dans un carter-pompe en retard par rapport au cylindre considéré.The prior art is illustrated in particular by documents EP-A-0.192.010 and EP-A-0.296.969 which disclose multi-cylinder engines whose cycles are angularly offset and for which the pressure source used in a cylinder for the Pneumatic fuel injection, for example, is provided by the pressure prevailing in a pump housing which is lagging behind the cylinder in question.

L'introduction de mélange carburé sous pression se produit à l'arrivée des gaz provenant de cette source de pression dans le cylindre considéré pendant sa phase de fin de balayage. L'arrivée du gaz provenant du carter-pompe dans un dispositif de dosage de carburant prépare un mélange carburé pouvant être introduit dans le cylindre à travers un orifice.The introduction of a fuel mixture under pressure occurs on the arrival of gases from this pressure source in the cylinder considered during its end of sweeping phase. The arrival of gas from the pump housing into a fuel metering device prepares a fuel mixture which can be introduced into the cylinder through an orifice.

Selon la présente invention, l'introduction et éventuellement la préparation du mélange carburé dans le cylindre considéré est prolongée et améliorée par l'utilisation des gaz en retour dans le conduit de transfert provenant du cylindre en retard et qui sont à un niveau de presion élevé.According to the present invention, the introduction and optionally the preparation of the fuel mixture into the cylinder in question is prolonged and improved by the use of return gases in the transfer duct coming from the lagging cylinder and which are at a high pressure level. .

L'utilisation de ces gaz en retour pourra être faite directement. Dans ces conditions on aura une liaison directe entre le conduit de transfert et le dispositif de dosage du carburant ou directement en effectuant un transit par le carter-pompe du cylindre en retard.The use of these gases in return can be made directly. Under these conditions there will be a direct connection between the transfer duct and the fuel metering device or directly by performing a transit through the pump housing of the late cylinder.

L'orifice d'introduction du mélange carburé dans le cylindre considéré pourra être, de préférence, ouvert uniquement pendant l'arrivée des gaz en provenance du carter-pompe du cylindre en retard et du cylindre en retard lui-même. Cet orifice peut se trouver dans la culasse.The opening for introducing the fuel mixture into the cylinder in question may preferably be opened only during the arrival of the gases coming from the pump housing of the late cylinder and of the late cylinder itself. This hole can be in the cylinder head.

Dans ce cas, le dispositif peut comporter une soupape commandée pour s'ouvrir pendant l'arrivée des gaz de cette source de pression, ou une soupape automatique (type clapet anti-retour) dont l'ouverture est commandée par la différence entre la pression provenant de la source de pression et la pression du cylindre considéré.In this case, the device may include a valve controlled to open during the arrival of the gases from this pressure source, or an automatic valve (non-return valve type), the opening of which is controlled by the difference between the pressure from the pressure source and the pressure of the cylinder considered.

L'orifice peut aussi se trouver dans le cylindre. Son ouverture peut alors en être contrôlée par le mouvement du piston (cas d'une lumière) combiné à un dispositif anti-retour de type clapet (ou à un boisseau rotatif).The hole can also be in the cylinder. Its opening can then be controlled by the movement of the piston (in the case of a light) combined with a non-return device of the valve type (or with a rotary plug).

Par exemple, un mode de réalisation de ce type peut consister à relier le carter du cylindre retardé d'un angle de 120 ou 90° du vilebrequin par rapport au cylindre considéré, via un conduit de liaison débouchant du côté opposé à l'échappement dans le cylindre considéré (conduit généralement appelé conduit de transfert arrière).For example, an embodiment of this type may consist in connecting the cylinder housing delayed by an angle of 120 or 90 ° of the crankshaft relative to the cylinder in question, via a connection conduit opening on the side opposite to the exhaust in the cylinder in question (conduit generally called rear transfer conduit).

Dans la mesure où le lieu de dosage du carburant (en amont de l'orifice d'injection débouchant dans le cylindre) n'est pas sous une pression supérieure à la pression ambiante pendant tout le temps en dehors de la période d'introduction de mélange carburé, ce dosage peut s'effectuer à l'aide d'injecteurs basse pression, mais aussi à l'aide de dispositifs plus simples, comme, par exemple, un carburateur du type de ceux utilisés à l'admission d'un moteur deux-temps.Insofar as the fuel metering location (upstream of the injection orifice opening into the cylinder) is not under a pressure higher than ambient pressure for all the time outside the period of introduction of fuel mixture, this metering can be carried out using '' low pressure injectors, but also using simpler devices, such as, for example, a carburetor of the type used for the intake of a two-stroke engine.

D'une manière générale, la présente invention concerne un dispositif d'introduction sous pression du mélange carburé dans un premier cylindre d'un moteur à combustion interne, ce moteur comportant au moins un autre cylindre ayant un carter-pompe, ledit carter-pompe communiquant avec ledit autre cylindre via au moins une lumière de transfert et du type comportant une canalisation de liaison entre ledit carter-pompe et le premier cylindre. Un décalage angulaire non nul existe entre le cycle de chacun desdits cylindres du moteur. Selon l'invention un conduit de transfert relie ladite lumière de transfert à ladite canalisation de liaison et ladite lumière de transfert est positionnée de façon à ce qu'il s'y produise un écoulement en retour pendant une partie du cycle.In general, the present invention relates to a device for introducing under pressure the fuel mixture into a first cylinder of an internal combustion engine, this engine comprising at least one other cylinder having a pump housing, said pump housing communicating with said other cylinder via at least one transfer lumen and of the type comprising a connecting pipe between said pump housing and the first cylinder. A non-zero angular offset exists between the cycle of each of said engine cylinders. According to the invention, a transfer duct connects said transfer lumen to said connecting pipe and said transfer lumen is positioned so that there is a return flow during part of the cycle.

Le décalage angulaire pourra être de 120° et le cycle du premier cylindre pourra précéder le cycle de l'autre cylindre de 120°.The angular offset can be 120 ° and the cycle of the first cylinder can precede the cycle of the other cylinder by 120 °.

De même, le décalage angulaire pourra être de 90° et le cycle du premier cylindre pourra précéder de 90° le cycle de l'autre cylindre.Similarly, the angular offset can be 90 ° and the cycle of the first cylinder can precede by 90 ° the cycle of the other cylinder.

Le dispositif selon l'invention s'applique notamment aux moteurs comportant un nombre de cylindres multiple de 3 ou 4.The device according to the invention applies in particular to engines comprising a number of cylinders multiple of 3 or 4.

La canalisation pourra déboucher dans le premier cylindre au voisinage de la culasse du moteur.The pipeline may open into the first cylinder in the vicinity of the cylinder head of the engine.

De même la canalisation pourra déboucher dans le premier cylindre sur la paroi latérale de ce cylindre, sensiblement à la partie basse de ce cylindre.Likewise, the pipeline may open into the first cylinder on the side wall of this cylinder, substantially at the bottom of this cylinder.

Le dispositif selon l'invention pourra comporter un organe d'obturation placé entre la canalisation et le premier cylindre, sensiblement au voisinage de ce dernier.The device according to the invention may include a shutter member placed between the pipe and the first cylinder, substantially in the vicinity of the latter.

L'organe d'obturation pourra être une soupape commandée par une came, ou un boisseau tournant.The shutter member may be a valve controlled by a cam, or a rotating plug.

De même, l'organe d'obturation pourra être automatique et être adapté à agir à la manière d'un clapet.Likewise, the shutter member may be automatic and be adapted to act like a valve.

La canalisation pourra comporter un organe d'introduction et de dosage de carburant.The pipeline may include a fuel introduction and metering device.

Ce dispositif d'introduction du carburant pourra être un injecteur basse pression, de même qu'il pourra comporter une buse venturi associée audit injecteur basse pression.This fuel introduction device may be a low pressure injector, just as it may include a venturi nozzle associated with said low pressure injector.

Le dispositif d'introduction du carburant pourra être un carburateur.The fuel introduction device may be a carburetor.

La commande de ce carburateur pourra être couplée avec une commande qui contrôle la quantité de gaz introduite dans le carter-pompe du premier cylindre.The control of this carburetor can be coupled with a control that controls the amount of gas introduced into the pump housing of the first cylinder.

Le dispositif selon l'invention pourra comporter entre le carburateur et la canalisation un élément anti- retour tel un clapet.The device according to the invention may comprise between the carburetor and the pipe a non-return element such as a valve.

On ne sortira pas du cadre de la présente invention si l'organe d'introduction et de dosage du carburant comporte une pompe à membrane actionnée par les pulsations de pression d'un carter-pompe.It will not depart from the scope of the present invention if the fuel introduction and metering member comprises a diaphragm pump actuated by the pressure pulses of a pump housing.

Le conduit de sortie de cette pompe à membrane qui relie cette dernière à la canalisation, pourra comporter un système d'ajustement de sa section de passage. Ce système pourra comporter un pointeau et des moyens de commande prenant en compte la pression moyenne d'un carter.The outlet duct of this diaphragm pump which connects the latter to the pipeline, may include a system for adjusting its passage section. This system may include a needle and control means taking into account the average pressure of a casing.

Ladite canalisation de liaison pourra avantageusement posséder une partie commune avec le conduit de transfert qui relie le carter-pompe avec ladite lumière.Said connecting pipe may advantageously have a common part with the transfer duct which connects the pump housing with said lumen.

Une pièce profilée aérodynamique pourra être placée à l'interconnexion de la canalisation de liaison, dudit conduit de transfert et de ladite lumière de transfert.An aerodynamic profiled part may be placed at the interconnection of the connecting pipe, said transfer duct and said transfer lumen.

Un clapet anti-retour pourra être placé sur ledit conduit de transfert, ledit clapet n'autorisant pas l'écoulement en retour vers le carter-pompe.A non-return valve may be placed on said transfer duct, said valve not allowing flow back to the pump housing.

Le piston dudit autre cylindre pourra être biseauté ou échancré sur une partie de sa surface pour permettre un écoulement en retour à travers au moins une lumière de transfert afin de faciliter l'écoulement en retour.The piston of said other cylinder may be bevelled or scalloped over a part of its surface to allow a return flow through at least one transfer lumen in order to facilitate the return flow.

La lumière où se produit l'écoulement en retour pourra être positionné pour que ledit écoulement se produise seulement après qu'au moins une lumière d'échappement dudit autre cylindre ait été découverte par ledit piston dudit autre cylindre.The lumen where the back flow occurs may be positioned so that said flow occurs only after at least one exhaust lumen of said other cylinder has been discovered by said piston of said other cylinder.

La présente invention concerne également une méthode d'introduction sous pression du mélange carburé dans un premier cylindre d'un moteur à combustion interne, ce moteur comportant au moins un autre cylindre ayant un carter-pompe, ce carter-pompe communiquant avec ledit autre cylindre par au moins une lumière de transfert. Le moteur comporte de préférence une canalisation de liaison entre ledit carter-pompe et le premier cylindre, et un décalage angulaire non nul existe entre les cycles des cylindres de sorte que l'on peut utiliser la pression des gaz contenus dans ledit carter-pompe comme source de pression pour injecter le mélange carburé dans le premier cylindre. La méthode selon l'invention se caractérise en ce que l'on provoque un écoulement en retour à travers ladite lumière de transfert pour accroître momentanément la pression dans ledit carter ou dans un conduit de transfert reliant ladite lumière à ladite canalisation de liaison.The present invention also relates to a method of introducing under pressure the fuel mixture into a first cylinder of an internal combustion engine, this engine comprising at least one other cylinder having a pump housing, this pump housing communicating with said other cylinder. by at least one transfer light. The engine preferably comprises a connecting pipe between said pump housing and the first cylinder, and a non-zero angular offset exists between the cycles of the cylinders so that the pressure of the gases contained in said pump housing can be used as pressure source for injecting the fuel mixture into the first cylinder. The method according to the invention is characterized in that a backward flow is caused through said transfer lumen to increase momentarily the pressure in said casing or in a transfer conduit connecting said lumen to said connecting pipe.

Lorsque la présente invention est appliquée à un moteur multicylindre dans lequel chaque cylindre comporte un carter-pompe, chacun des cylindres pourra être connecté, directement ou non, à un carter-pompe d'un autre cylindre retardé angulairement par rapport au cylindre considéré.When the present invention is applied to a multi-cylinder engine in which each cylinder comprises a pump housing, each of the cylinders may be connected, directly or not, to a pump housing of another cylinder angularly delayed relative to the cylinder considered.

Ainsi, dans le cas d'un moteur à trois cylindres ayant chacun un carter-pompe, chaque cylindre pourra être en liaison avec le carter-pompe du cylindre qui en retard de 120° vilebrequin par rapport au cylindre considéré.Thus, in the case of a three-cylinder engine each having a pump housing, each cylinder may be in connection with the pump housing of the cylinder which is 120 ° behind the crankshaft relative to the cylinder considered.

L'invention sera bien comprise à la lecture de la description suivante d'exemples de réalisation, illustrée par les figures annexées, parmi lesquelles :

  • la figure 1 illustre les courbes de pression régnant dans le carter du cylindre en retard et dans le cylindre en retard,
  • la figure 2 illustre les courbes de pression dans le conduit de transfert du cylindre en retard et dans le cylindre considéré,
  • la figure 3 est relative au cas d'une introduction retardée de 120° Vilebrequin du mélange carburé dans la chambre de combustion du cylindre considéré, via une soupape commandée,
  • la figure 4 montre le cas d'une introduction retardée de 120° vilebrequin du mélange carburé dans la chambre de combustion du cylindre considéré, via une soupape automatique,
  • la figure 5 illustre le cas d'une introduction retardée de 120° vilebrequin du mélange carburé par une lumière arrière du cylindre considéré, via un clapet anti-retour,
  • la figure 6 est relative au cas d'une introduction retardée de 120° vilebrequin de mélange carburé par une lumière arrière du cylindre considéré, via un boisseau rotatif,
  • la figure 7 montre le cas d'une introduction retardée de 90° vilebrequin de mélange carburé dans une lumière arrière du cylindre considéré,
  • la figure 8 illustre un dispositif de dosage et d'introduction du carburant par la pression régnant dans le carter,
  • la figure 9 est semblable à la figure 8, mais avec le perfectionnement du dispositif de dosage en fonction de la charge du moteur,
  • la figure 10 montre le cas d'une introduction de mélange carburé préalablement admis via un carburateur classique,
  • la figure 11 représente la mise en place d'un déflecteur profilé, ou pièce aérodynamique,
  • la figure 12 illustre un mode de réalisation particulier dans lequel le conduit de transfert comporte un clapet, et
  • la figure 13 montre le cas où le piston comporte une échancrure au déflecteur permettant de libérer plus tôt une lumière de transfert relativement à d'autres lumières de transfert de ce même cylindre.
The invention will be clearly understood on reading the following description of exemplary embodiments, illustrated by the appended figures, among which:
  • FIG. 1 illustrates the pressure curves prevailing in the case of the late cylinder and in the late cylinder,
  • FIG. 2 illustrates the pressure curves in the transfer duct of the late cylinder and in the cylinder considered,
  • FIG. 3 relates to the case of a delayed introduction of 120 ° crankshaft of the fuel mixture into the combustion chamber of the cylinder in question, via a controlled valve,
  • FIG. 4 shows the case of a delayed introduction of 120 ° crankshaft of the fuel mixture into the combustion chamber of the cylinder in question, via an automatic valve,
  • FIG. 5 illustrates the case of a delayed introduction of 120 ° crankshaft of the fuel mixture by a rear light of the cylinder in question, via a non-return valve,
  • FIG. 6 relates to the case of a delayed introduction of 120 ° crankshaft of fuel mixture by a rear light of the cylinder in question, via a rotary plug,
  • FIG. 7 shows the case of a delayed introduction of 90 ° crankshaft of fuel mixture into a rear light of the cylinder in question,
  • FIG. 8 illustrates a device for metering and introducing fuel by the pressure prevailing in the crankcase,
  • FIG. 9 is similar to FIG. 8, but with the improvement of the metering device as a function of the engine load,
  • FIG. 10 shows the case of an introduction of a fuel mixture previously admitted via a conventional carburetor,
  • FIG. 11 represents the installation of a profiled deflector, or aerodynamic part,
  • FIG. 12 illustrates a particular embodiment in which the transfer duct comprises a valve, and
  • FIG. 13 shows the case where the piston has a notch in the deflector making it possible to release a transfer lumen earlier relative to other transfer lumens of this same cylinder.

La figure 1 montre en trait plein portant la référence P1, la courbe de variation de la pression en fonction de l'angle de rotation du vilebrequin dans un cylindre d'un moteur deux temps, au voisinage du point mort bas correspondant à un angle vilebrequin de 180°.Figure 1 shows in solid lines with the reference P1, the pressure variation curve as a function of the angle of rotation of the crankshaft in a cylinder of a two-stroke engine, near the bottom dead center corresponding to a crankshaft angle 180 °.

La courbe de variation de la pression du carter équipant ce cylindre est indiquée en pointillé, et porte la référence P2. Selon la présente invention au moins l'une des lumières de transfert qui relie ce cylindre au carter-pompe de ce cylindre par l'intermédiaire d'un conduit de transfert est positionnée suffisamment haut de manière à s'ouvrir avant que la pression du carter-pompe soit supérieure ou égale à la pression dans le cylindre. Ainsi il se produit un écoulement dans le sens inverse de celui généralement admis dans les conduits de transfert. C'est cet écoulement inverse, ou en retour, qui est à l'origine du pic de pression 101 de la figure 1.The curve of variation of the pressure of the casing equipping this cylinder is indicated in dotted lines, and bears the reference P2. According to the present invention at least one of the transfer lights which connects this cylinder to the pump housing of this cylinder via a transfer conduit is positioned high enough to open before the pressure of the housing -pump is greater than or equal to the pressure in the cylinder. Thus there is a flow in the opposite direction to that generally accepted in the transfer conduits. It is this reverse flow, or return, which is the source of the pressure peak 101 in FIG. 1.

Ce pic de pression peut donc permettre de prolonger la durée de l'introduction de mélange carburé pendant toute la partie du cycle de fonctionnement du cylindre considéré où la différence de pression est suffisante pour permettre l'introduction de carburant dans le cylindre. Par le choix et la conception du mode d'introduction adopté : soupape commandée, soupape automatique, lumière plus clapet, ou lumière plus boisseau rotatif, il est possible de contrôler plus ou moins l'instant le plus favorable pour l'introduction de ce mélange carburé.This pressure peak can therefore make it possible to extend the duration of the introduction of fuel mixture during the whole part of the operating cycle of the cylinder considered where the pressure difference is sufficient to allow the introduction of fuel into the cylinder. By the choice and the design of the mode of introduction adopted: controlled valve, automatic valve, light more valve, or light more rotary valve, it is possible to control more or less the most favorable moment for the introduction of this mixture carbide.

La figure 2 montre la courbe de pression P3 dans le cylindre considéré en fonction du degré de rotation du vilebrequin, avec une source de pression P4 provenant d'un conduit de transfert d'un cylindre en retard de 120° vilebrequin par rapport au cylindre considéré. Ceci correspond notamment au cas d'un moteur comportant trois cylindres.Figure 2 shows the pressure curve P3 in the cylinder considered as a function of the degree of rotation of the crankshaft, with a pressure source P4 coming from a transfer duct of a cylinder lagging 120 ° crankshaft relative to the cylinder considered . This corresponds in particular to the case of an engine comprising three cylinders.

Les courbes de pression P2 et P4 sont proches l'une de l'autre puisque l'une P4 est prise dans un conduit de transfert et l'autre P2 dans le carter-pompe reliée à ce conduit de transfert. Sur la figure 2, le pic de pression 102 qui correspond au pic de pression 101, permet à la pression d'injection du carburant d'accompagner pendant un temps suffisamment long la courbe de pression P3 dans le cylindre. Il est ainsi possible d'améliorer l'injection.The pressure curves P2 and P4 are close to each other since one P4 is taken in a transfer duct and the other P2 in the pump housing connected to this transfer duct. In FIG. 2, the pressure peak 102 which corresponds to the pressure peak 101, allows the fuel injection pressure to accompany for a sufficiently long time the pressure curve P3 in the cylinder. It is thus possible to improve the injection.

Ainsi, le pic de pression 102 peut être choisi pour se produire pendant la fin de la période d'injection, au moment où la pression cylindre augmente (début de compression) et où donc une pression d'injection plus élevée est nécessaire pour continuer l'introduction du mélange injecté dans le sens organe d'injection vers cylindre et éviter l'inversion de sens en fin d'injection, une telle inversion pouvant être responsable d'une perte de la compression et du remplissage cylindre.Thus, the pressure peak 102 can be chosen to occur during the end of the injection period, at the moment when the cylinder pressure increases (start of compression) and therefore a higher injection pressure is necessary to continue l introduction of the injected mixture in the direction of injection member towards cylinder and avoid reversal of direction at the end of injection, such inversion may be responsible for a loss of compression and cylinder filling.

Dans le cas d'un moteur multicylindre, le conduit de raccordement entre les deux "cylindres" externes étant plus long, on pourra palier, si nécessaire, à cet inconvénient en plaçant, dans le cylindre, la lumière de transfert alimentant le conduit de raccordement entre les deux cylindres externes plus haut que ne le sont les autres lumières de transfert qui alimentent les conduits de raccordement des autres cylindres.In the case of a multi-cylinder engine, the connection conduit between the two external "cylinders" being longer, this disadvantage can be overcome, if necessary, by placing, in the cylinder, the transfer light supplying the connection conduit between the two external cylinders higher than the other transfer lights which supply the connection conduits of the other cylinders.

Les figures 3, 4, 5, 6, 7 représentent en traits pleins le cylindre considéré 1 avec son piston 2 en fin de balayage, son échappement 3, sa lumière d'échappement 4 qui est sur le point d'être fermée, ses lumières de transfert latérales 5, et arrière 6, son carter 7 avec une admission d'air uniquement, par exemple par clapets 8, sa bougie d'allumage 9, le système bielle-manivelle 10.Figures 3, 4, 5, 6, 7 show in solid lines the cylinder considered 1 with its piston 2 at the end of scanning, its exhaust 3, its exhaust light 4 which is about to be closed, its lights lateral transfer 5, and rear transfer 6, its casing 7 with an air intake only, for example by valves 8, its spark plug 9, the rod-crank system 10.

En traits mixtes est représenté le cylindre 11 ayant un piston 2R dont le mouvement est retardé angulairement de 120° par l'intermédiaire du système bielle-manivelle 13, par rapport au piston 2 du cylindre considéré 1. Le piston 2R est en phase de détente dans le cylindre 11 et en même temps de compression dans le carter-pompe 14.In dashed lines is shown the cylinder 11 having a piston 2R whose movement is angularly delayed by 120 ° by means of the rod-crank system 13, relative to the piston 2 of the cylinder considered 1. The piston 2R is in the expansion phase in the cylinder 11 and at the same time of compression in the pump housing 14.

Le carter-pompe 14 dont le mouvement du piston 2R est retardé angulairement de 120° fournit la source de pression à travers le conduit 15.The pump housing 14 whose movement of the piston 2R is angularly delayed by 120 ° supplies the source of pressure through the conduit 15.

La lumière de transfert 6R du cylindre 11 est positionnée suffisamment haut pour qu'il y ait un écoulement en retour.The transfer light 6R of the cylinder 11 is positioned high enough for there to be a return flow.

On a supposé à la figure 3 que le cylindre 1 sert à son tour comme source de pression à un autre cylindre. Ainsi, le cylindre 1 est identique dans sa configuration au cylindre 11 en ce qui concerne notamment le positionnement des lumières.It has been assumed in FIG. 3 that the cylinder 1 in turn serves as a source of pressure for another cylinder. Thus, the cylinder 1 is identical in its configuration to the cylinder 11 with regard in particular to the positioning of the lights.

L'écoulement en retour dans le carter 7 est permis par le fait que la lumière de transfert arrière 6 est surélevée par rapport à ce que devrait être sa hauteur normale pour qu'il n'y ait pas d'écoulement inverse. Cette hauteur normale est représentée par la position de la lumière de transfert latérale 5.The flow back into the casing 7 is allowed by the fact that the rear transfer light 6 is raised relative to what should be its normal height so that there is no reverse flow. This normal height is represented by the position of the lateral transfer lumen 5.

Comme cela est représenté à la figure 3, il y a un décalage DH1 entre le sommet des lumières arrières 6 et 5. Cependant, dans le cas représenté à la figure 3, la lumière de transfert arrière 6 s'ouvre plus tard que la lumière d'échappement 4. L'écart entre le sommet de la lumière 6 et la lumière d'échappement 4 est la référence DH2.As shown in Figure 3, there is a DH1 offset between the top of the rear lights 6 and 5. However, in the case shown in Figure 3, the rear transfer light 6 opens later than the light exhaust 4. The distance between the top of the light 6 and the exhaust light 4 is the reference DH2.

Dans le cas des figures 3 et 4, le conduit 15 est relié à la chambre de combustion 16 du cylindre considéré 1.In the case of FIGS. 3 and 4, the duct 15 is connected to the combustion chamber 16 of the cylinder considered 1.

L'introduction de l'air sous pression provenant du carter-pompe 14 dans la chambre 16 se fait par un orifice 18 dont l'ouverture est commandée par une soupape 19. En amont de la soupape se trouve un dispositif d'introduction et de dosage basse-pression du carburant 20.The introduction of the pressurized air from the pump housing 14 into the chamber 16 takes place through an orifice 18, the opening of which is controlled by a valve 19. Upstream of the valve is a device for introducing and low-pressure fuel metering 20.

Ce dispositif peut être un injecteur basse-pression que l'on trouve dans le commerce, ou une pompe de carburant actionnée par les pressions et dépressions successives d'un carter-pompe. Un schéma de ce dernier dispositif sera précisé à la figure 8. L'introduction du carburant liquide peut avoir lieu dans le conduit 15, aussi bien pendant tout le temps où la soupape 19 est fermée que pendant celui où elle est ouverte.This device can be a low-pressure injector that is commercially available, or a fuel pump actuated by the successive pressures and depressions of a pump housing. A diagram of this latter device will be specified in FIG. 8. The introduction of the liquid fuel can take place in the duct 15, both during the whole time when the valve 19 is closed and during that when it is open.

Ce dispositif 20 de dosage et d'introduction du carburant peut être associé à une buse-venturi 21 placée dans le conduit 15, juste en amont de la soupape 19 et de l'orifice 18, conformément au brevet EP-189.714, afin d'améliorer la pulvérisation du carburant par l'air provenant de la source de pression (carter-pompe 14).This fuel metering and introduction device 20 can be associated with a venturi nozzle 21 placed in the duct 15, just upstream from the valve 19 and the orifice 18, in accordance with patent EP-189,714, in order to improve the spraying of fuel with air from the pressure source (pump housing 14).

Juste en aval de l'orifice 18, on peut aussi avantageusement placer un déflecteur 22, ou dispositif d'orientation du jet de mélange introduit dans le cylindre. Ce dispositif faisant partie de la culasse ou rapporté sur la culasse est par exemple du type décrit dans le brevet EP-189.715.Just downstream of the orifice 18, it is also advantageously possible to place a deflector 22, or device for orienting the jet of mixture introduced into the cylinder. This device forming part of the cylinder head or attached to the cylinder head is for example of the type described in patent EP-189,715.

Dans le cas particulier de la figure 3, la soupape 19 est commandée mécaniquement, par exemple par une came 23 entraînée en rotation à la vitesse du moteur. Cette came commande le mouvement de la soupape 19 par l'intermédiaire d'un poussoir 24. Le rappel de la soupape 19 se fait par un ressort 25. On ne sortira pas du cadre de la présente invention si cette soupape est commandée par un autre moyen, tel que des moyens électromagnétiques.In the particular case of FIG. 3, the valve 19 is controlled mechanically, for example by a cam 23 driven in rotation at the speed of the motor. This cam controls the movement of the valve 19 by means of a pusher 24. The valve 19 is returned by a spring 25. It will not depart from the scope of the present invention if this valve is controlled by another means, such as electromagnetic means.

Dans le cas particulier de la figure 4 qui illustre une autre variante, la soupape 19 n'est pas commandée. Elle est simplement équipée d'un ressort de rappel 25. Elle est laissée libre de se déplacer en fonction des différences de pression amont et aval. Elle agit alors à la manière d'un clapet ou soupape automatique.In the particular case of FIG. 4 which illustrates another variant, the valve 19 is not controlled. It is simply fitted with a return spring 25. It is left free to move as a function of the upstream and downstream pressure differences. It then acts like a flap or automatic valve.

Dans le cas des deux figures 3 et 4, quand la pression dans le carter 14 est supérieure à la pression dans le cylindre 1 considéré, l'introduction de mélange carburé peut se produire dans le cylindre 1, soit au moment commandé choisi (Fig. 3), soit automatiquement pendant cette période de différence de pression, entre carter 14 et cylindre 1 (Fig. 4). Dans les deux cas, le mouvement du piston 2 est tel qu'il ferme la lumière d'échappement 4 avant que le carburant ait pu s'échapper du cylindre 1 dans l'échappement 3, à travers cette même lumière 4.In the case of the two figures 3 and 4, when the pressure in the casing 14 is higher than the pressure in the cylinder 1 considered, the introduction of fuel mixture can occur in the cylinder 1, either at the selected controlled time (FIG. 3), or automatically during this period of pressure difference, between casing 14 and cylinder 1 (Fig. 4). In both cases, the movement of the piston 2 is such that it closes the exhaust port 4 before the fuel can escape from the cylinder 1 in the exhaust 3, through this same port 4.

Dans le cas des figures 5 et 6, le conduit 15 provenant de la source d'air comprimé 14 est relié à une lumière d'injection débouchant dans les parois du cylindre et préférentiellement à une lumière d'injection arrière 6, ainsi nommée car elle est sensiblement opposée à la lumière d'échappement. A proximité de la lumière 6 et en aval de celle-ci, un clapet anti-retour 26 empêche les gaz du cylindre 1 de pénétrer dans le carter 14 pendant la phase de dépression de ce dernier.In the case of FIGS. 5 and 6, the duct 15 coming from the source of compressed air 14 is connected to an injection light opening into the walls of the cylinder and preferably to a rear injection light 6, so called because it is substantially opposite to the exhaust light. Near the light 6 and downstream from it, a non-return valve 26 prevents the gases from the cylinder 1 from entering the casing 14 during the vacuum phase of the latter.

En amont du clapet, se trouve le dispositif 27 de dosage et d'introduction basse-pression du carburant. Cette introduction de carburant peut avoir lieu à n'importe quel moment du cycle, même quand la lumière 6 est obturée par le piston 2.Upstream of the valve, there is the device 27 for metering and introducing low-pressure fuel. This fuel introduction can take place at any time during the cycle, even when the light 6 is closed by the piston 2.

Ce dispositif 27 de dosage et d'introduction du carburant peut être un injecteur basse-pression que l'on trouve dans le commerce, ou une pompe de carburant actionnée par les pressions et dépressions successives d'un carter-pompe (Fig. 8), ou encore un carburateur classique actionné par le débit d'air le traversant. Dans ce dernier cas, il convient de prévoir un deuxième circuit d'admission d'air extérieur, par exemple à travers ce carburateur et à travers le conduit 15. Une représentation schématique en est faite à la figure 10.This fuel metering and introduction device 27 can be a low-pressure injector that is commercially available, or a fuel pump actuated by the successive pressures and depressions of a pump housing (Fig. 8) , or a conventional carburetor actuated by the air flow passing through it. In the latter case, a second external air intake circuit should be provided, for example through this carburetor and through the duct 15. A schematic representation is made of it in FIG. 10.

L'échancrure 12 permet de diriger le mélange injecté dans le cylindre 1 ainsi que de définir le calage de l'injection. Ceci peut être également obtenu en pratiquant un biseautage ou une échancrure sur la partie du piston qui coopère avec la lumière d'injection.The notch 12 makes it possible to direct the mixture injected into the cylinder 1 as well as to define the timing of the injection. This can also be obtained by making a bevel or a notch on the part of the piston which cooperates with the injection port.

Bien entendu, le cylindre 1 de la figure 5 pourra comporter une lumière de transfert arrière et un conduit de transfert arrière (non représentés).Of course, the cylinder 1 of FIG. 5 may include a rear transfer light and a rear transfer duct (not represented).

Dans tous les cas, la pulvérisation du mélange carburé pourra être avantageusement améliorée par un dispositif de type buse-venturi 2B placé juste en amont du clapet 26 conformément au brevet FR-2.575.521.In all cases, the spraying of the fuel mixture may be advantageously improved by a device of the nozzle-venturi type 2B placed just upstream of the valve 26 in accordance with patent FR-2,575,521.

Dans le cas de la figure 6, le clapet 26 est remplacé par un boisseau rotatif 29 entraîné par la rotation du moteur et commandant ainsi préférentiellement l'ouverture de la lumière 6.In the case of FIG. 6, the valve 26 is replaced by a rotary plug 29 driven by the rotation of the motor and thus preferably controlling the opening of the light 6.

La figure 7 indique le cas de la figure 6 où la source de pression est fournie par le mouvement dans le carter-pompe 14 d'un piston 2R retardé angulairement de 90° vilebrequin par rapport au mouvement du piston 2 du cylindre considéré 1. Il est évident que les cas des figures 3, 4, 5 pourraient être décrits aussi de la même façon avec ce retard de 90° vilebrequin au lieu de 120°.FIG. 7 indicates the case of FIG. 6 where the pressure source is provided by the movement in the pump housing 14 of a piston 2R angularly delayed by 90 ° crankshaft relative to the movement of the piston 2 of the cylinder considered 1. It It is obvious that the cases of FIGS. 3, 4, 5 could also be described in the same way with this delay of 90 ° crankshaft instead of 120 °.

La figure 8 montre une représentation schématique d'un dispositif de dosage de carburant pouvant être utilisé en lieu et place des dispositifs 20 ou 27.FIG. 8 shows a schematic representation of a fuel metering device which can be used in place of the devices 20 or 27.

Ce dispositif pompe le carburant du réservoir 30 via le clapet anti-retour 31 jusqu'au conduit 34, à travers le clapet anti-retour 33. La membrane 32 fait office de pompe de carburant. D'un côté elle est en contact avec le carburant qu'elle pompe. De l'autre côté, son mouvement alternatif qui permet ce rôle de pompe est actionné par les pulsations de pression provenant d'un carter-pompe qui peut être indifféremment le carter 7 ou le carter 14 et qui est relié à ce côté de la membrane par le conduit 35.This device pumps the fuel from the tank 30 via the non-return valve 31 to the duct 34, through the non-return valve 33. The membrane 32 acts as a fuel pump. On the one hand it is in contact with the fuel it pumps. On the other side, its reciprocating movement which allows this pump role is actuated by the pressure pulses coming from a pump casing which can be either casing 7 or casing 14 and which is connected to this side of the membrane via conduit 35.

Pendant la phase d'admission du carter-pompe, celui-ci est en dépression et commande donc la membrane 32 de façon à augmenter le volume 36 en aspirant ainsi du carburant à travers le clapet 31 qui s'ouvre. Ensuite, pendant la phase de compression du carter, le mouvement de la membrane 32 réduit le volume 36 et pompe donc le carburant dans le conduit 34 via le clapet 33.During the intake phase of the pump crankcase, the latter is under vacuum and therefore controls the diaphragm 32 so as to increase the volume 36 thereby sucking fuel through the valve 31 which opens. Then, during the compression phase of the crankcase, the movement of the diaphragm 32 reduces the volume 36 and therefore pumps the fuel into the duct 34 via the valve 33.

Ce dispositif fait donc office de pompe et de dosage de carburant. Il est asservi au régime moteur, puisqu'il fournit un mouvement de pompe par tour, et il est aussi asservi à la charge, puisque l'amplitude des pulsations de pression dans le carter est proportionnelle à la charge.This device therefore acts as a pump and fuel metering. It is slaved to engine speed, since it provides one pump movement per revolution, and it is also slaved to load, since the amplitude of the pressure pulses in the crankcase is proportional to the load.

Dans le cas où il est utilisé seul, sans supplément de moyens de dosage plus fins, le conduit 34 est alors directement relié à l'emplacement dans le conduit 15 où a lieu l'introduction du carburant.In the case where it is used alone, without additional finer metering means, the pipe 34 is then directly connected to the location in the pipe 15 where the fuel is introduced.

Dans le cas où un réglage plus fin du débit de carburant par rapport à la charge est nécessaire, l'ouverture du conduit 34 est ajustée en fonction de la charge par un pointeau 37 qui peut être actionné soit directement, soit indirectement par un levier 38 relié à une autre membrane 39. L'autre côté de la membrane 39 est là encore en communication avec la pression d'un carter-pompe du moteur via un conduit 40.In the case where a finer adjustment of the fuel flow rate relative to the load is necessary, the opening of the duct 34 is adjusted as a function of the load by a needle 37 which can be actuated either directly or indirectly by a lever 38 connected to another membrane 39. The other side of the membrane 39 is again in communication with the pressure of a motor crankcase via a conduit 40.

L'inertie de l'ensemble constitué par le pointeau 37, le levier 38 et la membrane 39 est choisie telle qu'elle ne permet pas un mouvement de la membrane 39 suivant les pulsations de pression instantanée d'un carter. Elle doit être étudiée pour n'être commandée que par la pression moyenne d'un carter, pression qui est directement représentative de la charge du moteur. Il en résulte une position du pointeau de dosage directement représentative de la charge du moteur. A l'endroit du pointeau, le carburant ainsi dosé est guidé par le conduit 41 jusqu'au lieu d'introduction dans le conduit 15.The inertia of the assembly constituted by the needle 37, the lever 38 and the membrane 39 is chosen such that it does not allow movement of the membrane 39 according to the pulsations of instantaneous pressure of a casing. It must be studied in order to be controlled only by the average pressure of a crankcase, a pressure which is directly representative of the engine load. This results in a position of the metering needle directly representative of the engine load. At the point of the needle, the fuel thus dosed is guided by the pipe 41 to the place of introduction into the pipe 15.

La figure 10 montre une autre réalisation particulièrement simple du dispositif de dosage.Figure 10 shows another particularly simple embodiment of the metering device.

La source de pression du carter 14 à travers le conduit 15 qui sert à l'introduction de mélange carburé dans le cylindre 1, sert aussi pendant sa phase de dépression à l'aspiration de mélange carburé très riche via un carburateur classique 42 et un dispositif anti-retour de type clapet 43. Le carburateur est par exemple un carburateur du type classique pour moteur 2-temps, à boisseau et aiguille corrigeant l'ajutage du gicleur avec la charge.The pressure source of the casing 14 through the conduit 15 which serves for the introduction of fuel mixture into the cylinder 1, also serves during its vacuum phase for the suction of very rich fuel mixture via a conventional carburetor 42 and a device non-return valve 43. The carburetor is for example a carburetor of the conventional type for 2-stroke engine, with plug and needle correcting the nozzle nozzle with the load.

L'ensemble forme alors un véritable deuxième circuit d'admission de mélange très riche, séparé de l'admission via le clapet 8 d'air uniquement.The assembly then forms a true second very rich mixture intake circuit, separated from the intake via the air valve 8 only.

La longueur du conduit 15 pourra être étudiée pour ne pas permettre au mélange carburé ainsi admis dans ce conduit d'atteindre le carter-pompe 14 avant d'être repoussé dans le cylindre 1 par la pression du carter-pompe 14 revenu en phase de compression.The length of the conduit 15 may be studied so as not to allow the fuel mixture thus admitted into this conduit to reach the pump housing 14 before being pushed back into the cylinder 1 by the pressure of the pump housing 14 returned to the compression phase. .

Un autre avantage très intéressant réside dans le fait que, dans le cas d'un moteur multicylindre dont l'ensemble des cylindres fonctionne suivant le principe de l'invention, avec les combinaisons adaptées de conduits 15, un seul carburateur 42 peut être utilisé pour l'ensemble des cylindres. En aval du carburateur, les différents conduits 44 peuvent se séparer pour aboutir aux différents cylindres, afin de pouvoir alimenter en mélange carburé leurs conduits 15 respectifs à travers leurs clapets respectifs 43.Another very advantageous advantage lies in the fact that, in the case of a multi-cylinder engine whose set of cylinders operates according to the principle of the invention, with the suitable combinations of conduits 15, a single carburetor 42 can be used for all of the cylinders. Downstream of the carburetor, the different conduits 44 can be separated to end up at the different cylinders, in order to be able to supply with fuel mixture their respective conduits 15 through their respective valves 43.

Le dispositif à carburateur de la figure 10, variante du cas de la figure 5, peut aussi s'adapter au cas des figures 3, 4 et 6.The carburetor device of FIG. 10, a variant of the case of FIG. 5, can also be adapted to the case of FIGS. 3, 4 and 6.

Dans les figures 3, 5 et 10, le conduit 15 relie le conduit de transfert 17R du cylindre en retard 11 à l'orifice d'alimentation en carburant du cylindre considéré, le conduit de transfert 17R étant celui dans lequel se produit l'écoulement en retour. Un tel agencement permet de mieux profiter des effets de pression de l'écoulement en retour. Toutefois, on ne sortira pas du cadre de la présente invention si le conduit 15 est relié au carter-pompe de sorte que les effets de l'écoulement en retour transitent par le carter-pompe.In FIGS. 3, 5 and 10, the duct 15 connects the transfer duct 17R of the overdue cylinder 11 to the fuel supply orifice of the cylinder in question, the transfer duct 17R being that in which the flow occurs in return. Such an arrangement makes it possible to take better advantage of the pressure effects of the flow in return. However, it will not depart from the scope of the present invention if the conduit 15 is connected to the pump housing so that the effects of the return flow pass through the pump housing.

Les figures 11 et 12 représentent l'interconnexion entre le conduit 15, le conduit de transfert arrière 17R et la lumière de transfert arrière 6R.Figures 11 and 12 show the interconnection between the conduit 15, the rear transfer conduit 17R and the rear transfer lumen 6R.

Un clapet 45 (Fig. 12) pourra être installé dans le conduit de transfert 17R afin de minimiser les effets de l'écoulement en retour du cylindre 2R vers le carter 14 tout en gardant au niveau de l'injection les avantages de l'injection précitée. Un système ayant le même but pourra être réalisé en jouant uniquement sur l'aérodynamique des conduits par l'interposition d'une pièce 46 profilée (Fig. 11).A valve 45 (Fig. 12) may be installed in the transfer duct 17R in order to minimize the effects of the flow back from the cylinder 2R to the casing 14 while keeping the advantages of injection at the injection level. cited above. A system having the same purpose can be achieved by playing only on the aerodynamics of the conduits by the interposition of a profiled part 46 (FIG. 11).

Cette pièce profilée possède un bord 47 qui affleure le cylindre 11 au niveau de la lumière de transfert arrière 6R dans laquelle se produit l'écoulement en retour.This profiled part has an edge 47 which is flush with the cylinder 11 at the level of the rear transfer lumen 6R in which the return flow takes place.

Ce bord 47 partage en deux parties l'orifice 6R, une partie supérieure et une partie inférieure.This edge 47 divides the orifice 6R into two parts, an upper part and a lower part.

Lorsque le piston 2R descend et tant qu'il n'a pas découvert la lumière 6R, l'écoulement se fait du carter pompe 14 via le conduit de transfert arrière 17R, fournit des gaz sous pression au conduit 15.When the piston 2R descends and as long as it has not discovered the light 6R, the flow takes place from the pump housing 14 via the rear transfer duct 17R, supplies gases under pressure to the duct 15.

Lorsque le piston 2R découvre l'orifice 6R, il en découvre d'abord la partie supérieure alors que la pression du cylindre 2R est supérieure à celle du carter 14. De ce fait se produit un écoulement en retour qu'il convient de diriger vers le conduit 15 et c'est le rôle de la surface 48 de la pièce profilée 46.When the piston 2R discovers the orifice 6R, it discovers the upper part first while the pressure of the cylinder 2R is higher than that of the casing 14. As a result, there is a return flow which should be directed towards the conduit 15 and this is the role of the surface 48 of the profiled part 46.

Lorsque le piston continue sa course descendante, l'écoulement en retour cesse et cède la place à un écoulement dans le sens carter-pompe 14 vers le cylindre 11 et dans ce cas, c'est la surface 49 qui est sollicitée.When the piston continues its downward stroke, the return flow ceases and gives way to a flow in the direction pump casing 14 towards cylinder 11 and in this case, it is surface 49 which is stressed.

L'orifice 51 sert à faciliter le passage des gaz provenant du conduit 17R.The orifice 51 serves to facilitate the passage of the gases coming from the conduit 17R.

Sur la figure 13, le piston 2R est biseauté en 52 de manière à permettre d'anticiper l'ouverture de la lumière 6R de telle sorte qu'il s'y produise un écoulement en retour.In FIG. 13, the piston 2R is bevelled at 52 so as to make it possible to anticipate the opening of the light 6R so that a return flow occurs there.

Ainsi, il est possible d'adapter facilement le dispositif selon l'invention à un moteur existant déjà et dont la hauteur des lumières de transfert n'avait pas été prévue pour des écoulements en retour.Thus, it is possible to easily adapt the device according to the invention to an already existing motor, the height of the transfer lights of which had not been provided for return flows.

On pourra adapter un système permettant de faire varier le niveau de la lumière de transfert servant de source de pression et ce en fonction d'un ou plusieurs paramètres (par exemple en fonction du régime, de la charge... ).It is possible to adapt a system making it possible to vary the level of the transfer light serving as a pressure source and this as a function of one or more parameters (for example as a function of the speed, of the load, etc.).

Claims (25)

1) A device for introducing under pressure a carbureted mixture into a first cylinder of an internal-combustion engine, of the type comprising at least one other cylinder (11) having a pump casing (14), said pump casing communicating with said other cylinder via at least one transfer port (6R), and of the type comprising a connecting pipe (15) between said pump casing (14) and the first cylinder (1), and such that a non zero angular lag exits between the cycles of said cylinders, wherein a transfer duct connects said transfer port (6R) to said connecting pipe (15), said transfer port being positioned in such a way that a back-flow is momentarily caused therein towards said pump casing.
2) A device as claimed in claim 1, wherein said angular lag is 120° and wherein the cycle of the first cylinder precedes the cycle of the other cylinder by 120°.
3) A device as claimed in claim 1, wherein said angular lag is 90° and wherein the cycle of the first cylinder precedes the cycle of the other cylinder by 90°.
4) A device as claimed in claim 2, wherein said engine comprises a number of cylinders which is a multiple of 3.
5) A device as claimed in claim 3, wherein said engine comprises a number of cylinder which is a multiple of 4.
6) A device as claimed in claim 1, wherein said pipe (15) opens into the first cylinder in the vicinity of the cylinder head of the engine.
7) A device as claimed in claim 1, wherein said pipe (15) opens into the first cylinder (1) on the lateral wall of this cylinder, substantially on the lower part of this cylinder.
8) A device as claimed in claim 1, comprising a closing member (19, 26, 29) located between said pipe (15) and first cylinder (1), substantially in the vicinity of the first cylinder.
9) A device as claimed in claim 8, wherein said closing member is a valve (19) controlled by a cam (23) or electromagnetically.
10) A device as claimed in claim 8, wherein said closing member is automatic and adapted for acting as a check valve.
11) A device as claimed in claim 8, wherein said closing member is a rotary plug (29).
12) A device as claimed in claim 1, wherein said pipe comprises a fuel introduction and metering member (20, 27, 42).
13) A device as claimed in claim 12, wherein said fuel introduction device is a low pressure injector.
14) A device as claimed in claim 13, comprising a venturi nozzle (21, 28) associated with said low pressure injector.
15) A device as claimed in claim 12, wherein said fuel introduction device is a carburetor (42) located in a duct (44) opening into said pipe (15).
16) A device as claimed in claim 15, wherein the control of said carburetor is coupled to a device controlling the amount of gas introduced into the pump casing of said first cylinder.
17) A device as claimed in claim 15, comprising at least one nonreturn member such as a check valve (43) between the carburetor (42) and said connecting pipe (15).
18) A device as claimed in claim 12, wherein said fuel introduction and metering member comprises a diaphragm pump (32) actuated by the pressure pulses of a pump casing.
19) A device as claimed in claim 18, wherein the outlet duct (34) of said diaphragm pump which connects this pump to said pipe (15) comprises a system for adjusting the flow section thereof, this system comprising a needle (37) and control means taking into account the mean pressure of a casing.
20) A device as claimed in claim 1, wherein said connecting pipe (15) has a common part which transfer duct (17R) connecting said pump casing with said port.
21) A device as claimed in claim (20), comprising an aerodynamic shaped piece at the interconnection of said pipe, of said transfer duct and of said transfer port.
22) A device as claimed in claim 20, comprising a check valve on said transfer duct, said check valve allowing no back-flow towards the pump casing.
23) A device as claimed in claim 1, wherein at least one of said pistons (2) cooperating with at least one of said cylinders is bevelled or intended over a part of the surface thereof in order to allow said back-flow to occur through at least one transfer port.
24) A device as claimed in any one of the previous claims, wherein said port through which said back-flow occurs is positioned so that said back-flow takes place only after at least one exhaust port of said other cylinder has been uncovered by said piston of said other cylinder.
25) A method for introducing under pressure the carbureted mixture into a first cylinder of an internal-combustion engine of the type comprising at least one other cylinder having a pump casing (14), said pump casing communicating with said other cylinder via at least one transfer port (6R), and of the type comprising a connecting pipe (15) between said pump casing (14) and the first cylinder (1), such as to have a non zero angular lag between the cycles of said cylinders, according to which the pressure of the gases contained in said pump casing (14) is used as a pressure source for injecting the carbureted mixture into said first cylinder (1), wherein a back-flow is caused through said transfer port (6R) in order to increase momentarily the pressure in said casing (14) or in a transfer duct connecting said port (6R) to said connecting pipe (15).
EP89401497A 1988-06-08 1989-05-31 Device and method for the introduction of a pressurized air-fuel mixture into the cylinder of an engine Expired - Lifetime EP0346188B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8807642 1988-06-08
FR8807642A FR2632684B1 (en) 1988-06-08 1988-06-08 DEVICE AND METHOD FOR PRESSURIZING CARBIDE MIXTURE INTO THE CYLINDER OF AN ENGINE

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EP0346188A1 EP0346188A1 (en) 1989-12-13
EP0346188B1 true EP0346188B1 (en) 1992-08-26

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EP (1) EP0346188B1 (en)
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FR2649158A1 (en) * 1989-06-30 1991-01-04 Inst Francais Du Petrole DEVICE FOR MONITORING THE INTRODUCTION OF THE CARBIDE MIXTURE IN PRESSURE IN AN INTERNAL COMBUSTION ENGINE AND ITS APPLICATION TO THE 2-STROKE ENGINE
EP0435730B1 (en) * 1989-12-29 1994-01-26 Institut Francais Du Petrole Two-stroke engine with controlled pneumatic injection
DE59101370D1 (en) * 1990-09-07 1994-05-19 Laimboeck Franz External ignition two-stroke reciprocating internal combustion engine with crankcase scavenging.
US6026769A (en) * 1997-05-29 2000-02-22 Walbro Corporation Mechanical direct cylinder fuel injection
US6019075A (en) * 1998-08-25 2000-02-01 Walbro Corporation Air and fuel delivery system for fuel injected engines
US6189495B1 (en) 1998-10-23 2001-02-20 Walbro Corporation Direct cylinder fuel injection
US7270110B2 (en) * 2000-04-24 2007-09-18 Frank Keoppel Four stroke internal combustion engine with inlet air compression chamber
US7640911B2 (en) * 2007-08-28 2010-01-05 Pien Pao C Two-stroke, homogeneous charge, spark-ignition engine
US8051827B1 (en) 2010-11-19 2011-11-08 Pao Chi Pien Applying the law of conservation of energy to the analysis and design of internal combustion engines
US8826868B2 (en) 2012-04-02 2014-09-09 Pao Chi Pien Reciprocating internal combustion engine
DE102018003476A1 (en) * 2018-04-24 2019-10-24 Andreas Stihl Ag & Co. Kg Internal combustion engine and method for its operation

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FR2575523B1 (en) * 1984-12-28 1989-04-07 Inst Francais Du Petrole DEVICE AND METHOD FOR INJECTING FUEL ASSISTED BY COMPRESSED AIR OR GAS IN AN ENGINE
FR2617240B1 (en) * 1987-06-26 1992-10-02 Inst Francais Du Petrole DEVICE AND METHOD FOR PRESSURIZING CARBIDE MIXTURE INTO THE CYLINDER OF AN ENGINE

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Publication number Publication date
FR2632684A1 (en) 1989-12-15
DE68902588T2 (en) 1993-04-29
US5033418A (en) 1991-07-23
FR2632684B1 (en) 1993-08-06
DE68902588D1 (en) 1992-10-01
EP0346188A1 (en) 1989-12-13

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