EP0077235A1 - Injection pump with constant injection pressure and predosage, and a system therefor - Google Patents

Injection pump with constant injection pressure and predosage, and a system therefor Download PDF

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Publication number
EP0077235A1
EP0077235A1 EP82401738A EP82401738A EP0077235A1 EP 0077235 A1 EP0077235 A1 EP 0077235A1 EP 82401738 A EP82401738 A EP 82401738A EP 82401738 A EP82401738 A EP 82401738A EP 0077235 A1 EP0077235 A1 EP 0077235A1
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EP
European Patent Office
Prior art keywords
injection
chamber
pressure
injector
piston
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
EP82401738A
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German (de)
French (fr)
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EP0077235B1 (en
Inventor
Jean-Pierre Jourde
Pedro Campo-Garraza
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Renault SAS
Regie Nationale des Usines Renault
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Renault SAS
Regie Nationale des Usines Renault
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Publication of EP0077235A1 publication Critical patent/EP0077235A1/en
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Publication of EP0077235B1 publication Critical patent/EP0077235B1/en
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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the invention relates to injection engines and more particularly to direct injection diesel engines which require high injection pressure, in particular for operating points at low speed and at low load, that is to say for small amounts injected.
  • Injection pumps in line or rotary, "do not allow sufficient pressures to be obtained in this case.
  • Conventional pump injectors give significantly higher pressures in this operating case, but they are still not sufficient
  • mechanical pump injectors present great difficulties with regard to setting the injection advance.
  • the object of the invention is to remedy the above drawbacks, that is to say to produce an injection device which makes it possible to obtain high pressures, even for the small quantities injected, and very high precision on the instant the injection begins.
  • the invention essentially consists in combining a discharge piston with mechanical cam or eccentric control which discharges the fuel into a discharge chamber, with an injection piston which is actuated only by this discharge pressure and by an opposing spring, and which compresses the fuel in an injection chamber communicating with the injector, further providing a calibrated relief valve keeping the pressure in the discharge chamber constant throughout the duration of the discharge, thus making the pressure in the pressure chamber constant and independent injection of the speed and the law of movement of the delivery piston throughout the delivery time.
  • the assembly is advantageously combined with a discharge chamber of known type ensuring rapid closure of the injection needle, with in addition a single solenoid valve ensuring both the pre-metering of the fuel in the injection chamber and the control from the instant of injection by action on this discharge chamber.
  • the body 1 of the pump injector is made of several parts, not shown in FIG. 1, which are assembled together by suitable means. It contains a pusher 2, which is pushed up and down by a cam or eccentric 3 and returned in the opposite direction by an opposing spring 4, so as to move between one. top dead center and bottom dead center, this stroke possibly being further limited by stops.
  • An appropriate light makes it possible to secure this pusher to the head of a delivery piston 5, which therefore moves in the same movement and which slides in a bore of the body 1 by driving the fuel into a delivery chamber 6 during the downward movements. , while during the upward movements of the assembly 2 and 5 the fuel is admitted into this delivery chamber 6 from the booster pressure arriving at 7 by a non-return valve 8.
  • an injection piston 9 is placed, the stroke of which is limited by an upper stop 10 and a lower stop 11 arranged in the bottom of an injection chamber 12, further containing an opposing return spring 13 urging the injection piston 9 towards its upper stop 10.
  • the injection chamber 12 communicates by a pipe 14, in which a plane valve 15 is possibly interposed, with the capacity 16 of the injector 17 provided with a conventional injection needle 18.
  • the discharge chamber 6 comprises a pressure relief valve constituted by a discharge valve 19 calibrated for a well determined high pressure.
  • the diameter of the delivery piston 5 is greater by a determined value than that of the injection piston 9 so that, whatever the engine speed and the law of movement defined by the cam or eccentric 3, the injection pressure prevails. between 12 and 16 can be kept constant and equal to the value prevailing in the discharge chamber 16 when the injection occurs.
  • an injector 17 of known type comprising a discharge chamber 20 in which slides a discharge piston 21 which pushes, by means of a pusher 22 provided with a needle spring 23, the needle 18 in the closing direction.
  • a stop 24 in the blind bottom of the discharge chamber 20 precisely limits the needle lift, while the needle spring 23 allows the needle lift 18 only if the injection pressure at 16 is sufficient , and if in addition this lifting is not prohibited by the application of high pressure in the discharge chamber 20.
  • the entire volume containing the underside of the piston 21 as well as the pusher 22, the top of the 'needle 18 and the needle spring 23 is joined to the booster pressure.
  • the same solenoid valve 26 makes it possible to ensure both the pre-metering and the control of the injection.
  • the metering occurs, during the ascent of the delivery piston 5, the injection piston 9 only going up if the solenoid valve 26 is in its first position to allow the fuel to arrive from the booster pressure to the injection 12. 12.
  • the two chambers 6 and 12 are then supplied with the booster pressure by the non-return valves 8 and 25 , but due to the presence of the opposing return spring 13, the pressure prevailing in the chamber 6 is greater than the pressure prevailing in the chamber 12, which means that the fuel cannot penetrate into the chamber 6 by the check valve.
  • the predosed quantity therefore depends exclusively only on the calibrated passage sections of conduits and on the time elapsing between the return of the solenoid valve 26 to its first position and the moment when the delivery piston 2 reaches its top dead center. There is therefore the possibility of controlling this time with precision by means of an electronic device taking into account the speed of the motor.
  • the discharge chamber 20 like the injection chamber 12, is subjected to the high pressure regulated by 19 , so that injection does not take place until the solenoid valve is energized to pass into its second position tion.
  • the pressure prevailing in the discharge chamber 20 drops and the injection is therefore carried out by 14 under a constant pressure as we saw above, and naturally during the time necessary for the flow of the predosed quantity.
  • injection piston 9 for the conduits 30 and 31 and in the body 1 for communications 32 and 33 enabling the injection piston 9 to communicate at the end of the low stroke.
  • discharge chamber 6 with the discharge chamber 20 and on the other hand the injection chamber 12 with the booster pressure, which has the effect of completely discharging the pressure of the capacity 16 of the injector and at the same time force the needle to lower to ensure rapid closure.
  • Fig. 4 corresponds to the start of the discharge and the simultaneous pressurization of the discharge chamber 6 and of the injection chamber 12, pressure regulated by the pressure limiter 19. In this phase the needle 18 cannot rise because the same pressure prevails in the discharge chamber 20 and in the capacity 16.
  • Fig. 5 corresponds to the precise instant when the injection by excitation of the valve 26 is triggered.
  • the discharge capacity 20 is discharged, allowing the needle 18 to rise, and the quantity of fuel predosed in the chamber.
  • injection 12 is injected at the constant pressure regulated by 19.
  • fig. 6 corresponds to the end of travel of the injection piston 9, which precedes the end of travel of the piston 5; position in which the injection chamber 12 and the capacity 16 of the injector, as well as. the corresponding pipes are completely discharged whereas, on the contrary, the discharge chamber 20 is partially recharged by the end of the delivery of the piston 5 into the delivery chamber 6. This therefore corresponds to the rapid closure of the needle.
  • Figs. 7 and 8 show the stroke and speed curves of the pusher and of the delivery piston 5 (measured positively downwards) in the case of an eccentric control imposing a sinusoidal law, any other law of movement also being usable.
  • fig. 9 shows the control signal of the solenoid valve as a function of the rotation cycle of the camshaft. It can be seen in particular that the rising edge 34 of the supply slot of the solenoid valve precisely determines the start of the injection, naturally with an advance to the injection, while the falling edge 35 corresponds to the predosing which ends. with the beginning of the repression. Although the solenoid valve 26 performs two functions, it therefore receives only one pulse per cycle, the two edges, rising and falling, are determined separately and electronically according to the running conditions of the engine: injection advance, speed and charge.
  • the present invention relates to a pump injector, but it is conceivable for a polycylindrical engine to group all the elements, cams or eccentrics 3, the counter springs 4 and the discharge chambers 5 for the number of cylinders considered in the same body as shown in the fig. 10 which situates the example of a four-cylinder engine.
  • the shaft 51 supporting the cams or eccentrics 3 set according to the engine cycle is driven at half speed for a four-stroke engine and at the same speed for a two-stroke engine.
  • a delivery piston 5 is obviously associated to an injection piston 9 by a high pressure line 53.
  • the delivery chamber 6 of the pump injector solution is dissociated into two chambers 6a and 6b connected by line 53.
  • the operating principle is identical to that of the pump injector, only the regulation of the high pressure is different; this difference bringing in the present version an advantage compared to several pump injectors on a polycylinder.
  • the discharge valve 19 is integrated in the injector holder which requires a very precise and delicate calibration between several pump-injector holders so that the (constant) injection pressures are identical.
  • the chambers 6a are connected via conduits 54 and non-return valves 50 to a ramp 52. At the end of which is connected the single discharge valve 19; the valve 50 being arranged in such a way that the high pressure prevailing in one of the chambers 6a can be regulated without interaction with the other chambers 6a.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

1. An injector pump for passing a premetered amount of fuel to an injector (17) having a needle (18), of the type comprising a piston (21), a discharge chamber (20), a delivery piston (5) with mechanical control by cam or eccentric in accordance with any law of movement, said piston delivering fuel in a delivery chamber (6), and an injection piston (9) which is actuated exclusively by the pressure obtaining in the delivery chamber (6) with a return spring (13) acting there against, said piston in turn delivering the fuel in an injection chamber (12) which is intended to feed the injector (17), characterised in that it comprises a pressure regulator (19) for limiting the pressure in the delivery chamber (6) to a value which is high but preregulated and independent of the operating condition of the engine and the load thereon, that the constant pressure which is thus defined in the injection chamber (12) is transmitted to the injector (17) but at the same time to the discharge chamber (20) thereof to prevent injection as long as an electrically operated valve (26) does not suppress the application of said pressure to said discharge chamber so as to have immediate application of the preregulated constant pressure at the precise moment of injection, which is determined electrically, and that it further comprises a single three-way electrically operated valve (26) to provide both for the premetering effect, by delayed communicating of the injection chamber (12) with the feed pressure (7), and for determining the time of injection by suppressing the pressure in the discharge chamber (20) of the injector (17), the common way (28) of the threeway electrically operated valve (26) being for that purpose in communication with the discharge chamber (20) while the other two ways (27 and 29) of the valve (26) are respectively connected to the injection chamber (12) and to the feed pressure (7), excitation of said valve (26) being controlled by a single rectangular pulse per cycle, of which the two edges, the rising edge (34) and the falling edge (35), are determined by an electronic device which independently controls the injection advance and the premetered amount.

Description

L'invention concerne les moteurs à injection et plus particulièrement lé-,s moteurs Diesel à injection directe qui nécessitent de haute pression d'injection, notamment pour les points de fonctionnement à bas régime et à faible charge, c'est-à-dire pour de faibles quantités injectées.The invention relates to injection engines and more particularly to direct injection diesel engines which require high injection pressure, in particular for operating points at low speed and at low load, that is to say for small amounts injected.

Les pompes d'injection, en ligne ou rotative,"ne permettent pas d'obtenir des pressions suffisantes dans ce cas. Les injecteurs pompes de type classique donnent des pressions nettement plus élevées dans ce cas de fonctionnement, mais elles ne sont toujours pas suffisantes. Par ailleurs, les injecteurs pompes mécaniques présentent de grandes difficultés en ce qui concerne le calage de l'avance à l'injection.Injection pumps, in line or rotary, "do not allow sufficient pressures to be obtained in this case. Conventional pump injectors give significantly higher pressures in this operating case, but they are still not sufficient Furthermore, mechanical pump injectors present great difficulties with regard to setting the injection advance.

Le but de l'invention est de remédier aux inconvénients précédents, c'est-à-dire de réaliser un dispositif d'injection qui permette d'obtenir de hautes pressions, même pour les faibles quantités injectées, et une très grande précision sur l'instant où commence l'injection.The object of the invention is to remedy the above drawbacks, that is to say to produce an injection device which makes it possible to obtain high pressures, even for the small quantities injected, and very high precision on the instant the injection begins.

L'invention consiste essentiellement à combiner un piston de refoulement à commande mécanique par came ou excentrique qui refoule le combustible dans une chambre de refoulement, avec un piston d'injection qui est actionné uniquement par cette pression de refoulement et par un ressort antagoniste, et qui comprime le carburant dans une chambre d'injection communiquant avec l'injecteur, en prévoyant en outre un clapet de décharge taré maintenant constante la pression dans la chambre de refoulement pendant toute la durée du refoulement, rendant ainsi la pression dans la chambre d'injection constante et indépendante du régime et de la loi de mouvement du piston de refoulement pendant toute la durée du refoulement.The invention essentially consists in combining a discharge piston with mechanical cam or eccentric control which discharges the fuel into a discharge chamber, with an injection piston which is actuated only by this discharge pressure and by an opposing spring, and which compresses the fuel in an injection chamber communicating with the injector, further providing a calibrated relief valve keeping the pressure in the discharge chamber constant throughout the duration of the discharge, thus making the pressure in the pressure chamber constant and independent injection of the speed and the law of movement of the delivery piston throughout the delivery time.

L'ensemble est combiné avantageusement avec une chambre de décharge de type connu assurant la fermeture rapide de l'aiguille d'injection, avec en outre une électrovanne unique assurant tout à la fois le prédosage du carburant dans la chambre d'injection et la commande de l'instant de l'injection par action sur cette chambre de décharge.The assembly is advantageously combined with a discharge chamber of known type ensuring rapid closure of the injection needle, with in addition a single solenoid valve ensuring both the pre-metering of the fuel in the injection chamber and the control from the instant of injection by action on this discharge chamber.

D'autres particularités de l'invention apparaîtront dans la description qui va suivre d'un mode de réalisation pris comme exemple et représenté sur le dessin annexé, sur lequel :

  • la fig. 1 est une vue schématique d'ensemble du dispositif;
  • les fig. 2 à 7 sont des schémas simplifiés illustrant les diverses phases du fonctionnement; et
  • les fïg. 7 à 9 sont des graphiques illustrant le cycle de fonctionnement; .
  • la fig. 10 est une vue schématique d'une variante applicable à un moteur polycylindrique.
Other features of the invention will appear in the following description of an embodiment taken as an example and shown in the attached drawing, in which:
  • fig. 1 is a schematic overview of the device;
  • fig. 2 to 7 are simplified diagrams illustrating the various phases of operation; and
  • the figs. 7 to 9 are graphs illustrating the operating cycle; .
  • fig. 10 is a schematic view of a variant applicable to a polycylindrical engine.

Le corps 1 de l'injecteur pompe est en plusieurs pièces, non représentées sur la figure 1, qui sont assemblées entre elles par des moyens appropriés. Il contient un poussoir 2, qui est poussé de haut en bas par une came ou excentrique 3 et rappelé dans le sens opposé par un ressort antagoniste 4, de manière à se déplacer entre un. point mort haut et un point mort bas, cette course étant éventuellement limitée en outre par des butées. Une lumière appropriée permet de solidariser ce poussoir de la tête d'un piston de refoulement 5, qui se déplace donc du même mouvement et qui coulisse dans un alésage du corps 1 en refoulant le combustible dans une chambre de refoulement 6 pendant les mouvements de descente, tandis que pendant les mouvements de remontée de l'ensemble 2 et 5 le combustible est admis dans cette chambre de refoulement 6 à partir de la pression de gavage arrivant en 7 par un clapet anti-retour 8.The body 1 of the pump injector is made of several parts, not shown in FIG. 1, which are assembled together by suitable means. It contains a pusher 2, which is pushed up and down by a cam or eccentric 3 and returned in the opposite direction by an opposing spring 4, so as to move between one. top dead center and bottom dead center, this stroke possibly being further limited by stops. An appropriate light makes it possible to secure this pusher to the head of a delivery piston 5, which therefore moves in the same movement and which slides in a bore of the body 1 by driving the fuel into a delivery chamber 6 during the downward movements. , while during the upward movements of the assembly 2 and 5 the fuel is admitted into this delivery chamber 6 from the booster pressure arriving at 7 by a non-return valve 8.

Dans un autre alésage ou de préférence dans un prolongement du même alésage se trouve disposé un piston d'injection 9 dont la course est limitée par une butée supérieure 10 et une butée inférieure 11 disposée dans le fond d'une chambre d'injection 12, contenant en outre un ressort de rappel antagoniste 13 sollicitant le piston d'injection 9 vers sa butée supérieure 10.In another bore or preferably in an extension of the same bore, an injection piston 9 is placed, the stroke of which is limited by an upper stop 10 and a lower stop 11 arranged in the bottom of an injection chamber 12, further containing an opposing return spring 13 urging the injection piston 9 towards its upper stop 10.

La chambre d'injection 12 communique par une canalisation 14, dans laquelle est interposé éventuellement un clapet plan 15, avec la capacité 16 de l'injecteur 17 muni d'une aiguille d'injection classique 18.The injection chamber 12 communicates by a pipe 14, in which a plane valve 15 is possibly interposed, with the capacity 16 of the injector 17 provided with a conventional injection needle 18.

En outre, conformément à l'invention, la chambre de refoulement 6 comporte un limiteur de pression constitué par un clapet de décharge 19 taré pour une pression élevée bien déterminée. Le diamètre du piston de refoulement 5 est supérieur d'une valeur déterminée à celui du piston d'injection 9 pour que, quels que soient le régime moteur et la loi de mouvement définie par la came ou excentrique 3, la pression d'injection régnant entre 12 et 16 puisse être maintenue constante et égale à la valeur régnant dans la chambre'de refoulement 16 lorsque se produit l'injection. Ce qui revient à dire que le volume de combustible mis en mouvement par la course descendante du piston de refoulement 5 sera toujours supérieur au volume de combustible mis en mouvement par le piston d'injection 9 afin que la pression réglée par le clapet de décharge 19 soit maintenue constante, ce qui résout déjà le premier problème posé. Il reste à assurer le prédosage de la quantité de combustible à injecter, et le déclenchement précis de l'instant de l'injection.In addition, in accordance with the invention, the discharge chamber 6 comprises a pressure relief valve constituted by a discharge valve 19 calibrated for a well determined high pressure. The diameter of the delivery piston 5 is greater by a determined value than that of the injection piston 9 so that, whatever the engine speed and the law of movement defined by the cam or eccentric 3, the injection pressure prevails. between 12 and 16 can be kept constant and equal to the value prevailing in the discharge chamber 16 when the injection occurs. This amounts to saying that the volume of fuel set in motion by the downward stroke of the delivery piston 5 will always be greater than the volume of fuel set in motion by the injection piston 9 so that the pressure adjusted by the relief valve 19 is kept constant, which already solves the first problem. It remains to ensure the predosing of the quantity of fuel to be injected, and the precise triggering of the moment of injection.

Pour cela on utilise un injecteur 17 de type connu comportant une chambre de décharge 20 dans laquelle coulisse un piston de décharge 21 qui pousse, par l'intermédiaire d'un poussoir 22 muni d'un ressort d'aiguille 23, l'aiguille 18 dans le sens de la fermeture. Une butée 24 dans le fond borgne de la chambre de décharge 20 limite avec précision la levée d'aiguille, tandis que le ressort d'aiguille 23 n'autorise la levée d'aiguille 18 que si la pression d'injection en 16 est suffisante, et si en outre cette levée n'est pas interdite par l'application d'une pression élevée dans la chambre de décharge 20. L'ensemble du volume contenant la face inférieure du piston 21 ainsi que le poussoir 22, le sommet de l'aiguille 18 et le ressort d'aiguille 23 se trouve réuni à la pression de gavage.For this, an injector 17 of known type is used comprising a discharge chamber 20 in which slides a discharge piston 21 which pushes, by means of a pusher 22 provided with a needle spring 23, the needle 18 in the closing direction. A stop 24 in the blind bottom of the discharge chamber 20 precisely limits the needle lift, while the needle spring 23 allows the needle lift 18 only if the injection pressure at 16 is sufficient , and if in addition this lifting is not prohibited by the application of high pressure in the discharge chamber 20. The entire volume containing the underside of the piston 21 as well as the pusher 22, the top of the 'needle 18 and the needle spring 23 is joined to the booster pressure.

Conformément à l'invention, cette chambre de décharge 20 est alimentée à la pression de gavage provenant par 7 grâce à un autre clapet anti-retour 25 et une électrovanne à trois voies 26 peut prendre deux positions :

  • dans la première position cette électrovanne 26 fait communiquer la chambre d'injection 12 avec la chambre de décharge 20 par des conduites appropriées 27 et 28;
  • dans la deuxième position, qui correspond par exemple à l'excitation de l'électrovanne, celle-ci fait communiquer la chambre de décharge 20 avec la pression de gavage 7 par une conduite 29 tout en obturant la canalisation 27 de la chambre d'injection.
According to the invention, this discharge chamber 20 is supplied with the booster pressure coming from 7 by means of another non-return valve 25 and a three-way solenoid valve 26 can take two positions:
  • in the first position, this solenoid valve 26 communicates the injection chamber 12 with the discharge chamber 20 by suitable pipes 27 and 28;
  • in the second position, which corresponds for example to the excitation of the solenoid valve, the latter makes the discharge chamber 20 communicate with the booster pressure 7 via a pipe 29 while closing the pipe 27 of the injection chamber .

De cette manière la même électrovanne 26 permet d'assurer à la fois le prédosage et la commande de l'injection. Le dosage se produit, pendant la remontée du piston de refoulement 5, le piston d'injection 9 ne remontant que si l'électrovanne 26 est dans sa première position pour permettre au carburant d'arriver de la pression de gavage à la chambre d'injection 12. 12. Dans ce cas, c'est-à-dire pendant que l'électrovanne est dans sa première position, les deux chambres 6 et 12 sont alors alimentées à la pression de gavage par les clapets anti-retour 8 et 25, mais du fait de la présence du ressort de rappel antagoniste 13 la pression qui règne dans la chambre 6 est supérieure à la pression qui règne dans la chambre 12 ce qui fait que le combustible ne peut pénétrer dans la chambre 6 par le clapet anti-retour 8 lorsque le piston de refoulement 5 sous l'effet du ressort antagoniste 4 remonte, la came ou excentrique 3 se déplaçant de son point mort bas à son point mort haut. La quantité prédosée ne dépend donc exclusivement que des sections de passage calibrées de conduits et du temps s'écoulant entre le retour de l'électrovanne 26 à sa première position et l'instant où le piston de refoulement 2 atteint son point mort haut. On a donc la possibilité de commander ce temps avec précision grâce à un dispositif électronique en tenant compte de la vitesse du moteur.In this way the same solenoid valve 26 makes it possible to ensure both the pre-metering and the control of the injection. The metering occurs, during the ascent of the delivery piston 5, the injection piston 9 only going up if the solenoid valve 26 is in its first position to allow the fuel to arrive from the booster pressure to the injection 12. 12. In this case, that is to say while the solenoid valve is in its first position, the two chambers 6 and 12 are then supplied with the booster pressure by the non-return valves 8 and 25 , but due to the presence of the opposing return spring 13, the pressure prevailing in the chamber 6 is greater than the pressure prevailing in the chamber 12, which means that the fuel cannot penetrate into the chamber 6 by the check valve. return 8 when the delivery piston 5 under the effect of the opposing spring 4 rises, the cam or eccentric 3 moving from its bottom dead center to its top dead center. The predosed quantity therefore depends exclusively only on the calibrated passage sections of conduits and on the time elapsing between the return of the solenoid valve 26 to its first position and the moment when the delivery piston 2 reaches its top dead center. There is therefore the possibility of controlling this time with precision by means of an electronic device taking into account the speed of the motor.

Au contraire, pendant la phase de descente du piston de refoulement 5, si l'électrovanne 26 est dans sa première position, la chambre de décharge 20, tout comme la chambre d'injection 12, se trouve soumise à la haute pression régulée par 19, de sorte que l'injection ne se produit pas tant que l'électrovanne n'est pas excitée pour passer dans sa deuxième position. A ce moment là, la pression régnant dans la chambre de décharge 20 chute et l'injection se fait par conséquent par 14 sous une pression constante comme on l'a vu plus haut, et naturellement pendant le temps nécessaire pour l'écoulement de la quantité prédosée.On the contrary, during the descent phase of the delivery piston 5, if the solenoid valve 26 is in its first position, the discharge chamber 20, like the injection chamber 12, is subjected to the high pressure regulated by 19 , so that injection does not take place until the solenoid valve is energized to pass into its second position tion. At this time, the pressure prevailing in the discharge chamber 20 drops and the injection is therefore carried out by 14 under a constant pressure as we saw above, and naturally during the time necessary for the flow of the predosed quantity.

A titre de perfectionnement, il est prévu dans le piston d'injection 9 des conduits 30 et 31 et dans le corps 1 des communications 32 et 33 permettant en fin de course basse du piston d'injection 9 de faire communiquer d'une part la chambre de refoulement 6 avec la chambre de décharge 20, et d'autre part la chambre d'injection 12 avec la pression de gavage, ce qui a pour effet de décharger complétement la pression de la capacité 16 de l'injecteur et en même temps de forcer l'aiguille à s'abaisser pour assurer sa fermeture rapide.By way of improvement, provision is made in the injection piston 9 for the conduits 30 and 31 and in the body 1 for communications 32 and 33 enabling the injection piston 9 to communicate at the end of the low stroke. discharge chamber 6 with the discharge chamber 20, and on the other hand the injection chamber 12 with the booster pressure, which has the effect of completely discharging the pressure of the capacity 16 of the injector and at the same time force the needle to lower to ensure rapid closure.

On peut reprendre l'ensemble du fonctionnement et des divers perfectionnements sur les fig. 2 à 7 où l'on voit sur la fig. 2 le début de remontée du poussoir avec la vanne 26 sous tension ce qui permet le remplissage de la chambre de refoulement 6, tandis que la chambre d'injection 12 ne se remplit pas encore, le piston 9 restant immobile.We can resume the entire operation and various improvements in Figs. 2 to 7 where we see in fig. 2 the start of ascent of the pusher with the valve 26 energized which allows the filling of the discharge chamber 6, while the injection chamber 12 is not yet filling, the piston 9 remaining stationary.

Sur la fig. 3, on voit le début du dosage correspondant à la coupure de l'excitation de l'électrovanne 26 qui permet au piston 9 de remonter sous l'effet du ressort et de procéder au prédosage.In fig. 3, we can see the start of the dosage corresponding to the interruption of the excitation of the solenoid valve 26 which allows the piston 9 to rise under the effect of the spring and to carry out the pre-metering.

La fig. 4 correspond au début du refoulement et de la mise en pression simultanée de la chambre de refoulement 6 et de la chambre d'injection 12, pression régulée par le limiteur de pression 19. Dans cette phase l'aiguille 18 ne peut pas se lever car la même pression règne dans la chambre de décharge 20 et dans la capacité 16.Fig. 4 corresponds to the start of the discharge and the simultaneous pressurization of the discharge chamber 6 and of the injection chamber 12, pressure regulated by the pressure limiter 19. In this phase the needle 18 cannot rise because the same pressure prevails in the discharge chamber 20 and in the capacity 16.

La fig. 5 correspond à l'instant précis où est déclenchée l'injection par excitation de la vanne 26. La capacité de déçharge 20 se trouve déchargée, permettant à l'aiguille 18 de se lever, et la quantité de carburant prédosée dans la chambre d'injection 12 se trouve injectée à la pression constante régulée par 19.Fig. 5 corresponds to the precise instant when the injection by excitation of the valve 26 is triggered. The discharge capacity 20 is discharged, allowing the needle 18 to rise, and the quantity of fuel predosed in the chamber. injection 12 is injected at the constant pressure regulated by 19.

Enfin, la fig. 6 correspond à la fin de course du piston d'injection 9, qui précède la fin de course du piston 5; position dans laquelle la chambre d'injection 12 et la capacité 16 de l'injecteur, ainsi que. les canalisations correspondantes se trouvent complétement déchargées alors qu'au contraire la chambre de décharge 20 se trouve partiellement rechargée par la fin du refoulement du piston 5 dans la chambre de refoulement 6. Cela correspond donc à le refer- meture rapide de l'aiguille.Finally, fig. 6 corresponds to the end of travel of the injection piston 9, which precedes the end of travel of the piston 5; position in which the injection chamber 12 and the capacity 16 of the injector, as well as. the corresponding pipes are completely discharged whereas, on the contrary, the discharge chamber 20 is partially recharged by the end of the delivery of the piston 5 into the delivery chamber 6. This therefore corresponds to the rapid closure of the needle.

Les fig. 7 et 8 représentent les courbes de course et de vitesse du poussoir et du piston de refoulement 5 (mesurées positivement vers le bas) dans le cas d'une commande par excentrique imposant une loi sinusoïdale, tout autre loi de mouvement étant également utilisable. Enfin, la fig. 9 représente en fonction du cycle de rotation de l'arbre à cames le signal de commande de l'électrovanne. On voit en particulier que le front montant 34-du créneau d'alimentation de l'électrovanne détermine avec précision le début de l'injection, avec naturellement une avance à l'injection, tandis que le front descendant 35 correspond au prédosage qui se termine avec le début du refoulement. Bien que l'électrovanne 26 remplisse deux fonctions, elle ne reçoit donc qu'une impulsion par cycle dont les deux fronts, montant et descendant, sont déterminés séparément et électroniquement en fonction des conditions de marche du moteur : avance à l'injection, vitesse et charge.Figs. 7 and 8 show the stroke and speed curves of the pusher and of the delivery piston 5 (measured positively downwards) in the case of an eccentric control imposing a sinusoidal law, any other law of movement also being usable. Finally, fig. 9 shows the control signal of the solenoid valve as a function of the rotation cycle of the camshaft. It can be seen in particular that the rising edge 34 of the supply slot of the solenoid valve precisely determines the start of the injection, naturally with an advance to the injection, while the falling edge 35 corresponds to the predosing which ends. with the beginning of the repression. Although the solenoid valve 26 performs two functions, it therefore receives only one pulse per cycle, the two edges, rising and falling, are determined separately and electronically according to the running conditions of the engine: injection advance, speed and charge.

La présente invention concerne un injecteur pompe mais on peut concevoir pour un moteur polycylindrique de regrouper tous les éléments, cames ou excentriques 3, les ressorts antagonistes 4 et les chambres de refoulement 5 pour le nombre de cylindres considérés dans un même corps comme représenté sur la fig. 10 qui situe l'exemple d'un moteur à quatre cylindres.The present invention relates to a pump injector, but it is conceivable for a polycylindrical engine to group all the elements, cams or eccentrics 3, the counter springs 4 and the discharge chambers 5 for the number of cylinders considered in the same body as shown in the fig. 10 which situates the example of a four-cylinder engine.

L'arbre 51 supportant les cames ou excentriques 3 calés selon le cycle du moteur est entraîné à la vitesse moitié pour un moteur à quatre temps et à même vitesse pour un moteur deux temps. Un piston de refoulement 5 est bien évidemment associé à un piston d'injection 9 par une ligne haute pression 53. La chambre de refoulement 6 de la solution injecteur pompe est dissociée-en deux chambres 6a et 6b reliées par la ligne 53.The shaft 51 supporting the cams or eccentrics 3 set according to the engine cycle is driven at half speed for a four-stroke engine and at the same speed for a two-stroke engine. A delivery piston 5 is obviously associated to an injection piston 9 by a high pressure line 53. The delivery chamber 6 of the pump injector solution is dissociated into two chambers 6a and 6b connected by line 53.

Le principe de fonctionnement est identique à celui de l'injecteur-pompe, seule la régulation de la haute pression est différente; cette différence apportant dans la présente version un avantage comparativement à plusieurs injecteurs-pompe sur un polycylindre. En effet, dans le cas d'injecteur- pompe, le clapet de décharge 19 est intégré dans le porte- injecteur ce qui nécessite un étalonnage très précis et délicat entre plusieurs porte-injecteurs-pompe pour que les pressions (constantes) d'injection soient identiques. Dans la présente version, il n'y a qu'un seul clapet de décharge 19 pour plusieurs porte-injecteurs. Les chambres 6a sont reliées par l'intermédiaire de conduits 54 et de clapets anti-retour 50 à une rampe 52.à l'extrémité de laquelle est relié le clapet unique de décharge 19; le clapet 50 étant disposé de telle façon que la haute-pression régnant dans une des chambres 6a puisse être régulée sans interaction avec les autres chambres 6a.The operating principle is identical to that of the pump injector, only the regulation of the high pressure is different; this difference bringing in the present version an advantage compared to several pump injectors on a polycylinder. Indeed, in the case of pump injector, the discharge valve 19 is integrated in the injector holder which requires a very precise and delicate calibration between several pump-injector holders so that the (constant) injection pressures are identical. In the present version, there is only one relief valve 19 for several injector holders. The chambers 6a are connected via conduits 54 and non-return valves 50 to a ramp 52. At the end of which is connected the single discharge valve 19; the valve 50 being arranged in such a way that the high pressure prevailing in one of the chambers 6a can be regulated without interaction with the other chambers 6a.

Claims (6)

1. Injecteur pompe envoyant une quantité prédosée de carburant à un injecteur (17) à aiguille (18) du type comportant un piston (21) et une chambre (20) de décharge, caractérisé par le fait qu'il comporte un piston de refoulement (5) à commande mécanique par came ou excentrique selon une loi de mouvement quelconque, ce piston refoulant du carburant dans une chambre de refoulement (6), et un piston d'injection (9) actionné exclusivement par la pression régnant dans la chambre de refoulement (6) avec un ressort de rappel antagoniste (13), ce piston refoulant à son tour le carburant dans une chambre d'injection (12) destinée à alimenter l'injecteur (17), avec en outre un régulateur de pression (19) limitant la pression dans la chambre de refoulement (6) à une valeur élevée mais préréglée et indépendante du régime du moteur aussi bien que de la charge de celui-ci.1. Pump injector sending a predosed quantity of fuel to a needle injector (17) of the type comprising a piston (21) and a discharge chamber (20), characterized in that it comprises a delivery piston (5) mechanically controlled by cam or eccentric according to any law of movement, this piston delivering fuel into a delivery chamber (6), and an injection piston (9) actuated exclusively by the pressure prevailing in the delivery (6) with an opposing return spring (13), this piston in turn driving the fuel into an injection chamber (12) intended to supply the injector (17), with in addition a pressure regulator (19 ) limiting the pressure in the discharge chamber (6) to a high value but preset and independent of the engine speed as well as the load thereof. 2. Injecteur pompe selon la revendication 1, caractérisé par le fait que la pression constante ainsi déterminée dans la chambre d'injecteur (12) est transmise à l'injecteur (17) mais en même temps à sa chambre de décharge (20) pour empêcher l'injection tant qu'une électrovanne (26) ne supprime pas l'application de cette pression à cette chambre de décharge, de manière à avoir une application immédiate de la pression constante préréglée au moment précis de l'injection déterminé électriquement.2. Pump injector according to claim 1, characterized in that the constant pressure thus determined in the injector chamber (12) is transmitted to the injector (17) but at the same time to its discharge chamber (20) for prevent injection as long as a solenoid valve (26) does not suppress the application of this pressure to this discharge chamber, so as to have an immediate application of the constant pressure preset at the precise moment of injection determined electrically. 3. Injecteur pour pompe selon la revendication 2, carac-, térisé par le fait qu'il comporte une électrovanne unique à trois voies (26) pour assurer à la fois le prédosage, par mise en communication retardée de la chambre d'injection (12) avec la pression de gavage (7), et la détermination de l'instant d'injection par suppression de la pression dans la chambre de décharge (20) de l'injecteur (17), la voie commune (28) de l'électrovanne à trois voies (26) étant pour cela en communication avec la chambre de décharge (20), tandis que les deux autres voies (27) et (29) sont réunies respectivement à la chambre d'injection (12) et à la pression de gavage (7), l'excitation de cette électrovanne (26) étant commandée par une seule impulsion en créneau par cycle dont les deux fronts, montant (34) et descendant (35), sont déterminés par un dispositif électronique qui règle indépendamment l'avance à l'injection et la quantité prédospe.3. Pump injector according to claim 2, charac- terized by the fact that it comprises a single three-way solenoid valve (26) to ensure both the pre-metering, by delayed communication of the injection chamber ( 12) with the booster pressure (7), and the determination of the injection instant by removing the pressure in the discharge chamber (20) of the injector (17), the common path (28) of the 'three-way solenoid valve (26) being for this in communication with the discharge chamber (20), while the other two paths (27) and (29) are connected respectively to the injection chamber (12) and to the booster pressure (7), the excitation of this solenoid valve (26) being controlled by a single pulse in niche per cycle whose two edges, rising (34) and falling (35), are determined by an electronic device which independently regulates the injection advance and the predos quantity p e. 4. Injecteur pompe selon l'une des revendications précédentes, caractérisé par le fait qu'il comporte des conduits (31 et 33) dans le piston d'injection (9) et dans le corps (1), positionnés de manière à assurer, juste avant la fin de course de ce piston, la mise en communication de la chambre d'injection (12) avec la pression de gavage (7) afin de décharger la capacité (16) de l'injecteur pour une fermeture rapide de l'aiguille (18).4. pump injector according to one of the preceding claims, characterized in that it comprises conduits (31 and 33) in the injection piston (9) and in the body (1), positioned so as to ensure, just before the end of the stroke of this piston, the communication of the injection chamber (12) with the booster pressure (7) in order to discharge the capacity (16) of the injector for rapid closure of the needle (18). 5. Injecteur pompe selon la revendication 4, caractérisé par le fait qu'il comporte en outre d'autres conduits (30 et 32) dans le piston injecteur (9) et dans le corps (1) pour faire communiquer, la chambre de refoulement (6) avec la chambre de décharge (20) juste avant la fin de course du piston d'injection (9) qui précède la fin de course du piston de refoulement (5), de manière à recharger la chambre de décharge (20) afin d'accélérer la fermeture de l'aiguille (18).5. Injector pump according to claim 4, characterized in that it further comprises other conduits (30 and 32) in the injector piston (9) and in the body (1) to communicate, the delivery chamber (6) with the discharge chamber (20) just before the end of travel of the injection piston (9) which precedes the end of travel of the delivery piston (5), so as to reload the discharge chamber (20) to accelerate the closing of the needle (18). 6. Injecteur pompe selon une des revendications précédentes, mais de type multiple pour alimenter un moteur à plusieurs cylindres, caractérisé par le fait que chacune des chambres de refoulement correspondant à chaque cylindre est scindée en deux parties (6a, 6b) raccordées par une canalisation (53), les premières (6a) de ces parties et organes (1 à 5) correspondants étant réunies en un ensemble unique à arbre à cames commun (51) à distance des injecteurs (17), avec un régulateur de pression (19) unique raccordé aux diverses chambres (6a) par des clapets anti-retour (50).6. Injector pump according to one of the preceding claims, but of multiple type for supplying an engine with several cylinders, characterized in that each of the delivery chambers corresponding to each cylinder is split into two parts (6a, 6b) connected by a pipe (53), the first (6a) of these corresponding parts and members (1 to 5) being combined in a single assembly with a common camshaft (51) remote from the injectors (17), with a pressure regulator (19) single connected to the various chambers (6a) by non-return valves (50).
EP82401738A 1981-10-01 1982-09-27 Injection pump with constant injection pressure and predosage, and a system therefor Expired EP0077235B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8118558 1981-10-01
FR8118558A FR2514075A1 (en) 1981-10-01 1981-10-01 PUMP INJECTOR WITH CONSTANT INJECTION PRESSURE AND PREDOSAGE AND DERIVATIVE SYSTEM

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EP0077235A1 true EP0077235A1 (en) 1983-04-20
EP0077235B1 EP0077235B1 (en) 1985-08-14

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EP82401738A Expired EP0077235B1 (en) 1981-10-01 1982-09-27 Injection pump with constant injection pressure and predosage, and a system therefor

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EP (1) EP0077235B1 (en)
JP (1) JPS5874869A (en)
DE (1) DE3265437D1 (en)
FR (1) FR2514075A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0240353A2 (en) * 1986-04-04 1987-10-07 Nippondenso Co., Ltd. A fuel injection control device
EP0629776A1 (en) * 1993-06-03 1994-12-21 Cummins Engine Company, Inc. A fuel injector for an internal combustion engine
EP0724688A1 (en) * 1993-10-06 1996-08-07 Bkm, Inc. Two-cycle utility internal combustion engine
EP0962649A1 (en) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Fuel injection apparatus
WO1999063217A1 (en) * 1998-06-04 1999-12-09 Wolfgang Heimberg Pumping device

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558789A1 (en) * 1975-12-24 1977-07-14 Bosch Gmbh Robert HIGH PRESSURE FUEL INJECTION DEVICE FOR DIESEL ENGINES
GB2030222A (en) * 1978-09-13 1980-04-02 Bendix Corp Fuel injector for an internal combustion engine for producing fuel injection pulses which have a time-variable flow rate

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1103685B (en) * 1956-12-13 1961-03-30 Pierre Etienne Bessiere Self-regulating piston pump for fuel injection in internal combustion engines
JPS6014910B2 (en) * 1979-12-28 1985-04-16 株式会社デンソー fuel injector

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558789A1 (en) * 1975-12-24 1977-07-14 Bosch Gmbh Robert HIGH PRESSURE FUEL INJECTION DEVICE FOR DIESEL ENGINES
GB2030222A (en) * 1978-09-13 1980-04-02 Bendix Corp Fuel injector for an internal combustion engine for producing fuel injection pulses which have a time-variable flow rate

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0240353A2 (en) * 1986-04-04 1987-10-07 Nippondenso Co., Ltd. A fuel injection control device
EP0240353A3 (en) * 1986-04-04 1989-10-11 Nippondenso Co., Ltd. A fuel injection control device
EP0629776A1 (en) * 1993-06-03 1994-12-21 Cummins Engine Company, Inc. A fuel injector for an internal combustion engine
EP0724688A1 (en) * 1993-10-06 1996-08-07 Bkm, Inc. Two-cycle utility internal combustion engine
EP0724688A4 (en) * 1993-10-06 1997-07-09 Bkm Inc Two-cycle utility internal combustion engine
EP0962649A1 (en) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Fuel injection apparatus
WO1999063217A1 (en) * 1998-06-04 1999-12-09 Wolfgang Heimberg Pumping device

Also Published As

Publication number Publication date
JPH0454064B2 (en) 1992-08-28
FR2514075B1 (en) 1983-12-23
JPS5874869A (en) 1983-05-06
EP0077235B1 (en) 1985-08-14
DE3265437D1 (en) 1985-09-19
FR2514075A1 (en) 1983-04-08

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