EP1597474B1 - Fuel injection device - Google Patents

Fuel injection device Download PDF

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Publication number
EP1597474B1
EP1597474B1 EP04712002A EP04712002A EP1597474B1 EP 1597474 B1 EP1597474 B1 EP 1597474B1 EP 04712002 A EP04712002 A EP 04712002A EP 04712002 A EP04712002 A EP 04712002A EP 1597474 B1 EP1597474 B1 EP 1597474B1
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EP
European Patent Office
Prior art keywords
control
pump
piston
beginning
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04712002A
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German (de)
French (fr)
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EP1597474A1 (en
Inventor
Hans-Joachim Koch
Horst Ressel
Wolfgang Scheibe
Günther SCHRÖDLEN
Norbert Walter
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LOrange GmbH
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LOrange GmbH
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Publication date
Priority claimed from DE10319623A external-priority patent/DE10319623A1/en
Application filed by LOrange GmbH filed Critical LOrange GmbH
Publication of EP1597474A1 publication Critical patent/EP1597474A1/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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/28—Mechanisms therefor
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the invention relates to a fuel injection device, with a designed as a double-piston pump fuel pump, which promotes fuel for injecting into the combustion chamber of an internal combustion engine to a respective associated injector.
  • a cross section of the nozzle needle is acted upon by the fuel supplied by the fuel pump, which causes an opening force on the nozzle needle in the opening direction.
  • the fuel pressure during an injection increases until it reaches a maximum pressure, and then drops again.
  • a double piston pump of the type required, which is prior art in itself, has two pump pistons, each pump piston being associated with a control rod with which the delivery start and delivery end of the respective pump piston can be controlled by rotation of the pump piston.
  • Such double piston pumps have the advantage that large flow rates are possible with a small volume.
  • one of the two pump pistons is used to set the start of delivery and the delivery end.
  • the pumping is carried out by the non-controlled pump piston before the start of delivery and after delivery Amount of fuel controlled via the control bores of the controlled pump piston.
  • the document US 3 976 249 A shows a fuel injection system in which, in addition to the injection pump and the injector, there is a device for providing a control pressure, which control pressure variably sets the closing force acting on the nozzle needle of the injector.
  • the indicated in claim 1 invention is based on the problem of optimizing a fuel injection device containing a double piston pump with respect to the course of injection.
  • a control line is provided, which is connected to first control chambers of all injectors and provides a control pressure, which is a pressurization of the control chambers associated, acting on the nozzle needle in the closing direction of the piston for variable adjustment of the force acting in the closing direction of the nozzle needle force before the start of an injection depending on engine operating parameters.
  • control rod is advantageously carried out in dependence on the pressure prevailing in the control line.
  • the adjustment of the control rod can be done for example hydraulically or electrically by means of an electric motor.
  • control pressure applied in the control line is used directly for adjusting the control rod of the pump piston controlling the start of delivery.
  • the applied in the control line control pressure is set higher depending on operating parameters at low speeds of the internal combustion engine than at higher speeds.
  • a high, low speeds corresponding Control pressure corresponds to the first pump piston (70) an adjustment of the start of delivery in the direction of EARLY
  • a low, high rotational speeds corresponding control pressure corresponds to an adjustment of the start of delivery in the direction of LATE.
  • a further control line can be provided, with which the force acting on the nozzle needle closing force is increased during injection to raise the closing pressure.
  • the necessary control pressure can be removed at a bore which is arranged in the pump cylinder of the second pump piston controlling the delivery end of the double piston pump to use the Abêttik for acting on the nozzle needle in the closing direction before the pressure drop reaches the injection nozzle at the end.
  • the first, by the control rod rotatable pump piston with the control bores cooperating control edges are associated on the circumference, which are formed with steps.
  • the steps are staircase-shaped, and the step width is greater than the diameter of the control bores applied.
  • control rod (71) for stepwise adjustment with gradually variable control pressure can be acted upon.
  • Figure 1 shows an injection system with respect to the opening and closing pressure customizable injectors, each associated with a double-piston fuel pump;
  • Figure 2 shows a pump piston with stepped control edge, as he can find the stepwise adjustment of the start of injection in the double-piston fuel pump application.
  • FIG. 1 shows a fuel injection device with two injectors 5, to each of which a double-piston pump 1 is assigned.
  • the pump pistons 70, 73 of the fuel pump 1 are each driven by a cam, which is not shown. Due to the delivery characteristic of the fuel pump, the pressure in an injection line 4, which is connected to the supply line 6 of an injector 5, increases until it reaches a maximum value, and then drops off again at the end.
  • the injectors 5 are pressure-controlled, that is, the injection is controlled by pressurizing a nozzle space 11 with the fuel pressure acting on a collar of the nozzle needle 12, which is a circular ring surface located between the seated sealing diameter and the nozzle needle guide diameter.
  • a control line 9 is shown in the figure, which branches off from it via the first 7 and second 8 control lines is connected to each injector 5.
  • the control pressure acts on pistons 16 and 17, the control chambers 13 and 14 are assigned.
  • the control pressure applied in the first control chamber 13 before the beginning of the injection causes an increase in the nozzle opening pressure.
  • the control pressure via a control line 9 is also applied to the control rod 71 of the double-piston pump 1.
  • the control pressure is used on the control rod 71 to adjust the start of delivery to compensate for the injection start timing by increasing the nozzle opening pressure.
  • control rod In order to adjust the control rod, for example, depending on engine operating conditions deviating from the pressure prevailing in the control line 9 pressure, it is expedient not directly to apply the adjustment for the control rod with the control pressure in the control line 9, but a separate hydraulic or electrical control circuit use.
  • a control signal derived from the control pressure, a control signal, which is converted into a new electrical or hydraulic control variable.
  • suitable electrical or hydraulic control variables from the control signal for example, electronically stored tables can be used.
  • a device for generating the control pressure consists for example of an engine control unit 82 which controls a pressure regulating valve 83.
  • a control fluid can serve for example engine oil, which is removed from a motor oil tank 81 by a pump 80.
  • the double piston pump 1 is formed with a first 70 and a second 73 pump piston with pump cylinders 72, 75.
  • the pump piston 70, 73 are associated with control rods 71 and 77.
  • the first pump piston 70 is used according to the invention for controlling the start of delivery and the second pump piston 73 for controlling the delivery end.
  • the subsidized fuel The delivery start of the first pump piston is, for example, adjusted by the over the control line 9, 7 on the control rod 71 pressure at low speed of the engine in the direction of EARLY and at higher speeds in the direction LATE.
  • the adjustment of the control rod may require deviating control strategies depending on the engine operating condition. Accordingly, the control rod 71 must then be provided with an adjusting device which can be controlled independently of the pressure prevailing in the control line.
  • the second pump piston 73 can lead the first pump piston 70 with regard to the start of delivery, wherein the fuel delivered by the second pump piston 73 before the start of delivery of the first pump piston 70 is discharged via the control bores associated with the first pump
  • the injector can be acted upon via the second control chamber 14 during an injection via the second control line 8 additionally with fuel pressure or other control fluid to increase the closing pressure.
  • the illustrated injector 5 is a valve 20 which is automatically controlled by the stroke of the nozzle needle 12.
  • the second control lines 8 can branch off from the common control line 9 or be connected to a further, not shown, separate from the control line 9 control line, which has a different pressure level.
  • control chamber 14 can also be connected to a bore 61 of the pump cylinder 75 via a control line 60, which is shown only in sections for reasons of clarity.
  • the bore is arranged in the pump cylinder 75 so that the Ab Kunststoffeck rests in the control line 61 before the pressure drop at the delivery end of the injection nozzle reached.
  • the closing pressure can be additionally increased.
  • the control line 60 can also replace the second control lines 8 and serve exclusively for regulating the closing pressure.
  • the pump piston 70 shown in Figure 2 with stepped control edge 100 can be used in the double piston pump instead of a pump piston with a continuously extending control edge to control the start of injection.
  • the start of injection is undesirably delayed.
  • the rotational position of the pump piston 70 is corrected by the control rod 71.
  • the necessary adjustment of the control rod 71 can be done by any means, for example, with the help of the applied in the control line 9 control pressure acting on a control piston of the control rod 71, and a displacement of the control piston 71 causes a rotation of the pump piston 70.
  • the control piston of the control rod 71 operates against a rising with increasing travel force, such as the force of a spring, so that each control pressure a certain travel can be assigned, which corresponds to a specific rotational position of the pump piston 70.
  • the horizontal, circumferentially extending and axially offset portions are arranged as the steps of a staircase.
  • the transition from one horizontal step to the next horizontal step is preferably designed so that with the smallest possible angle of rotation of the pump piston 70, the respective next step is achieved.
  • An expedient embodiment are steps with horizontal and approximately vertical sections. Vertical means running in the direction of the longitudinal axis of the pump piston.
  • control error compensation is advantageous not only in connection with the illustrated type of actuation with pressurization of the control rod 71. Rather, the stepped control edge 100 is advantageously used in conjunction with other means for actuating the control rod 71.

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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 invention relates to a fuel injection device comprising a fuel pump embodied as a double piston pump which is used to pump fuel into the combustion chamber of an internal combustion engine to an injector respectively associated therewith and which is optimized with regard to the injection process thereof. The double piston pump comprises two pistons (70, 73) which pump in parallel along a common line and which are provided with control edges. A control rod (71,74) is associated with each piston (70,73) and is used to control the beginning and end of the pumping. The beginning of the pumping can be adjusted on the first piston (70) and the end of the pumping can be adjusted on the second piston (73). A control pressure is provided prior to the beginning of injection according to engine operation parameters in order to adjust the force acting upon the injector needle (12) in the direction of closure, said pressure enabling pressure to be impinged upon the valve needle (12) in the direction of closure. In order to compensate an alteration in the beginning of injection caused thereby, the control rod (71) of the first piston (70) regulating the beginning of pumping is adjusted accordingly.

Description

Die Erfindung betrifft eine Kraftstoffeinspritzeinrichtung, mit einer als Doppelkolbenpumpe ausgebildeten Kraftstoffpumpe, die zum Einspritzen in den Brennraum einer Brennkraftmaschine Kraftstoff zu einem ihr jeweils zugeordneten Injektor fördert. Zur Steuerung von Beginn und Ende einer Einspritzung wird ein Querschnitt der Düsennadel mit dem von der Kraftstoffpumpe gelieferten Kraftstoff beaufschlagt, der eine Öffnungskraft an der Düsennadel in Öffnungsrichtung bewirkt. Entsprechend der Fördercharakteristik der Doppelkolbenpumpe steigt der Kraftstoffdruck während einer Einspritzung bis zum Erreichen eines Höchstdrucks an, um dann wieder abzufallen.The invention relates to a fuel injection device, with a designed as a double-piston pump fuel pump, which promotes fuel for injecting into the combustion chamber of an internal combustion engine to a respective associated injector. To control the beginning and end of an injection, a cross section of the nozzle needle is acted upon by the fuel supplied by the fuel pump, which causes an opening force on the nozzle needle in the opening direction. According to the delivery characteristic of the double piston pump, the fuel pressure during an injection increases until it reaches a maximum pressure, and then drops again.

Eine Doppelkolbenpumpe der vorausgesetzten Bauart, die an sich Stand der Technik ist, besitzt zwei Pumpenkolben, wobei jedem Pumpenkolben eine Steuerstange zugeordnet ist, mit der Förderbeginn und Förderende des jeweiligen Pumpenkolbens durch Verdrehung des Pumpenkolbens regelbar ist. Derartige Doppelkolbenpumpen haben den Vorteil, dass große Fördermengen möglich sind bei kleinem Bauvolumen. Bei einer aus dem Stand der Technik bekannten Anwendung wird jeweils einer der beiden Pumpenkolben dazu benutzt, um Förderbeginn und Förderende einzustellen. Dadurch, dass beide Pumpenkolben parallel auf eine gemeinsame Leitung fördern, wird die vor Förderbeginn und nach Förderende vom nicht gesteuerten Pumpenkolben geförderte Kraftstoffmenge über die Steuerbohrungen des gesteuerten Pumpenkolbens abgesteuert.A double piston pump of the type required, which is prior art in itself, has two pump pistons, each pump piston being associated with a control rod with which the delivery start and delivery end of the respective pump piston can be controlled by rotation of the pump piston. Such double piston pumps have the advantage that large flow rates are possible with a small volume. In an application known from the prior art, in each case one of the two pump pistons is used to set the start of delivery and the delivery end. As a result of the fact that both pump pistons convey in parallel to a common line, the pumping is carried out by the non-controlled pump piston before the start of delivery and after delivery Amount of fuel controlled via the control bores of the controlled pump piston.

Im Weiteren ist es aus dem Stand der Technik bekannt, bei Einspritzsystemen mit Einfachkolbenpumpen den Öffnungsdruck eines Einspritzventils in Abhängigkeit von Motorparametern zu variieren, um eine bessere Zerstäubung des eingespritzten Kraftstoffs zu erreichen. Ein derartiges Kraftstoffeinspritzsystem geht beispielsweise aus der US 4,403,585 als bekannt hervor, bei dem die Düsennadelzuhaltekraft durch hydraulische Beaufschlagung eines auf die Ventilschließfeder wirkenden Kolbens variiert wird. Nachteil bei diesem System ist, dass mit Erhöhung der Zuhaltekraft zwar der Beginn der Einspritzung zu höheren Einspritzdrücken hin verschoben wird, aber mit der Verschiebung des Einspritzbeginns zugleich eine ungewollte Verschiebung des Einspritzbeginns nach SPÄT verbunden ist.Furthermore, it is known from the prior art to vary in injection systems with single piston pumps the opening pressure of an injection valve in dependence on engine parameters in order to achieve a better atomization of the injected fuel. Such a fuel injection system is known, for example from US 4,403,585 as known, in which the nozzle needle clamping force is varied by hydraulic loading of a force acting on the valve closing spring piston. Disadvantage of this system is that with increasing the clamping force, although the beginning of the injection is shifted towards higher injection pressures, but with the shift of the injection start at the same time an unwanted shift of the injection start is connected to LATE.

Im Weiteren ist es beispielsweise aus der DE 25 00 644 C2 bekannt, dass Kraftstoffeinspritzventile in Folge der unterschiedlichen Beaufschlagungsquerschnitte für den Kraftstoff in geschlossenem und geöffneten Zustand eine Differenz zwischen Öffnungs- und Schließdruck aufweisen. Deshalb wird der Schließdruck über den durch die Nadelgeometrie bestimmten Wert angehoben, indem die Düsennadel nach Einspritzbeginn mit einer zusätzlichen Schließkraft beaufschlagt wird.Furthermore, it is known, for example, from DE 25 00 644 C2 that fuel injection valves have a difference between the opening and closing pressure in the closed and opened state as a result of the different admission cross sections for the fuel. Therefore, the closing pressure is raised above the value determined by the needle geometry by applying an additional closing force to the nozzle needle after the start of injection.

Das Dokument US 3 976 249 A zeigt ein Kraftstoffeinspritzsystem, bei dem neben der Einspritzpumpe und den lujektozen eine Vorrichtung zum Bereitstellen eines Steuerdruckes vorhanden ist, welcher Steuerdruck die auf die Düsennadel des Injektors wirkende Schließkraft variabel einstellt.The document US 3 976 249 A shows a fuel injection system in which, in addition to the injection pump and the injector, there is a device for providing a control pressure, which control pressure variably sets the closing force acting on the nozzle needle of the injector.

Der im Patentanspruch 1 angegebenen Erfindung liegt das Problem zu Grunde, eine eine Doppelkolbenpumpe enthaltende Kraftstoffeinspritzeinrichtung hinsichtlich des Einspritzverlaufs zu optimieren.The indicated in claim 1 invention is based on the problem of optimizing a fuel injection device containing a double piston pump with respect to the course of injection.

Dieses Problem wird durch die im Patentanspruch aufgeführten Merkmale dadurch gelöst, dass am ersten Pumpenkolben der Dop-pelkolbenpumpe der Förderbeginn und am zweiten Pumpenkolben das Förderende eingestellt wird, wobei der zweite Pumpenkolben dem ersten Pumpenkolben hinsichtlich des Förderbeginns voreilt und der zweite Pumpenkolben dem ersten Pumpenkolben hinsichtlich des Förderendes nacheilt, wobei der vom zweiten Pumpenkolben vor dem Förderbeginn des ersten Pumpenkolbens geförderte Kraftstoff über die dem ersten Pumpenkolben zugeordneten Steuerbohrungen abgeführt wird, und wobei der vom ersten Pumpenkolben nach dem Förderende des zweiten Pumpenkolbens geförderte Kraftstoff über die dem zweiten Pumpenkolben zugeordneten Steueröffnungen abgeführt wird. Des weiteren ist eine Steuerleitung vorgesehen, die mit ersten Steuerräumen aller Injektoren verbunden ist und einen Steuerdruck bereitstellt, der eine Druckbeaufschlagung von den Steuerräumen zugeordneten, auf die Düsennadel in Schließrichtung wirkenden Kolben zur variablen Einstellung der in Schließrichtung auf die Düsennadel wirkenden Kraft vor Beginn einer Einspritzung in Abhängigkeit von Motorbetriebsparametern ermöglicht.This problem is solved by the features listed in the claim, characterized in that on the first pump piston of the double-piston pump the delivery end and the second pump piston, the delivery end is set, wherein the second pump piston leads the first pump piston with respect to the start of delivery and the second pump piston lags the first pump piston with respect to the delivery end, wherein the funded by the second pump piston before the start of delivery of the first pump piston fuel via the the first pump piston associated control bores is discharged, and wherein the funded from the first pump piston to the delivery end of the second pump piston fuel is discharged via the second pump piston associated control ports. Furthermore, a control line is provided, which is connected to first control chambers of all injectors and provides a control pressure, which is a pressurization of the control chambers associated, acting on the nozzle needle in the closing direction of the piston for variable adjustment of the force acting in the closing direction of the nozzle needle force before the start of an injection depending on engine operating parameters.

Zur Kompensation der damit verbundenen Spritzbeginnveränderung erfolgt eine Verstellung der Steuerstange zweckmäßigerweise in Abhängigkeit von dem in der Steuerleitung herrschenden Druck. Die Verstellung der Steuerstange kann beispielsweise hydraulisch oder auch elektrisch mittels eines Elektromotors erfolgen.To compensate for the associated start of injection change an adjustment of the control rod is advantageously carried out in dependence on the pressure prevailing in the control line. The adjustment of the control rod can be done for example hydraulically or electrically by means of an electric motor.

Zweckmäßigerweise wird der in der Steuerleitung anliegende Steuerdruck unmittelbar zur Einstellung der Steuerstange des den Förderbeginn regelnden Pumpenkolbens benutzt.Conveniently, the control pressure applied in the control line is used directly for adjusting the control rod of the pump piston controlling the start of delivery.

Zweckmäßigerweise wird der in der Steuerleitung anliegende Steuerdruck in Abhängigkeit von Betriebsparametern bei niedrigen Drehzahlen der Brennkraftmaschine höher eingestellt als bei höheren Drehzahlen. Ein hoher, niedrigen Drehzahlen entsprechender Steuerdruck entspricht am ersten Pumpenkolben (70) einer Verstellung des Förderbeginns in Richtung FRÜH, ein niedriger, hohen Drehzahlen entsprechender Steuerdruck entspricht einer Verstellung des Förderbeginns in Richtung SPÄT. Mit dieser Kopplung wird erreicht, dass einerseits eine Einspritzung bei niedrigen Einspritzdrücken vermieden wird. Gleichzeitig wird die mit der Öffnungsdruckerhöhung verbundene Verschiebung des Einspritzbeginns in Richtung SPÄT durch eine Verstellung des Förderbeginns am Pumpenkolben in Richtung FRÜH ausgeglichen. Grundsätzlich sind aber auch je nach Motorbetriebserfordernissen davon abweichende Regelstrategien möglich.Conveniently, the applied in the control line control pressure is set higher depending on operating parameters at low speeds of the internal combustion engine than at higher speeds. A high, low speeds corresponding Control pressure corresponds to the first pump piston (70) an adjustment of the start of delivery in the direction of EARLY, a low, high rotational speeds corresponding control pressure corresponds to an adjustment of the start of delivery in the direction of LATE. This coupling ensures that, on the one hand, injection at low injection pressures is avoided. At the same time, the shift in the start of injection associated with the opening pressure increase in the direction of LATHE is compensated for by adjusting the delivery start on the pump piston in the direction of EAR. In principle, deviating control strategies are also possible depending on the engine operating requirements.

In weiterer Ausgestaltung gemäß den Unteransprüchen kann eine weitere Steuerleitung vorgesehen sein, mit der die auf die Düsennadel wirkende Schließkraft während der Einspritzung erhöht wird, um den Schließdruck anzuheben. Der notwendige Steuerdruck kann an einer Bohrung abgenommen werden, die im Pumpenzylinder des das Förderende steuernden zweiten Pumpenkolbens der Doppelkolbenpumpe angeordnet ist, um den Absteuerdruck zur Beaufschlagung der Düsennadel in Schließrichtung zu nutzen, bevor der Druckabfall am Förderende die Einspritzdüse erreicht.In a further embodiment according to the dependent claims, a further control line can be provided, with which the force acting on the nozzle needle closing force is increased during injection to raise the closing pressure. The necessary control pressure can be removed at a bore which is arranged in the pump cylinder of the second pump piston controlling the delivery end of the double piston pump to use the Absteuerdruck for acting on the nozzle needle in the closing direction before the pressure drop reaches the injection nozzle at the end.

Gemäß einer weiteren Ausgestaltung sind dem ersten, durch die Steuerstange verdrehbaren Pumpenkolben mit den Steuerbohrungen zusammenwirkende Steuerkanten auf dem Umfang zugeordnet, die mit Stufen ausgebildet sind.According to a further embodiment, the first, by the control rod rotatable pump piston with the control bores cooperating control edges are associated on the circumference, which are formed with steps.

Vorzugsweise sind die Stufen treppenförmig ausgebildet, und die Stufenbreite ist größer als der Durchmesser der Steuerbohrungen angelegt.Preferably, the steps are staircase-shaped, and the step width is greater than the diameter of the control bores applied.

Zweckmäßigerweise erfolgt die Verstellung der Steuerstange (71) in Anpassung auf die stufenförmige Ausbildung der Steuerkante stufenweise.Appropriately, the adjustment of the control rod (71) in adaptation to the step-shaped design of the control edge takes place gradually.

Vorzugsweise ist die Steuerstange (71) zur stufenweisen Verstellung mit stufenweise veränderbarem Steuerdruck beaufschlagbar.Preferably, the control rod (71) for stepwise adjustment with gradually variable control pressure can be acted upon.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden näher beschrieben.An embodiment of the invention is illustrated in the drawing and will be described in more detail below.

Figur 1 zeigt ein Einspritzsystem mit bezüglich des Öffnungs- und Schließdrucks anpassbaren Injektoren, denen jeweils eine Doppelkolbenkraftstoffpumpe zugeordnet ist;Figure 1 shows an injection system with respect to the opening and closing pressure customizable injectors, each associated with a double-piston fuel pump;

Figur 2 zeigt einen Pumpenkolben mit stufenförmiger Steuerkante, wie er zur stufenweise Verstellung des Spritzbeginns bei der Doppelkolbenkraftstoffpumpe Anwendung finden kann.Figure 2 shows a pump piston with stepped control edge, as he can find the stepwise adjustment of the start of injection in the double-piston fuel pump application.

In der Figur 1 ist eine Kraftstoffeinspritzeinrichtung mit zwei Injektoren 5 dargestellt, denen jeweils eine Doppelkolbenpumpe 1 zugeordnet ist. Die Pumpenkolben 70, 73 der Kraftstoffpumpe 1 werden jeweils von einem Nocken angetrieben, der jedoch nicht dargestellt ist. Auf Grund der Fördercharakteristik der Kraftstoffpumpe nimmt der Druck in einer Einspritzleitung 4, die mit der Zulaufleitung 6 eines Injektors 5 verbunden ist, bis zum Erreichen eines Höchstwerts zu, um am Ende dann wieder abzufallen. Die Injektoren 5 sind druckgesteuert, das heißt, dass die Einspritzung durch Beaufschlagung eines Düsenraums 11 mit dem Kraftstoffdruck gesteuert wird, der auf einen Bund der Düsennadel 12 wirkt, der eine Kreisringfläche ist, die zwischen dem dichtenden Sitzdurchmesser und dem Düsennadelführungsdurchmesser liegt. Im Weiteren ist in der Figur eine Steuerleitung 9 dargestellt, die über davon abzweigende erste 7 und zweite 8 Steuerleitungen mit jedem Injektor 5 verbunden ist. Der Steuerdruck wirkt auf Kolben 16 und 17, die Steuerräumen 13 und 14 zugeordnet sind. Der im ersten Steuerraum 13 vor Beginn der Einspritzung anliegende Steuerdruck bewirkt eine Erhöhung des Düsenöffnungsdruck. Vorzugsweise liegt der Steuerdruck über eine Steuerleitung 9 auch an der Steuerstange 71 der Doppelkolbenpumpe 1 an. Der Steuerdruck wird an der Steuerstange 71 dazu benutzt, den Förderbeginn zu verstellen, um die Einspritzbeginnverstellung durch Erhöhung des Düsenöffnungsdrucks zu kompensieren. Um die Steuerstange beispielsweise in Abhängigkeit von Motorbetriebszuständen abweichend von dem in der Steuerleitung 9 herrschenden Druck verstellen zu können, ist es zweckmäßig, die Einstelleinrichtung für die Steuerstange nicht unmittelbar mit dem Steuerdruck in der Steuerleitung 9 zu beaufschlagen, sondern einen separaten hydraulischen oder elektrischen Steuerkreis zu verwenden. Gegebenenfalls kann aus dem Steuerdruck ein Steuersignal abgeleitet, das in eine neue elektrische oder hydraulische Stellgröße umgewandelt wird. Zur Erzeugung geeigneter elektrischer oder hydraulischer Stellgrößen aus dem Steuersignal können beispielweise elektronisch hinterlegte Tabellen verwendet werden.FIG. 1 shows a fuel injection device with two injectors 5, to each of which a double-piston pump 1 is assigned. The pump pistons 70, 73 of the fuel pump 1 are each driven by a cam, which is not shown. Due to the delivery characteristic of the fuel pump, the pressure in an injection line 4, which is connected to the supply line 6 of an injector 5, increases until it reaches a maximum value, and then drops off again at the end. The injectors 5 are pressure-controlled, that is, the injection is controlled by pressurizing a nozzle space 11 with the fuel pressure acting on a collar of the nozzle needle 12, which is a circular ring surface located between the seated sealing diameter and the nozzle needle guide diameter. In the following, a control line 9 is shown in the figure, which branches off from it via the first 7 and second 8 control lines is connected to each injector 5. The control pressure acts on pistons 16 and 17, the control chambers 13 and 14 are assigned. The control pressure applied in the first control chamber 13 before the beginning of the injection causes an increase in the nozzle opening pressure. Preferably, the control pressure via a control line 9 is also applied to the control rod 71 of the double-piston pump 1. The control pressure is used on the control rod 71 to adjust the start of delivery to compensate for the injection start timing by increasing the nozzle opening pressure. In order to adjust the control rod, for example, depending on engine operating conditions deviating from the pressure prevailing in the control line 9 pressure, it is expedient not directly to apply the adjustment for the control rod with the control pressure in the control line 9, but a separate hydraulic or electrical control circuit use. Optionally, derived from the control pressure, a control signal, which is converted into a new electrical or hydraulic control variable. To generate suitable electrical or hydraulic control variables from the control signal, for example, electronically stored tables can be used.

Eine Einrichtung zur Erzeugung des Steuerdrucks besteht beispielsweise aus einem Motorsteuergerät 82, das ein Druckregelventil 83 steuert. Als Steuerfluid kann beispielsweise Motoröl dienen, das von einer Pumpe 80 aus einem Motoröltank 81 entnommen wird.A device for generating the control pressure consists for example of an engine control unit 82 which controls a pressure regulating valve 83. As a control fluid can serve for example engine oil, which is removed from a motor oil tank 81 by a pump 80.

Die Doppelkolbenpumpe 1 ist mit einem ersten 70 und einem zweiten 73 Pumpenkolben mit Pumpenzylindern 72, 75 ausgebildet. Den Pumpenkolben 70, 73 sind Steuerstangen 71 und 77 zugeordnet. Der erste Pumpenkolben 70 wird erfindungsgemäß zum Steuern des Förderbeginns und der zweite Pumpenkolben 73 zum Steuern des Förderendes benutzt. Der geförderte Kraftstoff gelangt über eine Einspritzleitung 4 in den Düsenraum 11 des Injektors 5. Der Förderbeginn des ersten Pumpenkolbens wird zum Beispiel durch den über die Steuerleitung 9, 7 an der Steuerstange 71 anliegenden Druck bei niedriger Drehzahl der Brennkraftmaschine in Richtung FRÜH verstellt und bei höheren Drehzahlen in Richtung SPÄT. Die Verstellung der Steuerstange kann je nach Motorbetriebszustand auch davon abweichende Regelstrategien verlangen. Entsprechend muss die Steuerstange 71 dann mit einer Stelleinrichtung versehen sein, die unabhängig von dem in der Steuerleitung herrschenden Druck ansteuerbar ist. Der zweite Pumpenkolben 73 kann dem ersten Pumpenkolben 70 hinsichtlich des Förderbeginns voreilen, wobei der vom zweiten Pumpenkolben 73 vor dem Förderbeginn des ersten Pumpenkolbens 70 geförderte Kraftstoff über die dem ersten Pumpenkolben 70 zugeordneten Steuerbohrungen abgeführt wird.The double piston pump 1 is formed with a first 70 and a second 73 pump piston with pump cylinders 72, 75. The pump piston 70, 73 are associated with control rods 71 and 77. The first pump piston 70 is used according to the invention for controlling the start of delivery and the second pump piston 73 for controlling the delivery end. The subsidized fuel The delivery start of the first pump piston is, for example, adjusted by the over the control line 9, 7 on the control rod 71 pressure at low speed of the engine in the direction of EARLY and at higher speeds in the direction LATE. The adjustment of the control rod may require deviating control strategies depending on the engine operating condition. Accordingly, the control rod 71 must then be provided with an adjusting device which can be controlled independently of the pressure prevailing in the control line. The second pump piston 73 can lead the first pump piston 70 with regard to the start of delivery, wherein the fuel delivered by the second pump piston 73 before the start of delivery of the first pump piston 70 is discharged via the control bores associated with the first pump piston 70.

Der Injektor kann über den zweiten Steuerraum 14 während einer Einspritzung über die zweite Steuerleitung 8 zusätzlich mit Kraftstoffdruck oder einem anderen Steuerfluid beaufschlagt werden, um den Schließdruck zu erhöhen. Hierzu dient beim dargestellten Injektor 5 ein Ventil 20, das selbsttätig durch den Hub der Düsennadel 12 aufgesteuert wird. Die zweiten Steuerleitungen 8 können von der gemeinsamen Steuerleitung 9 abzweigen oder an eine weitere, nicht dargestellte, von der Steuerleitung 9 separate Steuerleitung angeschlossen sein, die ein anderes Druckniveau besitzt.The injector can be acted upon via the second control chamber 14 during an injection via the second control line 8 additionally with fuel pressure or other control fluid to increase the closing pressure. For this purpose, the illustrated injector 5 is a valve 20 which is automatically controlled by the stroke of the nozzle needle 12. The second control lines 8 can branch off from the common control line 9 or be connected to a further, not shown, separate from the control line 9 control line, which has a different pressure level.

Wie dargestellt kann der Steuerraum 14 auch über eine Steuerleitung 60, die aus Gründen der Übersichtlichkeit nur stückweise dargestellt ist, an eine Bohrung 61 des Pumpenzylinders 75 angeschlossen sein. Die Bohrung ist im Pumpenzylinder 75 so angeordnet, dass der Absteuerdruck in der Steuerleitung 61 anliegt, bevor der Druckabfall am Förderende die Einspritzdüse erreicht. Durch diese Ausbildung kann der Schließdruck zusätzlich erhöht werden. Die Steuerleitung 60 kann jedoch auch die zweiten Steuerleitungen 8 ersetzen und ausschließlich zur Regelung des Schließdrucks dienen.As shown, the control chamber 14 can also be connected to a bore 61 of the pump cylinder 75 via a control line 60, which is shown only in sections for reasons of clarity. The bore is arranged in the pump cylinder 75 so that the Absteuerdruck rests in the control line 61 before the pressure drop at the delivery end of the injection nozzle reached. By this training, the closing pressure can be additionally increased. However, the control line 60 can also replace the second control lines 8 and serve exclusively for regulating the closing pressure.

Der in Figur 2 dargestellte Pumpenkolben 70 mit stufenförmiger Steuerkante 100 kann bei der Doppelkolbenpumpe an Stelle eines Pumpenkolbens mit kontinuierlich verlaufender Steuerkante zur Steuerung des Spritzbeginns verwendet werden. Mit einer Erhöhung der Düsennadelniederhaltekraft wird, wie vorstehend schon beschrieben, der Spritzbeginn unerwünschterweise nach spät verschoben. Zur Kompensation der durch die Schließkraftänderung an der Düsennadel 12 hervorgerufenen Spritzbeginnänderung und zur Einstellung des für den Betriebsbereich optimalen Spritzbeginnzeitpunktes wird mit der Steuerstange 71 die Drehstellung des Pumpenkolbens 70 korrigiert. Die dazu notwendige Verstellung der Steuerstange 71 kann mit beliebigen Mitteln erfolgen, beispielsweise auch mit Hilfe des in der Steuerleitung 9 anliegenden Steuerdrucks, der auf einen Steuerkolben der Steuerstange 71 wirkt, und durch eine Verschiebung der Steuerstange 71 eine Verdrehung des Pumpenkolbens 70 bewirkt. Der Steuerkolben der Steuerstange 71 arbeitet gegen eine mit zunehmendem Stellweg ansteigende Kraft, beispielsweise die Kraft einer Feder, so dass jedem Steuerdruck ein bestimmter Stellweg zugeordnet werden kann, der einer bestimmten Verdrehstellung des Pumpenkolbens 70 entspricht.The pump piston 70 shown in Figure 2 with stepped control edge 100 can be used in the double piston pump instead of a pump piston with a continuously extending control edge to control the start of injection. With an increase in the nozzle needle holding force, as described above, the start of injection is undesirably delayed. To compensate for the change in closing force caused by the closing of the nozzle needle 12, the beginning of the injection change and the setting of the optimum injection starting time for the operating region, the rotational position of the pump piston 70 is corrected by the control rod 71. The necessary adjustment of the control rod 71 can be done by any means, for example, with the help of the applied in the control line 9 control pressure acting on a control piston of the control rod 71, and a displacement of the control piston 71 causes a rotation of the pump piston 70. The control piston of the control rod 71 operates against a rising with increasing travel force, such as the force of a spring, so that each control pressure a certain travel can be assigned, which corresponds to a specific rotational position of the pump piston 70.

Es besteht jedoch die Möglichkeit, dass aufgrund unterschiedlicher Ursachen keine exakte Gleichstellung der Pumpenkolben 70 aller an der gemeinsamen Steuerleitung 9 angeschlossenen Doppelkolbenpumpen 1 erzielbar ist, so dass von Injektor zu Injektor unerwünschte Abweichungen im Spritzbeginn entstehen. Diesem Stellfehler kann dadurch begegnet werden, dass die Steuerkante 100, die mit einer Steueröffnung 101 zusammenwirkt, mit Stufen mit waagerechten Abschnitten ausgeführt ist.However, there is the possibility that due to different causes no exact equalization of the pump piston 70 of all connected to the common control line 9 double piston pumps 1 can be achieved, so that arise from injector to injector unwanted deviations in the beginning of injection. This misalignment can be countered by the fact that the Control edge 100, which cooperates with a control opening 101, is designed with steps with horizontal sections.

Die waagerechten, in Umfangsrichtung verlaufenden und axial zueinander versetzten Abschnitte sind wie die Stufen einer Treppe angeordnet. Der Übergang von einer waagerechten Stufe zur nächsten waagerechten Stufe ist vorzugsweise so ausgebildet, dass mit dem kleinstmöglichen Drehwinkel des Pumpenkolbens 70 die jeweils nächste Stufe erreicht wird. Eine zweckmäßige Ausgestaltung sind Stufen mit waagerechten und ungefähr senkrechten Abschnitten. Senkrecht bedeutet in Richtung der Längsachse des Pumpenkolbens verlaufend.The horizontal, circumferentially extending and axially offset portions are arranged as the steps of a staircase. The transition from one horizontal step to the next horizontal step is preferably designed so that with the smallest possible angle of rotation of the pump piston 70, the respective next step is achieved. An expedient embodiment are steps with horizontal and approximately vertical sections. Vertical means running in the direction of the longitudinal axis of the pump piston.

Besonders vorteilhaft ist diese Stufung der Steuerkante, wenn auch der Steuerdruck in definierten Stufen verändert wird. Innerhalb einer zulässigen Toleranz führt eine Abweichung der Drehstellung des Pumpenkolbens 70 von der Solldrehstellung trotzdem zu gleichem Förderbeginn und damit Spritzbeginn an den verschiedenen Doppelkolbenpumpen 1. Die zulässigen Toleranzabweichungen sind um so größer, je größer die waagrechten Stufenabschnitte im Verhältnis zum Durchmesser der Steueröffnung 101 sind.Particularly advantageous is this gradation of the control edge, although the control pressure is changed in defined stages. Within a permissible tolerance, a deviation of the rotational position of the pump piston 70 from the nominal rotational position nevertheless leads to the same start of delivery and thus injection start at the various double piston pumps 1. The permissible tolerance deviations are the greater, the larger the horizontal step portions are in relation to the diameter of the control port 101.

Der mit der gestuften Steuerkante 100 erzielbare Stellfehlerausgleich ist nicht nur in Verbindung mit der dargestellten Betätigungsart mit Druckbeaufschlagung der Steuerstange 71 vorteilhaft. Vielmehr ist die gestufte Steuerkante 100 auch in Verbindung mit anderen Mitteln zur Betätigung der Steuerstange 71 vorteilhaft einsetzbar.The achievable with the stepped control edge 100 control error compensation is advantageous not only in connection with the illustrated type of actuation with pressurization of the control rod 71. Rather, the stepped control edge 100 is advantageously used in conjunction with other means for actuating the control rod 71.

Claims (13)

  1. Fuel injection device for injecting fuel into the combustion chamber of an internal combustion engine, having at least one dual-piston pump (1) for feeding fuel which is increasing and decreasing in pressure, which dual-piston pump (1) has two pump pistons (70, 73) which feed a common line in parallel and have control edges (100) which interact with control openings (101) in a respectively assigned pump cylinder (72, 75), each pump piston (70, 73) being assigned a control rod (71, 74), by means of which a beginning and an end of feeding can be controlled, and also having an injector (5) assigned to each dual-piston pump (1) with an injection nozzle and with a nozzle needle (12) for controlling the beginning and end of an injection, the nozzle needle (12) being kept in a closed position, in contact with a valve seat, in the intervals between injections by means of a force acting on the nozzle needle (12) in the closing direction, and it being possible for the nozzle needle (12) to be acted on by the fuel fed by the dual-piston pump (1) in order to generate a force which is directed in the opening direction, and an injection beginning when the force directed in the opening direction exceeds the force directed in the closing direction, characterized in that the beginning of feeding can be set at the first pump piston (70) and the end of feeding can be set at the second pump piston (73), the second pump piston (73) leading the first pump piston (70) with regard to the beginning of feeding, and the second pump piston (73) lagging the first pump piston (70) with regard to the end of feeding, the fuel fed by the second pump piston (73) before the beginning of feeding of the first pump piston (70) being discharged via the control openings (101) assigned to the first pump piston (70), and the fuel fed by the first pump piston (70) after the end of feeding of the second pump piston (73) being discharged via the control openings assigned to the second pump piston (73), in that, in addition, first control lines (7) are provided which are connected to first control spaces (13) of all injectors (5) and provide a control pressure which makes it possible for pistons (16), which are assigned to the control spaces (13) and act on the nozzle needle (12) in the closing direction, to be acted on with pressure in order to variably set the force acting on the nozzle needle (12) in the closing direction before the beginning of an injection as a function of engine operating parameters, and in that, in order to compensate for the resulting change in the beginning of injection, the control rod (71) of the first pump piston (70) which regulates the beginning of feeding is adjusted.
  2. Fuel injection device according to Claim 1, characterized in that the control rod (71) is adjusted as a function of the pressure prevailing in the control lines (7).
  3. Fuel injection device according to Claim 2, characterized in that to set the control rod (71), the control pressure present in the control lines (7) acts on a control piston of the control rod (71).
  4. Fuel injection device according to Claim 2 or 3, characterized in that the control pressure present in the control lines (7) can be set to higher values at low speeds than at high speeds as a function of operating parameters of the internal combustion engine, and in that a high control pressure corresponds to an adjustment of the control rod (71), which regulates the beginning of feeding, in the early direction, and in that a low control pressure corresponds to an adjustment of the control rod (71), which regulates the beginning of feeding, in the late direction.
  5. Fuel injection device according to one of Claims 1 to 4, characterized in that second control lines (8 or 60) are provided which provide a second control pressure which makes it possible for pistons (17), which are assigned to second control spaces (14) and act on the nozzle needle (12) in the closing direction, to be acted on with pressure in order to variably set the force acting on the nozzle needle (12) in the closing direction as a function of engine operating parameters after the beginning and before the end of an injection.
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that the first control lines (7) branch off from a control line (9) which is common to at least two injectors.
  7. Fuel injection device according to Claim 6, characterized in that, where present, the second control lines (8) branch off from the common control line (9).
  8. Fuel injection device according to Claim 5, characterized in that the second control line (60) is connected to a bore (61) of the pump cylinder (75) of the second pump piston (73), which regulates the end of feeding, the bore (61) being arranged in such a way that the terminating pressure is present in the control line (60) before the pressure drop reaches the nozzle space (11) of the injection nozzle at the end of feeding.
  9. Fuel injection device according to one of Claims 1 to 8, characterized in that control edges (100) which interact with the control openings (101) are assigned to the first pump piston (70) at the circumference, in that the first pump piston (70) can be rotated by means of the control rod (71) in order to control the beginning of feeding, and in that the control edges (100) are formed with steps having horizontal sections.
  10. Fuel injection device according to Claim 9, characterized in that the steps are formed in the manner of stairs with approximately perpendicular transitions.
  11. Fuel injection device according to Claim 9 or 10, characterized in that the horizontal step sections are larger than the diameter of the control openings (101).
  12. Fuel injection device according to Claim 9, 10 or 11, characterized in that the control rod (71) is adjusted in a stepped fashion in accordance with the design of the control edge (100).
  13. Fuel injection device according to Claim 12, characterized in that the control rod (71) can, for stepped adjustment, be acted on with a control pressure which can be varied in a stepped fashion.
EP04712002A 2003-02-20 2004-02-18 Fuel injection device Expired - Lifetime EP1597474B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10307398 2003-02-20
DE10307398 2003-02-20
DE10319623A DE10319623A1 (en) 2003-02-20 2003-05-02 Fuel injection system
DE10319623 2003-05-02
PCT/EP2004/001509 WO2004074675A1 (en) 2003-02-20 2004-02-18 Fuel injection device

Publications (2)

Publication Number Publication Date
EP1597474A1 EP1597474A1 (en) 2005-11-23
EP1597474B1 true EP1597474B1 (en) 2006-06-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04712002A Expired - Lifetime EP1597474B1 (en) 2003-02-20 2004-02-18 Fuel injection device

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Country Link
EP (1) EP1597474B1 (en)
JP (1) JP4142688B2 (en)
KR (1) KR100705854B1 (en)
AT (1) ATE331135T1 (en)
DE (1) DE502004000835D1 (en)
WO (1) WO2004074675A1 (en)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1253180A (en) * 1960-04-06 1961-02-03 Maschf Augsburg Nuernberg Ag Fuel injection pump
DE1526711A1 (en) * 1966-01-29 1969-12-04 Maschf Augsburg Nuernberg Ag Fuel injection pump for large quantities in internal combustion engines
US3976249A (en) * 1973-05-12 1976-08-24 C.A.V. Limited Fuel injection systems for internal combustion engines
DE2558790A1 (en) * 1975-12-24 1977-07-14 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR COMBUSTION MACHINES
DE2801976A1 (en) 1978-01-18 1979-07-19 Bosch Gmbh Robert FUEL INJECTION SYSTEM
US4327694A (en) * 1979-11-01 1982-05-04 Caterpillar Tractor Co. Unit fuel pump-injector with overfuel capability and timing retardation
JPS57102527A (en) * 1980-12-15 1982-06-25 Diesel Kiki Co Ltd Fuel injection nozzle unit
US5201295A (en) * 1986-07-30 1993-04-13 Ail Corporation High pressure fuel injection system
JPH05201295A (en) * 1992-01-29 1993-08-10 Yazaki Corp Connector for automotive door

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DE502004000835D1 (en) 2006-08-03
KR20050107585A (en) 2005-11-14
KR100705854B1 (en) 2007-04-09
JP4142688B2 (en) 2008-09-03
EP1597474A1 (en) 2005-11-23
ATE331135T1 (en) 2006-07-15
JP2006515399A (en) 2006-05-25
WO2004074675A1 (en) 2004-09-02

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