EP0596054B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

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Publication number
EP0596054B1
EP0596054B1 EP93907795A EP93907795A EP0596054B1 EP 0596054 B1 EP0596054 B1 EP 0596054B1 EP 93907795 A EP93907795 A EP 93907795A EP 93907795 A EP93907795 A EP 93907795A EP 0596054 B1 EP0596054 B1 EP 0596054B1
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EP
European Patent Office
Prior art keywords
pressure
valve
fuel
electrically controlled
pump
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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.)
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EP93907795A
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German (de)
French (fr)
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EP0596054A1 (en
Inventor
Bernhard Bonse
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/16—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor characterised by the distributor being fed from a constant pressure source, e.g. accumulator or constant pressure positive displacement pumps
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention is based on a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection device is already known from US Pat. No. 4,964,389 or the corresponding DE-A-38 43 467.
  • a predetermined fuel injection quantity is metered into an intermediate store via the electrically controlled valve in the fuel line discharging from the store, the output of which can be connected to the distributor opening via a second electrically controlled valve.
  • the amount of fuel supplied to the intermediate store via the first electrically controlled valve which is below the injection pressure provided by the high-pressure store, is measured by the stroke of a storage piston delimiting the intermediate store and the opening duration of the first electrically controlled valve is correspondingly determined by a control device.
  • the first electrically controlled valve thus controls the amount of fuel to be injected.
  • the second electrically controlled valve is opened at the desired injection point in time and the fuel stored by the intermediate store is conveyed to the respective injection
  • the second electrically controlled valve determines the injection timing.
  • This device is quite complex in that, in addition to two electrically controlled valves, a high-pressure intermediate store is also required.
  • a fuel injection pump of the generic type is also known from EP-A1-0 381 954.
  • the electrically controlled valve provided there is arranged in a connecting line leading from the high-pressure accumulator to the distributor, upstream of the latter and, through its open position, controls the point in time at which injection begins and the duration of its open state, the fuel injection quantity.
  • the electrically controlled valve operates as a 2/2 valve with regard to its intended function and, on the other hand, because of its design as a 3/2 valve, it relieves the pressure on the fuel-carrying area between the electrically controlled valve, distributor and a respective injection line up to the pressure valve upstream of the injection valve.
  • the electrically controlled valve according to this prior art must be a very fast-acting valve in order to be able to control the required injection times and short injection durations even with small fuel injection quantities. If an increased accuracy with regard to the injection point is to be achieved, this requires a high technical outlay for such a valve.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that it is constructed very simply with as few components as possible and exact, fast control times of the injection process can be achieved by means of the two electrically controlled valves.
  • FIG. 1 shows a first exemplary embodiment with a radial piston distributor pump as a pressure generator and as a device for controlling a plurality of fuel injection valves which are supplied with fuel from a high-pressure accumulator
  • FIG. 2 shows a second exemplary embodiment with a modified embodiment of a pressure control device, the high-pressure accumulator of the first exemplary embodiment.
  • FIG. 1 shows a partial section through parts of a high-pressure pump of the radial piston distributor injection pump type.
  • a distributor piston 2 is driven in rotation in a bore 3 by a drive (not shown further).
  • pump cylinders 6 lying radially to its axis of rotation 5, in which pump pistons 7 can be moved back and forth enclose a pump work space 8 between them.
  • the pump pistons On its outer end face, the pump pistons rest on roller shoes 10 with rollers 11, which run on a cam track 12 of a cam ring 13 when the distributor piston rotates.
  • the cam ring is mounted in the housing 14 of the high-pressure fuel pump.
  • the distributor 2 has a first annular groove 15 and a second annular groove 16 at an axial distance therefrom.
  • a fuel supply line 17 opens via a filling valve 18 in the form of a check valve, the fuel supply line being supplied with fuel by a fuel feed pump 19 driven synchronously with the distributor 2, which fuel is kept at a specific delivery pressure by means of a pressure control valve 20, which Relieved fuel supply line 17 to the suction side of the feed pump 19.
  • a pressure line 22 also leads from the second annular groove 16, in which a delivery valve 23 is arranged, which is designed as a check valve opening away from the annular groove 16.
  • the pressure line 22 opens into a high-pressure accumulator 24 via this delivery valve 23.
  • the second annular groove is finally in constant communication with the pump work chamber 8 through a pressure line 26.
  • the high-pressure accumulator is connected to the first annular groove 15 via a fuel line 28, in which a first electrically controlled valve 29, here a solenoid valve, is arranged.
  • This annular groove is permanently connected to a distributor opening of the distributor 2 in the form of a distributor groove 31, which is incorporated into the lateral surface of the distributor and extends parallel to the axis of rotation of the distributor and which is connected in succession to injection lines 23 leading away from the bore 3 when the distributor rotates .
  • These injection lines 33 lead via a pressure valve 34, which as a conventional pressure valve or as Constant pressure or constant space valve can be connected to a fuel injector on the internal combustion engine.
  • a relief line 35 branches off from the first annular groove 15, in which a second electrically controlled valve 36, here again a solenoid valve, is arranged. Both solenoid valves 29 and 36 are controlled by an electrical control device 37.
  • the high-pressure accumulator 24 also has a relief line 38, in which either a pressure-maintaining valve 39 which controls a specific pressure in the high-pressure accumulator 24 and which operates mechanically is arranged, or an electrically controlled valve 40, here again a solenoid valve which is controlled by the electrical control device 37 in accordance with signals from a pressure transmitter 41, which detects the pressure in the high-pressure accumulator 24 and emits corresponding signals to the electrical control device.
  • a pressure-maintaining valve 39 which controls a specific pressure in the high-pressure accumulator 24 and which operates mechanically is arranged
  • an electrically controlled valve 40 here again a solenoid valve which is controlled by the electrical control device 37 in accordance with signals from a pressure transmitter 41, which detects the pressure in the high-pressure accumulator 24 and emits corresponding signals to the electrical control device.
  • the fuel injection device described works as follows: If the distributor piston is driven in rotation, which is usually done via the crankshaft of the associated internal combustion engine in synchronism with its speed, the pump pistons are moved back and forth following the cams of the cam track 12 via the roller shoes 10. In the case of an outward movement corresponding to a suction stroke, the pump pistons 7 then suck in fuel via the filling valve 18. During the pressure stroke then caused by the cams of the cam track, the pump pistons 7 displace fuel under high pressure via the delivery valve 23 into the high-pressure accumulator until a certain predetermined pressure is achieved there. This pressure can either be set by the pressure holding valve 39 or via the pressure transmitter 41 in connection with the electrical one Control device 37 and the solenoid valve 40. As long as the predetermined pressure in the accumulator 24 has not been reached, there is no outflow via the relief line 38. When the set pressure is exceeded, the pressure-maintaining valve or the solenoid valve opens in an analog or clocked manner.
  • fuel can be drawn from the internal combustion engine for high-pressure injection. This takes place via the first electrically controlled valve 29, which is opened under the control of the electrical control device at a desired start of injection, the second electrically controlled valve 36 being closed.
  • the fuel then flowing out of the high-pressure accumulator 24 reaches the corresponding fuel injection nozzle via the distributor groove 31 and one of the injection lines 33 and there for injection.
  • the amount of fuel to be injected there is controlled by the second electrically controlled valve 36, in that it is opened when the fuel injection quantity is reached, so that the first annular groove 15 is relieved and the pressure in the injection line 33 or on the fuel injection valve drops below the injection pressure.
  • the first electrically controlled valve 29 is preferably closed. This closing of the first electrically controlled valve can also take place briefly after the opening of the second electrically controlled valve 36. In the former case, there is a minimum loss of fuel brought to high pressure from the accumulator 24. With the help of the pressure valve 34, a constant pressure in the injection line between the injection valve and pressure valve is usually maintained in the breaks between the high pressure injection processes, if this is designed as a constant pressure valve is. But there is also the possibility of an arrangement of Control grooves on the distributor piston to relieve the individual injection lines after the injection to a predetermined pressure level.
  • the proposed system also has advantages in that the design of the cams of the cam track no longer has to be matched to the special conditions during the time of the injection.
  • the cam drives only serve to provide the high injection pressure.
  • the conveying strokes can Pump pistons are in the periods in which the fuel injection valves from the high-pressure accumulator 24 are also supplied with high-pressure fuel for injection. The memory is thus kept free of any pressure pulsations that may occur during the injection processes.
  • the storage pressure can be controlled via an outflow control or else via the control of a delivery rate of the high-pressure pump, which would have meant the advantage of a lower drive power but a somewhat greater effort.
  • the design of the delivery capacity of the high-pressure pump advantageously offers the possibility of generating a high injection pressure in the accumulator 24 even at a low speed, in which case the accumulator is relieved accordingly at a higher speed, with the possible adjustment of the accumulator pressure to the speed.
  • the fuel injection device described is characterized above all by simple components with universal control options for the start of injection and the amount of injection.
  • a pump of the axial piston pump type can also be used according to FIG.
  • One of these has a rotatingly driven front cam disk 44, which runs on fixedly mounted rollers, only one of which is shown.
  • a pump and distributor piston 46 Connected to the end cam disk is a pump and distributor piston 46, which is rotatably carried along by the end cam disk 44 and is axially moved back and forth on the rollers 45 by the cam track 47 of the end cam disk in a pump cylinder 48 into which the pump - And distributor piston 46 includes a pump work chamber 49 at the end.
  • the end cam disk is held in contact with the rollers 45 by a strong return spring 50 so that the pump piston 46 safely performs its suction stroke.
  • the pump piston is moved during a complete revolution into a plurality of reciprocating suction and delivery strokes connected to the pump working chamber 49. During its suction strokes, it sucks in fuel via a suction groove 51 connected to the pump working space 49 in its outer surface and a fuel supply or suction line 52 opening into the pump cylinder 48.
  • the control edges delimiting the suction groove close the mouth of the suction line 52 and the fuel located in the pump work chamber 49 is compressed and via an axial blind bore 54, which starts from the end face of the pump piston 46 and a transverse bore 55 in an annular groove 56 in the surface of the guided in the pump cylinder 48 area of the pump piston.
  • This annular groove 56 is in constant communication with a pressure line 57, which corresponds to the pressure line 22 and opens into the high-pressure accumulator 24 and contains a delivery valve 23.
  • the annular groove 56 is in constant communication with a relief line 58, in which a pressure-maintaining valve 59, which opens to the relief side, is arranged.
  • a first annular groove 60 is provided in the lateral surface of the pump piston 46, corresponding to the first annular groove 15 or the second annular groove 16 from the exemplary embodiment in FIG. 1.
  • This first annular groove 16 is in turn via a fuel line 28 connected to the high-pressure accumulator 24 and contains the first electrically controlled valve 29.
  • the relief line 35 also branches off from the first annular groove 60 with the second electrically controlled valve 36.
  • the distributor groove 31 is also connected to the first annular groove 60, via which in the Course of the rotation of the pump and distributor pistons 46 each during the delivery stroke, one of the injection lines 31 is actuated, which likewise contains a pressure valve 34 and leads to the respective injection valve on the fuel injection pump.
  • this exemplary embodiment with respect to the first annular groove 60 has the same structure as the exemplary embodiment according to FIG. 1, the width of the annular groove in the axial direction of the pump piston 46 and the length of the distributor groove having to take into account the pumping stroke movements of the pump piston 46.
  • the solenoid valves 29 and 36 are actuated in the same way as in the exemplary embodiment according to FIG. 1, and the intended pump strokes of the pump piston can be designed analogously to the instructions for FIG.
  • suction control with the aid of the suction groove 15 is provided for this.
  • suction grooves corresponding to the number of suction strokes of the pump piston per revolution can be provided with a single suction line 52 or more, or only one suction groove is provided and the suction lines are corresponding to the number of suction strokes of the pump piston on the circumference of the pump cylinder 48 distributed.
  • control of the suction stroke with the aid of a control edge offers advantages over a filling valve designed as a check valve. It can of course also be used analogously in the exemplary embodiment according to FIG. 1.
  • the pressure-maintaining valve 59 designed here as a check valve can of course also be a solenoid valve controlled by a pressure sensor, analogous to the exemplary embodiment according to FIG.
  • the pressure generation was carried out with the aid of pumps corresponding to the design of conventional distributor pump types, these pumps also taking on the distributor function in addition to the pressure generation for the high-pressure accumulator, it is also possible to provide a high-pressure pump and a separate distributor in a known manner.
  • the high pressure generation is in principle independent of the distributor function.
  • a very compact structural unit results if a pump of the distributor pump type is used as a pressure generator.

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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)

Abstract

The proposal is for a fuel injection device for internal combustion engines in which a high-pressure reservoir (24) is supplied via a high-pressure pump with fuel under injection pressure, from which the fuel to be injected is taken off at the appropriate time and in the appropriate quantity via two sequentially electrically controlled valves (29, 36) and taken to one of several injection points via a distributor. The injection points are controlled in succession by a distribution aperture (31) of the distributor. With fuel kept at a given pressure in the high-pressure reservoir (24), a highly universally controllable fuel injection device is produced in a simple and cheap manner.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Eine solche Kraftstoffeinspritzeinrichtung ist bereits durch die US-PS 4 964 389 bzw. die entsprechenden DE-A-38 43 467 bekannt. Dort wird über das elektrisch gesteuerte Ventil in der vom Speicher abführenden Kraftstoffleitung eine vorgegebene Kraftstoffeinspritzmenge in einen Zwischenspeicher zugemessen, dessen Ausgang über ein zweites elektrisch gesteuertes Ventil mit der Verteileröffnung verbindbar ist. Die über das erste elektrisch gesteuerte Ventil dem Zwischenspeicher zugeführte Kraftstoffmenge, die unter den vom Hochdruckspeicher zur Verfügung gestellten Einspritzdruck steht, wird durch den Hub eines den Zwischenspeicher begrenzenden Speicherkolbens gemessen und entsprechend die Öffnungsdauer des ersten elektrisch gesteuerten Ventils durch eine Steuereinrichtung bestimmt. Das erste elektrisch gesteuerte Ventil steuert somit die zur Einspritzung kommende Kraftstoffmenge. Das zweite elektrisch gesteuerte Ventil wird zum gewünschten Einspritzzeitpunkt geöffnet und dabei der vom Zwischenspeicher gespeicherte Kraftstoff zur jeweiligen Einspritzdüse gefördert.The invention is based on a fuel injection device for internal combustion engines according to the preamble of claim 1. Such a fuel injection device is already known from US Pat. No. 4,964,389 or the corresponding DE-A-38 43 467. There, a predetermined fuel injection quantity is metered into an intermediate store via the electrically controlled valve in the fuel line discharging from the store, the output of which can be connected to the distributor opening via a second electrically controlled valve. The amount of fuel supplied to the intermediate store via the first electrically controlled valve, which is below the injection pressure provided by the high-pressure store, is measured by the stroke of a storage piston delimiting the intermediate store and the opening duration of the first electrically controlled valve is correspondingly determined by a control device. The first electrically controlled valve thus controls the amount of fuel to be injected. The second electrically controlled valve is opened at the desired injection point in time and the fuel stored by the intermediate store is conveyed to the respective injection nozzle.

Das zweite elektrisch gesteuerte Ventil bestimmt dabei den Einspritzzeitpunkt. Diese Einrichtung ist insofern recht aufwendig, als neben zwei elektrisch gesteuerten Ventilen auch noch ein Hochdruckzwischenspeicher erforderlich ist.The second electrically controlled valve determines the injection timing. This device is quite complex in that, in addition to two electrically controlled valves, a high-pressure intermediate store is also required.

Durch die EP-A1-0 381 954 ist ebenso eine Kraftstoffeinspritzpumpe der gattungsgemäßen Art bekannt. Das dort vorgesehen elektrisch gesteuerte Ventil ist in einer Verbindungsleitung, die vom Hochdruckspeicher zum Verteiler führt, stromaufwärts desselben angeordnet und steuert durch seine Offenstellung den Zeitpunkt des Einspritzbeginns und durch die Dauer seines geöffneten Zustands die Kraftstoffeinspritzmenge. Das elektrisch gesteuerte Ventil arbeitet dabei bezüglich seiner bestimmungsgemäßen Funktion als 2/2-Ventil und ermöglicht andererseits aufgrund seiner Ausgestaltung als 3/2-Ventil eine Entlastung des kraftstofführenden Bereichs zwischen elektrisch gesteuertem Ventil, Verteiler und einer jeweiligen Einspritzleitung bis zum dem Einspritzventil vorgeschalteten Druckventil. Aufgrund seiner Funktion zur Steuerung der Einspritzmenge als 2/2-Ventil muß das elektrisch gesteuerte Ventil gemäß diesem Stand der Technik ein sehr schnell arbeitendes Ventil sein, um auch bei kleinen Kraftstoffeinspritzmengen die erforderlichen Einspritzzeitpunkte und kurzen Einspritzdauern zu beherrschen. Dies bedingt, wenn eine erhöhte Genauigkeit bezüglich des Einspritzzeitpunktes erzielt werden soll, einen hohen technischen Aufwand für ein solches Ventil.A fuel injection pump of the generic type is also known from EP-A1-0 381 954. The electrically controlled valve provided there is arranged in a connecting line leading from the high-pressure accumulator to the distributor, upstream of the latter and, through its open position, controls the point in time at which injection begins and the duration of its open state, the fuel injection quantity. The electrically controlled valve operates as a 2/2 valve with regard to its intended function and, on the other hand, because of its design as a 3/2 valve, it relieves the pressure on the fuel-carrying area between the electrically controlled valve, distributor and a respective injection line up to the pressure valve upstream of the injection valve. Due to its function for controlling the injection quantity as a 2/2 valve, the electrically controlled valve according to this prior art must be a very fast-acting valve in order to be able to control the required injection times and short injection durations even with small fuel injection quantities. If an increased accuracy with regard to the injection point is to be achieved, this requires a high technical outlay for such a valve.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat den Vorteil, daß sie sehr einfach mit möglichst wenigen Bauelementen aufgebaut ist und vermittels der beiden elektrisch gesteuerten Ventile exakte, schnelle Steuerzeiten des Einspritzvorganges erzielt werden können.The fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that it is constructed very simply with as few components as possible and exact, fast control times of the injection process can be achieved by means of the two electrically controlled valves.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erstes Ausführungsbeispiel mit einer Radialkolbenverteilerpumpe als Druckerzeuger und als Einrichtung zur Ansteuerung mehrerer Kraftstoffeinspritzventile, die aus einem Hochdruckspeicher mit Kraftstoff versorgt werden und Figur 2 ein zweites Ausführungsbeispiel mit einer abgewandelten Ausführung einer Drucksteuereinrichtung, des Hochdruckspeichers des ersten Ausführungsbeispiels.Two embodiments of the invention are shown in the drawing and are explained in more detail in the following description. 1 shows a first exemplary embodiment with a radial piston distributor pump as a pressure generator and as a device for controlling a plurality of fuel injection valves which are supplied with fuel from a high-pressure accumulator, and FIG. 2 shows a second exemplary embodiment with a modified embodiment of a pressure control device, the high-pressure accumulator of the first exemplary embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Figur 1 zeigt einen Teilschnitt durch Teile einer Hochdruckpumpe der Bauart einer Radialkolbenverteilereinspritzpumpe. Hierbei wird ein Verteilerkolben 2 in einer Bohrung 3 durch einen nicht weiter gezeigten Antrieb rotierend angetrieben. Am Fuß 4 des Verteilers sind radial zu seiner Drehachse 5 liegende Pumpenzylinder 6 vorgesehen, in denen Pumpenkolben 7 hin- und herbeweglich sind und zwischen sich einen Pumpenarbeitsraum 8 einschließen. An ihrer außen liegenden Stirnseite liegen die Pumpenkolben an Rollenschuhen 10 mit Rollen 11 an, die bei der Drehung des Verteilerkolbens auf einer Nockenbahn 12 eines Nockenringes 13 ablaufen. Der Nockenring ist im Gehäuse 14 der Kraftstoffhochdruckpumpe gelagert.FIG. 1 shows a partial section through parts of a high-pressure pump of the radial piston distributor injection pump type. Here, a distributor piston 2 is driven in rotation in a bore 3 by a drive (not shown further). At the base 4 of the distributor, there are provided pump cylinders 6 lying radially to its axis of rotation 5, in which pump pistons 7 can be moved back and forth enclose a pump work space 8 between them. On its outer end face, the pump pistons rest on roller shoes 10 with rollers 11, which run on a cam track 12 of a cam ring 13 when the distributor piston rotates. The cam ring is mounted in the housing 14 of the high-pressure fuel pump.

Der Verteiler 2 weist eine erste Ringnut 15 und eine zweite Ringnut 16 im axialen Abstand davon aus. In diese zweite Ringnut 16 mündet eine Kraftstoffzufuhrleitung 17 über ein Füllventil 18 in Form eines Rückschlagventils ein, wobei die Kraftstoffzuführleitung von einer synchron zum Verteiler 2 angetriebenen Kraftstofförderpumpe 19 mit Kraftstoff versorgt wird der auf einen bestimmten Förderdruck mit Hilfe eines Drucksteuerventils 20 gehalten wird, das die Kraftstoffzuführleitung 17 zur Saugseite der Förderpumpe 19 entlastet. Von der zweiten Ringnut 16 führt ferner eine Druckleitung 22 ab, in der ein Förderventil 23 angeordnet ist, das als von der Ringnut 16 weg öffnendes Rückschlagventil ausgebildet ist. Die Druckleitung 22 mündet über dieses Förderventil 23 in einen Hochdruckspeicher 24. Die zweite Ringnut ist schließlich durch eine Druckleitung 26 in ständiger Verbindung mit dem Pumpenarbeitsraum 8.The distributor 2 has a first annular groove 15 and a second annular groove 16 at an axial distance therefrom. In this second annular groove 16, a fuel supply line 17 opens via a filling valve 18 in the form of a check valve, the fuel supply line being supplied with fuel by a fuel feed pump 19 driven synchronously with the distributor 2, which fuel is kept at a specific delivery pressure by means of a pressure control valve 20, which Relieved fuel supply line 17 to the suction side of the feed pump 19. A pressure line 22 also leads from the second annular groove 16, in which a delivery valve 23 is arranged, which is designed as a check valve opening away from the annular groove 16. The pressure line 22 opens into a high-pressure accumulator 24 via this delivery valve 23. The second annular groove is finally in constant communication with the pump work chamber 8 through a pressure line 26.

Der Hochdruckspeicher ist über eine Kraftstoffleitung 28, in der ein erstes elektrisch gesteuertes Ventil 29, hier ein Magnetventil, angeordnet ist, mit der ersten Ringnut 15 verbunden. Diese Ringnut ist ständig mit einer Verteileröffnung des Verteilers 2 in Form einer Verteilernut 31 verbunden, die sich parallel zur Drehachse des Verteilers erstreckend in die Mantelfläche des Verteilers eingearbeitet ist und die bei der Drehung des Verteilers nacheinander mit von der Bohrung 3 abführenden Einspritzleitungen 23 verbunden wird. Diese Einspritzleitungen 33 führen über ein Druckventil 34, das als übliches Druckventil oder als Gleichdruck- oder Gleichraumventil ausgeführt werden kann mit jeweils einer Kraftstoffeinspritzdüse an der Brennkraftmaschine verbunden.The high-pressure accumulator is connected to the first annular groove 15 via a fuel line 28, in which a first electrically controlled valve 29, here a solenoid valve, is arranged. This annular groove is permanently connected to a distributor opening of the distributor 2 in the form of a distributor groove 31, which is incorporated into the lateral surface of the distributor and extends parallel to the axis of rotation of the distributor and which is connected in succession to injection lines 23 leading away from the bore 3 when the distributor rotates . These injection lines 33 lead via a pressure valve 34, which as a conventional pressure valve or as Constant pressure or constant space valve can be connected to a fuel injector on the internal combustion engine.

Von der ersten Ringnut 15 zweigt ferner eine Entlastungsleitung 35 ab, in der ein zweites elektrisch gesteuertes Ventil 36, hier wiederum ein Magnetventil, angeordnet ist. Beide Magnetventile 29 und 36 werden von einer elektrischen Steuereinrichtung 37 gesteuert.A relief line 35 branches off from the first annular groove 15, in which a second electrically controlled valve 36, here again a solenoid valve, is arranged. Both solenoid valves 29 and 36 are controlled by an electrical control device 37.

Der Hochdruckspeicher 24 weist schließlich noch eine Entlastungsleitung 38 auf, in der entweder ein einen bestimmten Druck im Hochdruckspeicher 24 steuerndes Druckhalteventil 39 angeordnet ist, das mechanisch arbeitet oder ein elektrisch gesteuertes Ventil 40, hier wiederum ein Magnetventil, das von der elektrischen Steuereinrichtung 37 gesteuert wird nach Maßgabe von Signalen eines Druckgebers 41, der den Druck im Hochdruckspeicher 24 erfaßt und entsprechende Signale an die elektrische Steuereinrichtung abgibt.Finally, the high-pressure accumulator 24 also has a relief line 38, in which either a pressure-maintaining valve 39 which controls a specific pressure in the high-pressure accumulator 24 and which operates mechanically is arranged, or an electrically controlled valve 40, here again a solenoid valve which is controlled by the electrical control device 37 in accordance with signals from a pressure transmitter 41, which detects the pressure in the high-pressure accumulator 24 and emits corresponding signals to the electrical control device.

Die beschriebene Kraftstoffeinspritzeinrichtung arbeitet folgendermaßen: Wird der Verteilerkolben drehend angetrieben, was in der Regel über die Kurbelwelle der zugehörigen Brennkraftmaschine synchron zu deren Drehzahl erfolgt, so werden die Pumpenkolben den Nocken der Nockenbahn 12 über die Rollenschuhe 10 folgend hin- und herbewegt. Bei einer nach außen gehenden Bewegung entsprechend einem Saughub saugen dann die Pumpenkolben 7 Kraftstoff über das Füllventil 18 an. Beim daraufhin durch die Nocken der Nockenbahn bewirkten Druckhub verdrängen die Pumpenkolben 7 Kraftstoff unter Hochdruck über das Förderventil 23 in den Hochdruckspeicher bis dort ein bestimmter vorgegebener Druck erzielt ist. Dieser Druck kann entweder durch das Druckhalteventil 39 eingestellt werden oder über den Druckgeber 41 in Verbindung mit der elektrischen Steuereinrichtung 37 und das Magnetventil 40. Solange der vorbestimmte Druck in dem Speicher 24 nicht erreicht ist, erfolgt keine Abströmung über die Entlastungsleitung 38. Bei Überschreiten des eingestellten Drucks öffnet das Druckhalteventil oder das Magnetventil in analoger oder getakteter Weise.The fuel injection device described works as follows: If the distributor piston is driven in rotation, which is usually done via the crankshaft of the associated internal combustion engine in synchronism with its speed, the pump pistons are moved back and forth following the cams of the cam track 12 via the roller shoes 10. In the case of an outward movement corresponding to a suction stroke, the pump pistons 7 then suck in fuel via the filling valve 18. During the pressure stroke then caused by the cams of the cam track, the pump pistons 7 displace fuel under high pressure via the delivery valve 23 into the high-pressure accumulator until a certain predetermined pressure is achieved there. This pressure can either be set by the pressure holding valve 39 or via the pressure transmitter 41 in connection with the electrical one Control device 37 and the solenoid valve 40. As long as the predetermined pressure in the accumulator 24 has not been reached, there is no outflow via the relief line 38. When the set pressure is exceeded, the pressure-maintaining valve or the solenoid valve opens in an analog or clocked manner.

Ist der bestimmte Druck im Hochdruckspeicher erreicht, so kann aus diesem Kraftstoff zur Hochdruckeinspritzung an der Brennkraftmaschine entnommen werden. Dies geschieht über das erste elektrisch gesteuerte Ventil 29, das gesteuert von der elektrischen Steuereinrichtung zu einem gewünschten Einspritzbeginn geöffnet wird, wobei das zweite elektrisch gesteuerte Ventil 36 geschlossen ist. Der dann vom Hochdruckspeicher 24 abströmende Kraftstoff gelangt über die Verteilernut 31 und eine der Einspritzleitungen 33 zu der entsprechenden Kraftstoffeinspritzdüse und dort zur Einspritzung. Die Menge des dort einzuspritzenden Kraftstoffs wird durch das zweite elektrisch gesteuerte Ventil 36 gesteuert, indem dieses bei erreichter Kraftstoffeinspritzmenge geöffnet wird, so daß die erste Ringnut 15 entlastet wird und der Druck in der Einspritzleitung 33 bzw. am Kraftstoffeinspritzventil unter den Einspritzdruck sinkt. Zugleich mit dem Öffnen des zweiten elektrisch gesteuerten Ventils 36 wird vorzugsweise das erste elektrisch gesteuerte Ventil 29 geschlossen. Dieses Schließen des ersten elektrisch gesteuerten Ventils kann dabei auch kurzzeitig nach dem Öffnen des zweiten elektrisch gesteuerten Ventils 36 erfolgen. Im erstgenannten Fall ergibt sich ein Minimum an Verlust von auf Hochdruck gebrachten Kraftstoff aus dem Speicher 24. Mit Hilfe des Druckventils 34 wird dabei üblicherweise in den Pausen zwischen den Hochdruckeinspritzvorgängen ein gleichbleibender Druck in der Einspritzleitung zwischen Einspritzventil und Druckventil eingehalten, wenn dieses als Gleichdruckventil ausgestaltet ist. Es besteht aber auch die Möglichkeit durch eine Anordnung von Steuernuten am Verteilerkolben die einzelnen Einspritzleitungen nach erfolgter Einspritzung auf ein vorgegebenes Druckniveau zu entlasten.Once the specific pressure in the high-pressure accumulator has been reached, fuel can be drawn from the internal combustion engine for high-pressure injection. This takes place via the first electrically controlled valve 29, which is opened under the control of the electrical control device at a desired start of injection, the second electrically controlled valve 36 being closed. The fuel then flowing out of the high-pressure accumulator 24 reaches the corresponding fuel injection nozzle via the distributor groove 31 and one of the injection lines 33 and there for injection. The amount of fuel to be injected there is controlled by the second electrically controlled valve 36, in that it is opened when the fuel injection quantity is reached, so that the first annular groove 15 is relieved and the pressure in the injection line 33 or on the fuel injection valve drops below the injection pressure. Simultaneously with the opening of the second electrically controlled valve 36, the first electrically controlled valve 29 is preferably closed. This closing of the first electrically controlled valve can also take place briefly after the opening of the second electrically controlled valve 36. In the former case, there is a minimum loss of fuel brought to high pressure from the accumulator 24. With the help of the pressure valve 34, a constant pressure in the injection line between the injection valve and pressure valve is usually maintained in the breaks between the high pressure injection processes, if this is designed as a constant pressure valve is. But there is also the possibility of an arrangement of Control grooves on the distributor piston to relieve the individual injection lines after the injection to a predetermined pressure level.

Durch die Anordnung dieser genannten beiden elektrisch gesteuerten Ventile kann in getakteter Ansteuerung derselben ein exakter Kraftstoffeinspritzbeginn und ein exaktes Einspritzende bei den jeweiligen Einspritzvorgängen erzielt werden, wobei selbst kleinste Kraftstoffeinspritzmengen genau gesteuert werden können. Dies ergibt sich insbesondere als Vorteil in Verbindung mit dem auf einen konstanten Druck gebrachten Hochdruckspeicher, da über den gesamten Betriebsbereich der zugehörigen Brennkraftmaschine gleichbleibende Verhältnisse von anstehendem Einspritzdruck und Druckgefällen vorhanden sind. Kraftstoffeinspritzmengenstreuungen, die sich insbesondere aus einer Drehzahlabhängigkeit ergeben werden somit sehr klein gehalten. Ggf. können aber auch Drosselungen bei kurzen Einspritzzeiten bzw. hohen Drehzahlen durch entsprechende Angleichung des Drucks im Hochdruckspeicher kompensiert werden.By arranging these two electrically controlled valves, an exact start of fuel injection and an exact end of injection in the respective injection processes can be achieved in clocked activation thereof, whereby even the smallest fuel injection quantities can be precisely controlled. This results in particular as an advantage in connection with the high-pressure accumulator brought to a constant pressure, since constant conditions of the injection pressure and pressure drops present are present over the entire operating range of the associated internal combustion engine. Fuel injection quantity spreads, which result in particular from a speed dependency, are thus kept very small. Possibly. throttling at short injection times or high speeds can also be compensated for by appropriate adjustment of the pressure in the high-pressure accumulator.

Da die Einspritzventile jeweils nur mit einer Flanke nach Öffnung oder Schließbewegung in die Steuerung des Einspritzvorganges eingreifen, ist das Steuerergebnis weniger stark von der Schnelligkeit der Ventile in sowohl ihrem Öffnungsvorgang als auch ihrem Schließvorgang abhängig. Insbesondere lassen sich dabei ohne großen Aufwand steuernde schnelle Bewegungen der Ventile erzielen. Bei dem vorgeschlagenen System ergeben sich auch Vorteile darin, daß die Auslegung der Nocken der Nockenbahn nicht mehr auf die besonderen Verhältnisse während der Zeit der Einspritzung abgestimmt sein müssen. Die Nockenantriebe dienen dabei lediglich der Bereitstellung des hohen Einspritzdruckes. Um einen besonders gleichmäßigen Einspritzdruck zu erzielen ist es von Vorteil, mehrere Pumpenkolben vorzusehen bzw. mehrere Pumpenkolbenförderhübe pro Umdrehung des Verteilers. Dabei können die Förderhübe der Pumpenkolben in den Zeitabschnitten liegen, in denen auch die Kraftstoffeinspritzventile aus dem Hochdruckspeicher 24 zur Einspritzung mit Hochdruckkraftstoff versorgt werden. Damit wird der Speicher von evtl. entstehenden Druckpulsationen während der Einspritzvorgänge freigehalten.Since the injection valves only intervene in the control of the injection process with one flank after opening or closing movement, the control result is less dependent on the speed of the valves in both their opening process and their closing process. In particular, fast, controlling movements of the valves can be achieved without great effort. The proposed system also has advantages in that the design of the cams of the cam track no longer has to be matched to the special conditions during the time of the injection. The cam drives only serve to provide the high injection pressure. In order to achieve a particularly uniform injection pressure, it is advantageous to provide a plurality of pump pistons or a plurality of pump piston delivery strokes per revolution of the distributor. The conveying strokes can Pump pistons are in the periods in which the fuel injection valves from the high-pressure accumulator 24 are also supplied with high-pressure fuel for injection. The memory is thus kept free of any pressure pulsations that may occur during the injection processes.

Die Steuerung des Speicherdruckes kann wie beschrieben über eine Abströmsteuerung erfolgen oder aber auch über die Steuerung einer Fördermenge der Hochdruckpumpe, was den Vorteil einer geringeren Antriebsleistung hätte aber einen etwas größeren Aufwand bedeutet.As described, the storage pressure can be controlled via an outflow control or else via the control of a delivery rate of the high-pressure pump, which would have meant the advantage of a lower drive power but a somewhat greater effort.

Die Auslegung der Förderleistung der Hochdruckpumpe bietet dabei in vorteilhafter Weise die Möglichkeit bereits bei niedriger Drehzahl einen hohen Einspritzdruck im Speicher 24 zu erzeugen, wobei dann der Speicher bei höherer Drehzahl entsprechend entlastet wird bei ggf. möglicher Angleichung des Speicherdrucks an die Drehzahl.The design of the delivery capacity of the high-pressure pump advantageously offers the possibility of generating a high injection pressure in the accumulator 24 even at a low speed, in which case the accumulator is relieved accordingly at a higher speed, with the possible adjustment of the accumulator pressure to the speed.

Die beschriebene Kraftstoffeinspritzeinrichtung zeichnet sich vor allen Dingen durch Einfachbauteile auf mit universellen Steuermöglichkeiten von Einspritzbeginn und Einspritzmenge.The fuel injection device described is characterized above all by simple components with universal control options for the start of injection and the amount of injection.

Statt der beschriebenen Radialkolbenpumpe als Erzeuger für den hohen Einspritzdruck kann auch gemäß Figur 2 eine Pumpe der Axialkolbenpumpenbauart verwendet werden. Eine solche hat eine rotierend angetriebene Stirnnockenscheibe 44, die auf ortsfest gelagerten Rollen, von denen nur eine gezeigt ist, abläuft. Mit der Stirnnockenscheibe verbunden ist ein Pump- und Verteilerkolben 46, der sowohl drehend von der Stirnnockenscheibe 44 mitgenommen wird als auch durch den Ablauf der Nockenbahn 47 der Stirnnockenscheibe auf den Rollen 45 axial hin- und herbewegt wird in einem Pumpenzylinder 48, in den der Pump- und Verteilerkolben 46 stirnseitig einen Pumpenarbeitsraum 49 einschließt.Instead of the radial piston pump described as a generator for the high injection pressure, a pump of the axial piston pump type can also be used according to FIG. One of these has a rotatingly driven front cam disk 44, which runs on fixedly mounted rollers, only one of which is shown. Connected to the end cam disk is a pump and distributor piston 46, which is rotatably carried along by the end cam disk 44 and is axially moved back and forth on the rollers 45 by the cam track 47 of the end cam disk in a pump cylinder 48 into which the pump - And distributor piston 46 includes a pump work chamber 49 at the end.

Die Stirnnockenscheibe wird bei ihrer Drehung durch eine starke Rückstellfeder 50 in Anlage an den Rollen 45 gehalten, so daß der Pumpenkolben 46 sicher seinen Saughub ausführt. Durch die Stirnnockenscheibe wird der Pumpenkolben während einer vollkommenen Umdrehung in mehrere hin- und hergehende mit dem Pumpenarbeitsraum 49 verbundene Saug- und Förderhub bewegt. Bei seinen Saughüben saugt er über eine mit dem Pumpenarbeitsraum 49 verbundene Saugnut 51 in seiner Mantelfläche und einer in den Pumpenzylinder 48 mündende Kraftstoffzufuhr- oder Saugleitung 52 Kraftstoff an. Bei beginnendem Förderhub verschließen die die Saugnut begrenzenden Steuerkanten die Einmündung der Saugleitung 52 und der im Pumpenarbeitsraum 49 befindliche Kraftstoff wird komprimiert und über eine axiale Sackbohrung 54, die von der Stirnseite des Pumpenkolbens 46 ausgeht sowie eine Querbohrung 55 in eine Ringnut 56 in der Oberfläche des im Pumpenzylinder 48 geführten Bereiches des Pumpenkolbens geleitet. Diese Ringnut 56 ist in ständiger Verbindung mit einer Druckleitung 57, die der Druckleitung 22 entspricht und in den Hochdruckspeicher 24 mündet und ein Förderventil 23 enthält. Weiterhin ist die Ringnut 56 in ständiger Verbindung mit einer Entlastungsleitung 58, in der ein Druckhalteventil 59, das zur Entlastungsseite öffnet, angeordnet ist.The end cam disk is held in contact with the rollers 45 by a strong return spring 50 so that the pump piston 46 safely performs its suction stroke. Through the front cam disc, the pump piston is moved during a complete revolution into a plurality of reciprocating suction and delivery strokes connected to the pump working chamber 49. During its suction strokes, it sucks in fuel via a suction groove 51 connected to the pump working space 49 in its outer surface and a fuel supply or suction line 52 opening into the pump cylinder 48. When the delivery stroke begins, the control edges delimiting the suction groove close the mouth of the suction line 52 and the fuel located in the pump work chamber 49 is compressed and via an axial blind bore 54, which starts from the end face of the pump piston 46 and a transverse bore 55 in an annular groove 56 in the surface of the guided in the pump cylinder 48 area of the pump piston. This annular groove 56 is in constant communication with a pressure line 57, which corresponds to the pressure line 22 and opens into the high-pressure accumulator 24 and contains a delivery valve 23. Furthermore, the annular groove 56 is in constant communication with a relief line 58, in which a pressure-maintaining valve 59, which opens to the relief side, is arranged.

Weiterhin ist auch bei diesem Ausführungsbeispiel neben der bereits genannten zweiten Ringnut 56 eine erste Ringnut 60 in der Mantelfläche des Pumpenkolbens 46 vorgesehen entsprechend der erste Ringnut 15 bzw. der zweiten Ringnut 16 vom Ausführungsbeispiel Figur 1. Diese erste Ringnut 16 ist wiederum über eine Kraftstoffleitung 28 mit dem Hochdruckspeicher 24 verbunden und enthält das erste elektrisch gesteuerte Ventil 29. Von der ersten Ringnut 60 zweigt ferner die Entlastungsleitung 35 ab mit dem zweiten elektrisch gesteuerten Ventil 36. Schließlich ist mit der ersten Ringnut 60 auch wiederum die Verteilernut 31 verbunden, über die im Laufe der Drehung des Pump- und Verteilerkolbens 46 jeweils beim Förderhub eine der Einspritzleitungen 31 angesteuert wird, die ebenfalls ein Druckventil 34 enthält und zum jeweiligen Einspritzventil an der Kraftstoffeinspritzpumpe führt. Insofern ist dieses Ausführungsbeispiel bezüglich der ersten Ringnut 60 gleich aufgebaut wie das Ausführungsbeispiel nach Figur 1, wobei die Breite der Ringnut in Achsrichtung des Pumpenkolbens 46 und die Länge der Verteilernut die pumpenden Hubbewegungen des Pumpenkolbens 46 berücksichtigen müssen. Die Ansteuerung der Magnetventile 29 und 36 erfolgt in gleicher Weise wie beim Ausführungsbeispiel nach Figur 1 wie auch die vorgesehenen Pumphübe des Pumpenkolbens analog den Hinweisen zu Figur 1 ausgelegt sein können. Abweichend ist bei diesem Ausführungsbeispiel, daß ein Füllventil in Form eines Rückschlagventils 18 entfällt, es ist noch gestrichelt in der Figur eingezeichnet, und dafür die Saugsteuerung mit Hilfe der Saugnut 15 vorgesehen ist. Bei dieser Steuerung können entweder Saugnuten entsprechend der Zahl der Saughübe des Pumpenkolbens pro Umdrehung vorgesehen sein mit einer einzigen Saugleitung 52 oder auch mehreren, oder es ist nur eine Saugnut vorgesehen und es sind die Saugleitungen entsprechend der Zahl der Saughübe des Pumpenkolbens am Umfang des Pumpenzylinders 48 verteilt angeordnet. In bezug auf die Lebensdauer bietet eine solche Steuerung des Saughubes mit Hilfe einer Steuerkante Vorteile gegenüber einem als Rückschlagventil ausgebildeten Füllventil. Sie ist natürlich auch analog beim Ausführungsbeispiel nach Figur 1 verwendbar. Abweichend vom Ausführungsbeispiel nach Figur 1 aber dort ebenfalls so ausführbar, ist es ferner, daß das Druckhalteventil 59 nun stromaufwärts des Förderventils 23 liegt, so daß frühzeitig ein zu hoher Druckanstieg abgebaut werden kann. Das hier als Rückschlagventil ausgebildete Druckhalteventil 59 kann natürlich auch analog zum Ausführungsbeispiel nach Figur 1 ein von einem Drucksensor gesteuertes Magnetventil sein.Furthermore, in this exemplary embodiment, in addition to the second annular groove 56 already mentioned, a first annular groove 60 is provided in the lateral surface of the pump piston 46, corresponding to the first annular groove 15 or the second annular groove 16 from the exemplary embodiment in FIG. 1. This first annular groove 16 is in turn via a fuel line 28 connected to the high-pressure accumulator 24 and contains the first electrically controlled valve 29. The relief line 35 also branches off from the first annular groove 60 with the second electrically controlled valve 36. Finally, the distributor groove 31 is also connected to the first annular groove 60, via which in the Course of the rotation of the pump and distributor pistons 46 each during the delivery stroke, one of the injection lines 31 is actuated, which likewise contains a pressure valve 34 and leads to the respective injection valve on the fuel injection pump. In this respect, this exemplary embodiment with respect to the first annular groove 60 has the same structure as the exemplary embodiment according to FIG. 1, the width of the annular groove in the axial direction of the pump piston 46 and the length of the distributor groove having to take into account the pumping stroke movements of the pump piston 46. The solenoid valves 29 and 36 are actuated in the same way as in the exemplary embodiment according to FIG. 1, and the intended pump strokes of the pump piston can be designed analogously to the instructions for FIG. 1. The difference in this embodiment is that a filling valve in the form of a check valve 18 is omitted, it is also shown in broken lines in the figure, and the suction control with the aid of the suction groove 15 is provided for this. With this control, either suction grooves corresponding to the number of suction strokes of the pump piston per revolution can be provided with a single suction line 52 or more, or only one suction groove is provided and the suction lines are corresponding to the number of suction strokes of the pump piston on the circumference of the pump cylinder 48 distributed. In terms of service life, such control of the suction stroke with the aid of a control edge offers advantages over a filling valve designed as a check valve. It can of course also be used analogously in the exemplary embodiment according to FIG. 1. Deviating from the exemplary embodiment according to FIG. 1, but also executable there, it is furthermore the case that the pressure holding valve 59 is now upstream of the delivery valve 23, so that an excessively high pressure rise can be reduced at an early stage. The pressure-maintaining valve 59 designed here as a check valve can of course also be a solenoid valve controlled by a pressure sensor, analogous to the exemplary embodiment according to FIG.

Wenn hier die Druckerzeugung mit Hilfe von Pumpen entsprechend der Ausgestaltung von üblichen Verteilerpumpenbauarten vorgenommen wurde, wobei diese Pumpen zugleich neben der Druckerzeugung für den Hochdruckspeicher auch die Verteilerfunktion übernehmen ist es auch möglich, eine Hochdruckpumpe und einen separaten Verteiler in bekannter Weise vorzusehen. Die Hochdruckerzeugung ist im Prinzip unabhängig von der Verteilerfunktion. Es ergibt sich aber eine sehr kompakte Baueinheit, wenn eine Pumpe der Verteilerpumpenbauart als Druckerzeuger verwendet wird.If here the pressure generation was carried out with the aid of pumps corresponding to the design of conventional distributor pump types, these pumps also taking on the distributor function in addition to the pressure generation for the high-pressure accumulator, it is also possible to provide a high-pressure pump and a separate distributor in a known manner. The high pressure generation is in principle independent of the distributor function. However, a very compact structural unit results if a pump of the distributor pump type is used as a pressure generator.

Claims (7)

  1. Fuel injection device for internal combustion engines, with a high-pressure pump which sucks up fuel into a pump working space (8, 49) via a filling valve (18; 51; 52) and which feeds the fuel, brought to high pressure, in a high-pressure reservoir (24) via a feed valve (23), the pressure of which reservoir is maintained at a specific value via a pressure-control device (39, 59; 40, 41, 37), with a distributor (2, 46) which is driven synchronously with the internal combustion engine and which, during its rotation, successively activates via a distributor port (31) injection conduits (33) leading to various injection valves on the internal combustion engine, and with a first electrically controlled valve (29) in a fuel conduit (28, 16, 60, 31) leading from the high-pressure reservoir (24) to the distributor port (31), characterized in that, downstream of the first electrically controlled valve (29) and of the distributor port, a second electrically controlled valve (36) is provided in a relief conduit (35) connected to the distributor port (31), and in that, in order to control the injection timing and the injection quantity, the start of injection is determined by the opening of the first electrically controlled valve (29), with the second electrically controlled valve (36) closed, and the end of injection is determined by the opening of the second electrically controlled valve (36).
  2. Fuel injection device according to Claim 1, characterized in that the first electrically controlled valve (29) is activated into its closing operation at the same time as the opening of the second electrically controlled valve (36).
  3. Fuel injection device according to Claim 1, characterized in that the first electrically controlled valve (29) is closed after the opening of the second electrically controlled valve (36).
  4. Fuel injection device according to one of the preceding Claims, characterized in that the pressure-control device has a relief conduit (38, 58) which contains a valve (39, 40, 59) and which can be connected to the pump working space upstream of the feed valve.
  5. Fuel injection device according to one of the preceding Claims, characterized in that the feed valve (23) is a non-return valve.
  6. Fuel injection device according to one of the preceding Claims, characterized in that the suction valve (18) is a non-return valve.
  7. Fuel injection device according to one of Claims 1 to 5, characterized in that the suction valve consists of a control edge (51) which is moved synchronously with the pump-piston drive and by means of which the pump working space (49), during the suction stroke of the pump piston, is connected to a fuel supply space and, during the high-pressure feed of the pump piston, is separated from the said fuel supply space.
EP93907795A 1992-04-25 1993-04-10 Fuel injection device for internal combustion engines Expired - Lifetime EP0596054B1 (en)

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DE4213720 1992-04-25
DE4213720 1992-04-25
PCT/DE1993/000330 WO1993022554A1 (en) 1992-04-25 1993-04-10 Fuel injection device for internal combustion engines

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EP0596054A1 EP0596054A1 (en) 1994-05-11
EP0596054B1 true EP0596054B1 (en) 1996-03-13

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EP (1) EP0596054B1 (en)
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DE3843467A1 (en) * 1988-12-23 1990-06-28 Bosch Gmbh Robert FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
DE3903313A1 (en) * 1989-02-04 1990-08-09 Bosch Gmbh Robert STORAGE FUEL INJECTION DEVICE
GB8918429D0 (en) * 1989-08-12 1989-09-20 Lucas Ind Plc Fuel pumping apparatus
DE4019586A1 (en) * 1990-06-20 1992-01-02 Bosch Gmbh Robert FUEL INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES
US5265576A (en) * 1993-01-08 1993-11-30 Stanadyne Automotive Corp. Calibration system for electrically controlled fuel injection pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19904074A1 (en) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Delivery arrangement for liquid medium has step change transmission between electric motor of electric drive arrangement and distributor arrangement
DE19904075A1 (en) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Liquid medium delivery arrangement has valve unit between pressure reservoir and distributor arrangement to determine start of delivery and dosing of liquid medium

Also Published As

Publication number Publication date
KR940701500A (en) 1994-05-28
DE59301885D1 (en) 1996-04-18
EP0596054A1 (en) 1994-05-11
JPH07500400A (en) 1995-01-12
WO1993022554A1 (en) 1993-11-11
US5363824A (en) 1994-11-15

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