EP1727977B1 - Fuel-injection valve - Google Patents

Fuel-injection valve Download PDF

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Publication number
EP1727977B1
EP1727977B1 EP05701507A EP05701507A EP1727977B1 EP 1727977 B1 EP1727977 B1 EP 1727977B1 EP 05701507 A EP05701507 A EP 05701507A EP 05701507 A EP05701507 A EP 05701507A EP 1727977 B1 EP1727977 B1 EP 1727977B1
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EP
European Patent Office
Prior art keywords
nozzle needle
fuel
pressure
valve
throttle
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.)
Not-in-force
Application number
EP05701507A
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German (de)
French (fr)
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EP1727977A1 (en
Inventor
Wolfgang Stoecklein
Peter Boehland
Godehard Nentwig
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1727977A1 publication Critical patent/EP1727977A1/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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators

Definitions

  • the invention is based on a fuel injection valve of an internal combustion engine according to the closer defined in the preamble of claim 1. Art.
  • Such a fuel injection valve is out of DE 102 05 970 A1 known and used for injection of fuel under high pressure in a combustion chamber of a motor vehicle internal combustion engine.
  • A1 known fuel injection valve comprises a housing with a nozzle module and a valve control module.
  • the valve control module is designed like a valve and can be actuated by means of an actuator acting on a valve closure member.
  • a pressure level in a valve control chamber is adjustable, which adjoins a needle unit of the nozzle module.
  • the needle unit comprises an outer nozzle needle, which is biased by a compression spring in the closing direction and is guided on the housing. In the outer nozzle needle, an inner nozzle needle is guided.
  • the inner nozzle needle is used to control a Injection of fuel via inner injection openings and the outer nozzle needle is used to control an injection via outer injection openings, wherein in a triggered by the valve control module pressure drop in the valve control chamber first the outer nozzle needle and subsequently the inner nozzle needle are moved in the open position. In a subsequent, triggered by the valve control module pressure increase in the valve control chamber, the two nozzle needles are moved simultaneously in the closed position.
  • the US 5,899,389 shows a fuel injection valve with - two coaxial successively guided valve needles.
  • the valve needles are either each acted upon by a spring and then open according to the fuel pressure is supplied to the injection valve for injection or the corresponding closing force on the valve needle is generated by the fuel pressure in a common control chamber, which determines the level of pressure in the control chamber, the pressure level can be, in which the inner and the outer valve needle opens.
  • a fuel injection valve which also has two nested valve needles.
  • the valve needles are pressed by the pressure in each one control chamber against a valve seat, wherein near the valve seat a transverse bore in the outer valve needle is formed, via which the fuel is introduced into the formed between the inner and the outer valve needle space.
  • the fuel injection valve according to the invention with the features according to the preamble of claim 1 and an outer nozzle needle with at least one transverse channel through which fuel to the periphery and to an inner pressure stage of the inner nozzle needle is feasible, offers the possibility of opening the needle unit first, the inner nozzle needle and then open the outer nozzle needle.
  • By appropriate design of the pressure levels of the inner and outer nozzle needle then optimized opening and closing speeds of the two nozzle needles can be achieved.
  • the outer nozzle needle is preferably guided in a sleeve disposed in the high-pressure space connected to the fuel supply passage, a leak-free fuel injection valve having two nozzle needles inserted into each other can be realized.
  • the fuel injection valve according to the invention may in particular be part of a common-rail injection system and serve for the injection of fuel under high pressure into a combustion chamber of a diesel internal combustion engine of a motor vehicle.
  • the fuel injection valve is connected on the inlet side to a high-pressure accumulator, the so-called common rail, which supplies all the fuel injection valves of the relevant internal combustion engine with high-pressure fuel.
  • the transverse channel of the outer nozzle needle may be provided with a throttle.
  • the inner nozzle needle In order to hold the inner nozzle needle in the closed position, it is expediently biased by a closing spring in the closing direction.
  • the closing spring is supported for example on an intermediate plate of a housing of the fuel injection valve.
  • the outer nozzle needle expediently biased by a further closing spring in the closing direction.
  • a driver is advantageously formed on the inner nozzle needle, which acts on the outer nozzle needle.
  • the driver is formed for example by the inner pressure stage.
  • the inner nozzle needle can be designed so that it acts in the open state as a throttle for a fuel flow into the valve control chamber and thus accelerates a lowering of the pressure level in the valve control chamber and thus the opening of the outer nozzle needle.
  • a fuel throttle is arranged in the fuel supply channel of the injection valve.
  • a fuel injection valve 10 is shown, which is part of a so-called common-rail injection system and for injecting fuel into a combustion chamber of a diesel internal combustion engine of a motor vehicle.
  • the fuel injection valve 10 includes, as essential components, a valve-type valve control module 12 and a nozzle module 14. Between the nozzle module 14 and the valve control module 12, a throttle plate 16 is arranged.
  • the nozzle module 14 is designed as a so-called coaxial vario nozzle and has a needle unit 18, which is arranged in a high-pressure chamber 20 of a nozzle housing 22 and an outer nozzle needle 24 and an inner nozzle needle 26 comprises.
  • the outer nozzle needle 24 is in one in the high pressure space 20 arranged, cylindrical sleeve 28 and is used to control the outer, leading to the combustion chamber of the internal combustion engine spray holes or injection ports 32.
  • the inner nozzle needle 26 is guided over a region 54 of increased diameter in the outer nozzle needle 24 and is used to control internal, also to the combustion chamber of the internal combustion engine leading spray holes or injection openings 34.
  • the inner injection holes 34 each have a smaller cross-section than the outer injection holes 32nd
  • the two nozzle needles 24 and 26 border with their spray ports 32 and 34 facing away from end faces to a valve control chamber 36 which is bounded radially from the cylindrical sleeve 28 and on the nozzle needles 24 and 26 side facing away from the throttle plate 16.
  • a valve control chamber 36 which is bounded radially from the cylindrical sleeve 28 and on the nozzle needles 24 and 26 side facing away from the throttle plate 16.
  • the position of the two nozzle needles 24 and 26 is adjustable.
  • first closing spring 38 which is supported on the sleeve 28 and engages a support 40 of the outer nozzle needle 24, biased in the closing direction.
  • the inner nozzle needle 26 is biased in the closing direction by means of a second closing spring 42, which is supported on the throttle plate 16 and acts on a bearing 44 formed by the enlarged diameter portion 54 of the inner nozzle needle 26.
  • the outer nozzle needle 24 further has a transverse channel 46, which has the high-pressure chamber 20 with an annular gap 48 between the outer nozzle needle 24 and the circumference of the inner nozzle needle 26 and with an inner pressure stage 50 of the inner nozzle needle 26 connects.
  • the pressure stage 50 is formed by the enlarged diameter portion 54 of the inner nozzle needle 26.
  • a throttle 52 is formed in the transverse channel 46.
  • the throttle plate 16 has a fuel throttle 60, which is assigned to the one leading to the high-pressure chamber 20 fuel supply channel 62, disposed between the fuel supply channel 62 and the valve control chamber 36, so-called inlet throttle 64, one between the valve control chamber 36 and a valve chamber 66 of the nozzle module 12th arranged, so-called outlet throttle 68 and a bypass channel 70 which is connected via a channel 72 to the fuel supply channel 62 and also leads to the valve control chamber 66.
  • a fuel throttle 60 which is assigned to the one leading to the high-pressure chamber 20 fuel supply channel 62, disposed between the fuel supply channel 62 and the valve control chamber 36, so-called inlet throttle 64, one between the valve control chamber 36 and a valve chamber 66 of the nozzle module 12th arranged, so-called outlet throttle 68 and a bypass channel 70 which is connected via a channel 72 to the fuel supply channel 62 and also leads to the valve control chamber 66.
  • the inlet throttle 64 is arranged centrally in the throttle plate 16, whereas the outlet throttle 68 is arranged eccentrically.
  • valve closure member 74 is arranged, which by means of a not shown here, preferably piezoelectric actuator is controllable.
  • the valve closure member 74 is biased by a biasing spring 76 in the closing direction.
  • An inflow of fuel to the spray holes 34 takes place from the fuel supply channel 62 via the fuel throttle 60, past the sleeve 28 in the high-pressure chamber 20 and then through the transverse channel 46 and the throttle 52 to the outside of the inner nozzle needle 26 and from there at open inner nozzle needle 26 to the spray holes 34th
  • the inner nozzle needle 26 and the outer nozzle needle 24 are held by the respective associated closing spring 42 and 38 and by the hydraulic pressure ratios when not driven piezoelectric actuator in the closed position.
  • the pressure surfaces of the inner nozzle needle 26 and the outer nozzle needle 24, ie, the spray holes 32 and 34 facing away from the two nozzle needles 24 and 26 and the inner pressure stage 50 of the inner nozzle needle 26 and the outer pressure stage 58 of the outer nozzle needle 24 are tuned so that the prevailing in the valve control chamber 36 opening pressure for the inner nozzle needle 26 is greater than that prevailing in the valve control chamber 36 opening pressure for the outer nozzle needle 24, which is based FIG. 2 is shown by way of example.
  • FIG. 2 shows a broken line for the inner nozzle needle 26 and a solid curve for the outer nozzle needle 24 an opening pressure p, which must prevail for opening the inner nozzle needle 26 and the outer nozzle needle 24 in the valve control chamber 36, wherein the opening pressure p as a function of the diameter D of inner nozzle needle 26 is shown.
  • the inner nozzle needle 26 has a seat diameter of 1.3 mm
  • the outer nozzle needle 24 has a seat diameter of 1.8 mm
  • the outer needle has a diameter of 4 mm
  • a rail pressure of 1 kbar is provided and in the relevant Combustion chamber a pressure of 50 bar prevails.
  • the inner nozzle needle 26 must have a diameter greater than 2.45 mm to allow the inner nozzle needle 26 to open in front of the outer nozzle needle 24. This means that only from this diameter D of the inner nozzle needle 26, the opening pressure of the inner nozzle needle 26 is greater than the opening pressure of the outer nozzle needle 24th
  • FIG. 3 1 shows a simulation of a stroke H for an inner nozzle needle based on a curve X and a stroke H for an outer nozzle needle on the basis of a curve Y in each case as a function of a driving time of the piezoelectric actuator for a fuel injection valve of the type shown in FIG.
  • FIG. 3 As shown, it can be seen that the inner nozzle needle opens earlier than the outer nozzle needle, so that fuel can be injected into the combustion chamber of the internal combustion engine in a stepped manner via the respective associated injection holes 32 and 34.
  • the piezoelectric actuator In the initial state, the piezoelectric actuator is in a de-energized state, so that the valve closing member 74 is in the closed position and in the valve control chamber 36 rail pressure prevails.
  • the valve closing member 74 Upon actuation of the piezoelectric actuator, the valve closing member 74 is moved in the open position, so that the fluid pressure in the valve control chamber 36 is lowered via the outlet throttle 68.
  • the fluid pressure prevailing in the valve control chamber 36 has dropped to the opening pressure required to open the inner nozzle needle 26, the latter opens.
  • the total stroke of the inner nozzle needle 26 is for example 0.2 mm, wherein the throttle plate 16 forms a stop.
  • the inner nozzle needle strikes against the throttle plate 18, whereupon the inner nozzle needle 26 largely throttles the supply of fuel via the inlet throttle 64 into the valve control chamber 36. This causes the pressure in the valve control chamber 36 to further decrease, so that the opening pressure required to open the outer nozzle needle 24 is exceeded.
  • This also opens the outer nozzle needle 24, so that fuel is injected via the outer injection holes 32 into the combustion chamber of the internal combustion engine.
  • valve closing member 74 When an injection of fuel into the combustion chamber is to be terminated, the valve closing member 74 is moved by the piezoelectric actuator in the closed position, so that the pressure in the valve control chamber 36 increases again to the rail pressure. At this time, the one in the High pressure chamber 20 prevailing pressure due to the throttling means of the fuel throttle 60 is less than the rail pressure. Due to the different pressure levels in the valve chamber 36 and the high-pressure chamber 20, a closing force is exerted on both needles. Characterized in that the pressure stage 50 acts as a driver, close the inner nozzle needle 26 and the outer nozzle needle 24 substantially simultaneously.
  • the piezoelectric actuator is moved to an intermediate position, whereby due to the effect of flowing over the bypass channel into the valve chamber 66 fuel, the pressure in the valve control chamber 36 does not drop so far that the outer nozzle needle 24th opens. Also, an opening of the outer nozzle needle 24 can be prevented by a Mehrfachbestromung the piezoelectric actuator.

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

Abstract

The invention relates to a fuel-injection valve comprising a nozzle module (12). An outer nozzle needle (24), which co-operates with a first injection orifice (32) and is surrounded by a high-pressure chamber (20) that is connected to a fuel-supply channel (62) and an inner nozzle needle (26), which co-operates with at least one second injection orifice (34) and is guided in a channel that axially penetrates the outer nozzle needle (24), are configured in said module to be axially displaced. The fuel-injection valve also comprises a valve-type valve control module (12), which controls the fluid pressure prevailing in a valve control chamber (36) that is equipped with an input throttle (64) and an output throttle (68). The level of the fluid pressure defines the position of the outer nozzle needle (24) and the inner nozzle needle (26). The outer nozzle needle (24) has at least one transverse channel (46), via which fuel can be conducted from the high-pressure chamber (20) to the periphery and the inner pressure stage (50) of the inner nozzle needle (26).

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil einer Brennkraftmaschine gemäß der im Oberbegriff des Patentanspruches 1 näher definierten Art aus.The invention is based on a fuel injection valve of an internal combustion engine according to the closer defined in the preamble of claim 1. Art.

Ein derartiges Kraftstoffeinspritzventil ist aus der DE 102 05 970 A1 bekannt und dient zur Einspritzung von unter Hochdruck stehendem Kraftstoff in einen Brennraum einer Kraftfahrzeugbrennkraftmaschine.Such a fuel injection valve is out of DE 102 05 970 A1 known and used for injection of fuel under high pressure in a combustion chamber of a motor vehicle internal combustion engine.

Das aus der DE 102 05 970 A1 bekannte Kraftstoffeinspritzventil umfasst ein Gehäuse mit einem Düsenmodul und einem Ventilsteuermodul. Das Ventilsteuermodul ist ventilartig ausgebildet und mittels eines auf ein Ventilschließglied wirkenden Aktuators betätigbar. In Abhängigkeit von der Schaltstellung des Ventilschließglieds ist ein Druckniveau in einem Ventilsteuerraum einstellbar, der an eine Nadeleinheit des Düsenmoduls grenzt. Die Nadeleinheit umfasst eine äußere Düsennadel, die mittels einer Druckfeder in Schließrichtung vorgespannt ist und an dem Gehäuse geführt ist. In der äußeren Düsennadel ist eine innere Düsennadel geführt. Die innere Düsennadel dient zur Steuerung einer Einspritzung von Kraftstoff über innere Einspritzöffnungen und die äußere Düsennadel dient zur Steuerung einer Einspritzung über äußere Einspritzöffnungen, wobei bei einer mittels des Ventilsteuermoduls ausgelösten Druckabsenkung in dem Ventilsteuerraum zunächst die äußere Düsennadel und nachfolgend die innere Düsennadel in Öffnungsstellung verfahren werden. Bei einem nachfolgenden, mittels des Ventilsteuermoduls ausgelösten Druckanstieg in dem Ventilsteuerraum werden die beiden Düsennadeln gleichzeitig in Schließstellung verfahren.That from the DE 102 05 970 A1 known fuel injection valve comprises a housing with a nozzle module and a valve control module. The valve control module is designed like a valve and can be actuated by means of an actuator acting on a valve closure member. Depending on the switching position of the valve closure member, a pressure level in a valve control chamber is adjustable, which adjoins a needle unit of the nozzle module. The needle unit comprises an outer nozzle needle, which is biased by a compression spring in the closing direction and is guided on the housing. In the outer nozzle needle, an inner nozzle needle is guided. The inner nozzle needle is used to control a Injection of fuel via inner injection openings and the outer nozzle needle is used to control an injection via outer injection openings, wherein in a triggered by the valve control module pressure drop in the valve control chamber first the outer nozzle needle and subsequently the inner nozzle needle are moved in the open position. In a subsequent, triggered by the valve control module pressure increase in the valve control chamber, the two nozzle needles are moved simultaneously in the closed position.

Die US 5 899 389 zeigt ein Kraftstoffeinspritzventil mit - zwei koaxial hintereinander geführten Ventilnadeln. Die Ventilnadeln werden entweder jeweils von einer Feder beaufschlagt und öffnen dann entsprechend dem Kraftstoffdruck der dem Einspritzventil zur Einspritzung zugeführt wird oder die entsprechende Schließkraft auf die Ventilnadel wird durch den Kraftstoffdruck in einem gemeinsamen Steuerraum erzeugt, wobei über die Höhe des Drucks im Steuerraum das Druckniveau bestimmt werden kann, bei dem die innere bzw. die äußere Ventilnadel öffnet.The US 5,899,389 shows a fuel injection valve with - two coaxial successively guided valve needles. The valve needles are either each acted upon by a spring and then open according to the fuel pressure is supplied to the injection valve for injection or the corresponding closing force on the valve needle is generated by the fuel pressure in a common control chamber, which determines the level of pressure in the control chamber, the pressure level can be, in which the inner and the outer valve needle opens.

Aus der US 2003/0038185 A1 ist darüber hinaus ein Kraftstoffeinspritzventil bekannt, das ebenfalls zwei ineinander geführte Ventilnadeln aufweist. Die Ventilnadeln werden durch den Druck in jeweils einem Steuerraum gegen einen Ventilsitz gedrückt, wobei nahe dem Ventilsitz eine Querbohrung in der äußeren Ventilnadel ausgebildet ist, über die der Kraftstoff in den zwischen der inneren und der äußeren Ventilnadel ausgebildeten Raum eingeleitet wird.From the US 2003/0038185 A1 In addition, a fuel injection valve is known, which also has two nested valve needles. The valve needles are pressed by the pressure in each one control chamber against a valve seat, wherein near the valve seat a transverse bore in the outer valve needle is formed, via which the fuel is introduced into the formed between the inner and the outer valve needle space.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen nach dem Oberbegriff des Patentanspruches 1 und einer äußeren Düsennadel mit mindestens einem Querkanal, über den Kraftstoff an den Umfang und an eine innere Druckstufe der inneren Düsennadel führbar ist, bietet die Möglichkeit, beim Öffnen der Nadeleinheit zunächst die innere Düsennadel und anschließend die äußere Düsennadel zu öffnen. Durch entsprechende Ausbildung der Druckstufen der inneren und der äußeren Düsennadel können dann optimierte Öffnungs- und Schließgeschwindigkeiten der beiden Düsennadeln erzielt werden. Ferner kann durch dieses Konzept, bei dem die äußere Düsennadel vorzugsweise in einer Hülse geführt ist, die in dem mit dem Kraftstoffzufuhrkanal verbundenen Hochdruckraum angeordnet ist, ein leckagefreies Kraftstoffeinspritzventil mit zwei ineinander geführten Düsennadeln realisiert werden.The fuel injection valve according to the invention with the features according to the preamble of claim 1 and an outer nozzle needle with at least one transverse channel through which fuel to the periphery and to an inner pressure stage of the inner nozzle needle is feasible, offers the possibility of opening the needle unit first, the inner nozzle needle and then open the outer nozzle needle. By appropriate design of the pressure levels of the inner and outer nozzle needle then optimized opening and closing speeds of the two nozzle needles can be achieved. Further, by this concept in which the outer nozzle needle is preferably guided in a sleeve disposed in the high-pressure space connected to the fuel supply passage, a leak-free fuel injection valve having two nozzle needles inserted into each other can be realized.

Das Kraftstoffeinspritzventil nach der Erfindung kann insbesondere Bestandteil eines Common-Rail-Einspritzsystems sein und zur Einspritzung von unter einem Hochdruck stehenden Kraftstoff in einen Brennraum einer Dieselbrennkraftmaschine eines Kraftfahrzeuges dienen. In diesem Falle ist das Kraftstoffeinspritzventil zulaufseitig mit einem Hochdruckspeicher, der so genannten Common-Rail, verbunden, welcher sämtliche Kraftstoffeinspritzventile der betreffenden Brennkraftmaschine mit unter Hochdruck stehendem Kraftstoff versorgt.The fuel injection valve according to the invention may in particular be part of a common-rail injection system and serve for the injection of fuel under high pressure into a combustion chamber of a diesel internal combustion engine of a motor vehicle. In this case, the fuel injection valve is connected on the inlet side to a high-pressure accumulator, the so-called common rail, which supplies all the fuel injection valves of the relevant internal combustion engine with high-pressure fuel.

Die getrennte Ansteuerung zweier Reihen von Einspritzöffnungen bzw. Spritzlöchern führt dazu, dass jeweils eine gewisse Anzahl von Spritzlöchern freigegeben und dadurch auch bei kleinen Einspritzmengen ausreichend lange Einspritzdauern bei guter Zerstäubungsqualität gewährleistet werden können. Bei großen Einspritzmengen müssen aber auch keine übermäßig langen Einspritzdauern oder übermäßig hohe Einspritzdrücke in Kauf genommen werden.The separate control of two rows of injection openings or spray holes causes each release a certain number of spray holes and thus can be ensured with good atomization quality even with small injection quantities sufficiently long injection periods. For large injection quantities, however, no excessively long injection periods or excessively high injection pressures must be accepted.

Zur präzisen Abstimmung eines auf die innere Druckstufe der inneren Düsennadel wirkenden Kraftstoffdrucks kann der Querkanal der äußeren Düsennadel mit einer Drossel versehen sein.For precise tuning of an acting on the inner pressure stage of the inner nozzle needle fuel pressure, the transverse channel of the outer nozzle needle may be provided with a throttle.

Um die innere Düsennadel in Schließstellung halten zu können, ist sie zweckmäßigerweise mittels einer Schließfeder in Schließrichtung vorgespannt. Die Schließfeder stützt sich beispielsweise an einer Zwischenplatte eines Gehäuses des Kraftstoffeinspritzventils ab. Entsprechend ist auch die äußere Düsennadel zweckmäßigerweise mittels einer weiteren Schließfeder in Schließrichtung vorgespannt.In order to hold the inner nozzle needle in the closed position, it is expediently biased by a closing spring in the closing direction. The closing spring is supported for example on an intermediate plate of a housing of the fuel injection valve. Corresponding is also the outer nozzle needle expediently biased by a further closing spring in the closing direction.

Um bei einer Unterbrechung eines Einspritzvorganges ein im Wesentlichen gleichzeitiges Schließen der beiden Düsennadeln zu erreichen, ist an der inneren Düsennadel vorteilhafterweise ein Mitnehmer ausgebildet, der auf die äußere Düsennadel wirkt. Der Mitnehmer ist beispielsweise von der inneren Druckstufe gebildet.In order to achieve a substantially simultaneous closing of the two nozzle needles at an interruption of an injection process, a driver is advantageously formed on the inner nozzle needle, which acts on the outer nozzle needle. The driver is formed for example by the inner pressure stage.

Des Weiteren kann die innere Düsennadel so ausgebildet sein, dass sie im geöffneten Zustand als Drossel für einen Kraftstoffzufluss in den Ventilsteuerraum wirkt und so ein Absenken des Druckniveaus in dem Ventilsteuerraum und damit das Öffnen der äußeren Düsennadel beschleunigt.Furthermore, the inner nozzle needle can be designed so that it acts in the open state as a throttle for a fuel flow into the valve control chamber and thus accelerates a lowering of the pressure level in the valve control chamber and thus the opening of the outer nozzle needle.

Zur weiteren Optimierung der Öffnungs- und Schließgeschwindigkeiten der beiden Düsennadeln ist es vorteilhaft, wenn in dem Kraftstoffzufuhrkanal des Einspritzventils eine Kraftstoffdrossel angeordnet ist.To further optimize the opening and closing speeds of the two nozzle needles, it is advantageous if a fuel throttle is arranged in the fuel supply channel of the injection valve.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes nach der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the article according to the invention are the description, the drawings and the claims removed.

Zeichnungdrawing

Ein Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils ist in der Zeichnung schematisch vereinfacht dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen

  • Figur 1 einen ausschnittsweisen, schematischen Längsschnitt durch ein Kraftstoffeinspritzventil mit einer inneren und einer äußeren Düsennadel;
  • Figur 2 ein Diagramm, das beispeilhaft einen Öffnungsdruck der inneren Düsennadel und der äußeren Düsennadel in Abhängigkeit von dem Durchmesser der inneren Düsennadel darstellt; und
  • Figur 3 ein Diagramm, das einen Nadelhub der inneren und der äußeren Düsennadel in Abhängigkeit von einer Ansteuerzeit zeigt.
An embodiment of a fuel injection valve according to the invention is schematically simplified in the drawing and will be explained in more detail in the following description. Show it
  • FIG. 1 a fragmentary, schematic longitudinal section through a fuel injection valve having an inner and an outer nozzle needle;
  • FIG. 2 a diagram illustrating an opening pressure of the inner nozzle needle and the outer nozzle needle depending on the diameter of the inner nozzle needle; and
  • FIG. 3 a diagram showing a needle stroke of the inner and outer nozzle needle in response to a drive time.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Kraftstoffeinspritzventil 10 dargestellt, das Bestandteil eines so genannten Common-Rail-Einspritzsystems ist und zur Einspritzung von Kraftstoff in einen Brennraum einer Dieselbrennkraftmaschine eines Kraftfahrzeuges dient. Das Kraftstoffeinspritzventil 10 umfasst als wesentliche Baueinheiten ein ventilartig ausgebildetes Ventilsteuermodul 12 und ein Düsenmodul 14. Zwischen dem Düsenmodul 14 und dem Ventilsteuermodul 12 ist eine Drosselplatte 16 angeordnet.In FIG. 1 a fuel injection valve 10 is shown, which is part of a so-called common-rail injection system and for injecting fuel into a combustion chamber of a diesel internal combustion engine of a motor vehicle. The fuel injection valve 10 includes, as essential components, a valve-type valve control module 12 and a nozzle module 14. Between the nozzle module 14 and the valve control module 12, a throttle plate 16 is arranged.

Das Düsenmodul 14 ist als so genannte Koaxial-Vario-Düse ausgebildet und weist eine Nadeleinheit 18 auf, die in einem Hochdruckraum 20 eines Düsengehäuses 22 angeordnet ist und eine äußere Düsennadel 24 und eine innere Düsennadel 26 umfasst. Die äußere Düsennadel 24 ist in einer in dem Hochdruckraum 20 angeordneten, zylindrischen Hülse 28 geführt und dient zur Steuerung von äußeren, zu dem Brennraum der Brennkraftmaschine führenden Spritzlöchern bzw. Einspritzöffnungen 32. Die innere Düsennadel 26 ist über einen Bereich 54 vergrößerten Durchmessers in der äußeren Düsennadel 24 geführt und dient zur Steuerung von inneren, ebenfalls zu dem Brennraum der Brennkraftmaschine führenden Spritzlöchern bzw. Einspritzöffnungen 34. Die inneren Spritzlöcher 34 haben jeweils einen geringeren Querschnitt als die äußeren Spritzlöcher 32.The nozzle module 14 is designed as a so-called coaxial vario nozzle and has a needle unit 18, which is arranged in a high-pressure chamber 20 of a nozzle housing 22 and an outer nozzle needle 24 and an inner nozzle needle 26 comprises. The outer nozzle needle 24 is in one in the high pressure space 20 arranged, cylindrical sleeve 28 and is used to control the outer, leading to the combustion chamber of the internal combustion engine spray holes or injection ports 32. The inner nozzle needle 26 is guided over a region 54 of increased diameter in the outer nozzle needle 24 and is used to control internal, also to the combustion chamber of the internal combustion engine leading spray holes or injection openings 34. The inner injection holes 34 each have a smaller cross-section than the outer injection holes 32nd

Die beiden Düsennadeln 24 und 26 grenzen mit ihren den Spritzlöchern 32 und 34 abgewandten Stirnseiten an einen Ventilsteuerraum 36, der radial von der zylindrischen Hülse 28 und an der den Düsennadeln 24 und 26 abgewandten Seite von der Drosselplatte 16 begrenzt ist. Über den in dem Ventilsteuerraum 36 herrschenden Fluiddruck ist die Lage der beiden Düsennadeln 24 und 26 einstellbar.The two nozzle needles 24 and 26 border with their spray ports 32 and 34 facing away from end faces to a valve control chamber 36 which is bounded radially from the cylindrical sleeve 28 and on the nozzle needles 24 and 26 side facing away from the throttle plate 16. About the prevailing in the valve control chamber 36 fluid pressure, the position of the two nozzle needles 24 and 26 is adjustable.

Des Weiteren ist die äußere Düsennadel 24 mittels einer ersten Schließfeder 38, die sich an der Hülse 28 abstützt und an einem Auflager 40 der äußeren Düsennadel 24 angreift, in Schließrichtung vorgespannt. Die innere Düsennadel 26 ist mittels einer zweiten Schließfeder 42, die sich an der Drosselplatte 16 abstützt und an einem von dem Bereich 54 vergrößerten Durchmessers gebildeten Auflager 44 der inneren Düsennadel 26 angreift, in Schließrichtung vorgespannt.Furthermore, the outer nozzle needle 24 by means of a first closing spring 38, which is supported on the sleeve 28 and engages a support 40 of the outer nozzle needle 24, biased in the closing direction. The inner nozzle needle 26 is biased in the closing direction by means of a second closing spring 42, which is supported on the throttle plate 16 and acts on a bearing 44 formed by the enlarged diameter portion 54 of the inner nozzle needle 26.

Die äußere Düsennadel 24 weist des Weiteren einen Querkanal 46 auf, der den Hochdruckraum 20 mit einem Ringspalt 48 zwischen der äußeren Düsennadel 24 und dem Umfang der inneren Düsennadel 26 sowie mit einer inneren Druckstufe 50 der inneren Düsennadel 26 verbindet. Die Druckstufe 50 ist von dem Bereich 54 vergrößerten Durchmessers der inneren Düsennadel 26 gebildet. In dem Querkanal 46 ist eine Drossel 52 ausgebildet.The outer nozzle needle 24 further has a transverse channel 46, which has the high-pressure chamber 20 with an annular gap 48 between the outer nozzle needle 24 and the circumference of the inner nozzle needle 26 and with an inner pressure stage 50 of the inner nozzle needle 26 connects. The pressure stage 50 is formed by the enlarged diameter portion 54 of the inner nozzle needle 26. In the transverse channel 46, a throttle 52 is formed.

Ferner weist die äußere Düsennadel 24 an ihrer dem Ventilsteuerraum 36 abgewandten Stirnseite einen Doppelsitz 56 auf, mittels dessen die äußeren Spritzlöcher 32 verschließbar sind. An dieser Seite ist die äußere Düsennadel 24 auch mit einer äußeren Druckstufe 58 versehen.Furthermore, the outer nozzle needle 24 on its side remote from the valve control chamber 36 end face on a double seat 56, by means of which the outer injection holes 32 are closable. On this side, the outer nozzle needle 24 is also provided with an outer pressure stage 58.

Die Drosselplatte 16 weist eine Kraftstoffdrossel 60 auf, die dem ein zu dem Hochdruckraum 20 führenden Kraftstoffzufuhrkanal 62 zugeordnet ist, eine zwischen dem Kraftstoffzufuhrkanal 62 und dem Ventilsteuerraum 36 angeordnete, so genannte Zulaufdrossel 64, eine zwischen dem Ventilsteuerraum 36 und einem Ventilraum 66 des Düsenmoduls 12 angeordnete, so genannte Ablaufdrossel 68 sowie ein Bypass-Kanal 70 auf, die über einen Kanal 72 mit dem Kraftstoffzufuhrkanal 62 verbunden ist und ebenfalls zu dem Ventilsteuerraum 66 führt.The throttle plate 16 has a fuel throttle 60, which is assigned to the one leading to the high-pressure chamber 20 fuel supply channel 62, disposed between the fuel supply channel 62 and the valve control chamber 36, so-called inlet throttle 64, one between the valve control chamber 36 and a valve chamber 66 of the nozzle module 12th arranged, so-called outlet throttle 68 and a bypass channel 70 which is connected via a channel 72 to the fuel supply channel 62 and also leads to the valve control chamber 66.

Die Zulaufdrossel 64 ist mittig in der Drosselplatte 16 angeordnet, wohingegen die Ablaufdrossel 68 exzentrisch angeordnet ist.The inlet throttle 64 is arranged centrally in the throttle plate 16, whereas the outlet throttle 68 is arranged eccentrically.

In dem Ventilraum 66 des Ventilsteuermoduls 12 ist ein Ventilschließglied 74 angeordnet, das mittels eines hier nicht näher dargestellten, vorzugsweise piezoelektrischen Aktors steuerbar ist. Das Ventilschließglied 74 ist mittels einer Vorspannfeder 76 in Schließrichtung vorgespannt.In the valve chamber 66 of the valve control module 12, a valve closure member 74 is arranged, which by means of a not shown here, preferably piezoelectric actuator is controllable. The valve closure member 74 is biased by a biasing spring 76 in the closing direction.

Ein Zulauf von Kraftstoff zu den Spritzlöchern 34 erfolgt von dem Kraftstoffzufuhrkanal 62 über die Kraftstoffdrossel 60, an der Hülse 28 vorbei in den Hochdruckraum 20 und dann durch den Querkanal 46 bzw. die Drossel 52 an die Außenseite der inneren Düsennadel 26 und von dort bei geöffneter innerer Düsennadel 26 zu den Spritzlöchern 34.An inflow of fuel to the spray holes 34 takes place from the fuel supply channel 62 via the fuel throttle 60, past the sleeve 28 in the high-pressure chamber 20 and then through the transverse channel 46 and the throttle 52 to the outside of the inner nozzle needle 26 and from there at open inner nozzle needle 26 to the spray holes 34th

Die innere Düsennadel 26 und die äußere Düsennadel 24 sind durch die jeweils zugeordnete Schließfeder 42 bzw. 38 sowie durch die hydraulischen Druckverhältnisse bei nicht angesteuertem piezoelektrischen Aktuator in Schließstellung gehalten. Die Druckflächen der inneren Düsennadel 26 und der äußeren Düsennadel 24, d. h. die den Spritzlöchern 32 und 34 abgewandten Stirnflächen der beiden Düsennadeln 24 und 26 sowie die innere Druckstufe 50 der inneren Düsennadel 26 und die äußere Druckstufe 58 der äußeren Düsennadel 24 sind so abgestimmt, dass der in dem Ventilsteuerraum 36 herrschende Öffnungsdruck für die innere Düsennadel 26 größer ist als der in dem Ventilsteuerraum 36 herrschende Öffnungsdruck für die äußere Düsennadel 24, was anhand Figur 2 beispielhaft dargestellt ist.The inner nozzle needle 26 and the outer nozzle needle 24 are held by the respective associated closing spring 42 and 38 and by the hydraulic pressure ratios when not driven piezoelectric actuator in the closed position. The pressure surfaces of the inner nozzle needle 26 and the outer nozzle needle 24, ie, the spray holes 32 and 34 facing away from the two nozzle needles 24 and 26 and the inner pressure stage 50 of the inner nozzle needle 26 and the outer pressure stage 58 of the outer nozzle needle 24 are tuned so that the prevailing in the valve control chamber 36 opening pressure for the inner nozzle needle 26 is greater than that prevailing in the valve control chamber 36 opening pressure for the outer nozzle needle 24, which is based FIG. 2 is shown by way of example.

Figur 2 zeigt anhand einer gestrichelten Kurve für die innere Düsennadel 26 und anhand einer durchgezogenen Kurve für die äußere Düsennadel 24 einen Öffnungsdruck p, der zum Öffnen der inneren Düsennadel 26 und der äußeren Düsennadel 24 in dem Ventilsteuerraum 36 herrschen muss, wobei der Öffnungsdruck p in Abhängigkeit von dem Durchmesser D der inneren Düsennadel 26 dargestellt ist. Beispielsweise hat die innere Düsennadel 26 einen Sitzdurchmesser von 1,3 mm, die äußere Düsennadel 24 einen Sitzdurchmesser von 1,8 mm, die Außennadel einen Durchmesser von 4 mm, wobei in der Kraftstoffzufuhrleitung 62 ein Raildruck von 1 kbar bereitgestellt wird und in dem betreffenden Brennraum ein Druck von 50 bar herrscht. Unter diesen Bedingungen muss die innere Düsennadel 26 einen Durchmesser von mehr als 2,45 mm haben, um zu erreichen, dass die innere Düsennadel 26 vor der äußeren Düsennadel 24 öffnet. Dies bedeutet, dass erst ab diesem Durchmesser D der inneren Düsennadel 26 der Öffnungsdruck der inneren Düsennadel 26 größer ist als der Öffnungsdruck der äußeren Düsennadel 24. FIG. 2 shows a broken line for the inner nozzle needle 26 and a solid curve for the outer nozzle needle 24 an opening pressure p, which must prevail for opening the inner nozzle needle 26 and the outer nozzle needle 24 in the valve control chamber 36, wherein the opening pressure p as a function of the diameter D of inner nozzle needle 26 is shown. For example, the inner nozzle needle 26 has a seat diameter of 1.3 mm, the outer nozzle needle 24 has a seat diameter of 1.8 mm, the outer needle has a diameter of 4 mm, wherein in the fuel supply line 62, a rail pressure of 1 kbar is provided and in the relevant Combustion chamber a pressure of 50 bar prevails. Under these conditions, the inner nozzle needle 26 must have a diameter greater than 2.45 mm to allow the inner nozzle needle 26 to open in front of the outer nozzle needle 24. This means that only from this diameter D of the inner nozzle needle 26, the opening pressure of the inner nozzle needle 26 is greater than the opening pressure of the outer nozzle needle 24th

Figur 3 zeigt für ein Kraftstoffeinspritzventil der in Figur 1 dargestellten Art eine Simulation eines Hubs H für eine innere Düsennadel anhand einer Kurve X und eines Hubs H für eine äußere Düsennadel anhand einer Kurve Y jeweils in Abhängigkeit von einer Ansteuerzeit des piezoelektrischen Aktors. FIG. 3 1 shows a simulation of a stroke H for an inner nozzle needle based on a curve X and a stroke H for an outer nozzle needle on the basis of a curve Y in each case as a function of a driving time of the piezoelectric actuator for a fuel injection valve of the type shown in FIG.

Dem in Figur 3 dargestellten Diagramms ist zu entnehmen, dass die innere Düsennadel zu einem früheren Zeitpunkt als die äußere Düsennadel öffnet, so dass über die jeweils zugeordneten Spritzlöcher 32 bzw. 34 Kraftstoff in den Brennraum der Brennkraftmaschine in gestufter Weise eingespritzt werden kann.The in FIG. 3 As shown, it can be seen that the inner nozzle needle opens earlier than the outer nozzle needle, so that fuel can be injected into the combustion chamber of the internal combustion engine in a stepped manner via the respective associated injection holes 32 and 34.

Das in Figur 1 dargestellte Kraftstoffeinspritzventil 10 arbeitet in nachfolgend beschriebener Weise.This in FIG. 1 shown fuel injector 10 operates in the manner described below.

Im Ausgangszustand ist der piezoelektrische Aktor in einem unbestromten Zustand, so dass sich das Ventilschließglied 74 in Schließstellung befindet und in dem Ventilsteuerraum 36 Raildruck herrscht.In the initial state, the piezoelectric actuator is in a de-energized state, so that the valve closing member 74 is in the closed position and in the valve control chamber 36 rail pressure prevails.

Bei einem Ansteuern des piezoelektrischen Aktors wird das Ventilschließglied 74 in Öffnungsstellung verfahren, so dass der Fluiddruck in dem Ventilsteuerraum 36 über die Ablaufdrossel 68 absenkt wird. Wenn der in dem Ventilsteuerraum 36 herrschende Fluiddruck auf den zum Öffnen der inneren Düsennadel 26 erforderlichen Öffnungsdruck abgesunken ist, öffnet letztere. Zunächst fällt dann der Druck in dem Ventilsteuerraum 36 nicht wesentlich weiter ab. Der Gesamthub der inneren Düsennadel 26 beträgt beispielsweise 0,2 mm, wobei die Drosselplatte 16 einen Anschlag bildet. Nach Zurücklegen ihres Gesamthubes schlägt die innere Düsennadel an der Drosselplatte 18 an, worauf die innere Düsennadel 26 den Zulauf von Kraftstoff über die Zulaufdrossel 64 in den Ventilsteuerraum 36 weitgehend abdrosselt. Dies bewirkt, dass der Druck in dem Ventilsteuerraum 36 weiter absinkt, so dass der zum Öffnen der äußeren Düsennadel 24 erforderliche Öffnungsdruck unterschritten wird. Damit öffnet auch die äußere Düsennadel 24, so dass auch Kraftstoff über die äußeren Spritzlöcher 32 in den Brennraum der Brennkraftmaschine eingespritzt wird.Upon actuation of the piezoelectric actuator, the valve closing member 74 is moved in the open position, so that the fluid pressure in the valve control chamber 36 is lowered via the outlet throttle 68. When the fluid pressure prevailing in the valve control chamber 36 has dropped to the opening pressure required to open the inner nozzle needle 26, the latter opens. First, then the pressure in the valve control chamber 36 does not drop much further. The total stroke of the inner nozzle needle 26 is for example 0.2 mm, wherein the throttle plate 16 forms a stop. After covering its total stroke, the inner nozzle needle strikes against the throttle plate 18, whereupon the inner nozzle needle 26 largely throttles the supply of fuel via the inlet throttle 64 into the valve control chamber 36. This causes the pressure in the valve control chamber 36 to further decrease, so that the opening pressure required to open the outer nozzle needle 24 is exceeded. This also opens the outer nozzle needle 24, so that fuel is injected via the outer injection holes 32 into the combustion chamber of the internal combustion engine.

Wenn eine Einspritzung von Kraftstoff in den Brennraum beendet werden soll, wird das Ventilschließglied 74 mittels des piezoelektrischen Aktors in Schließstellung verfahren, so dass der Druck in dem Ventilsteuerraum 36 wieder auf den Raildruck ansteigt. Zu diesem Zeitpunkt ist der in dem Hochdruckraum 20 herrschende Druck aufgrund der Drosselung mittels der Kraftstoffdrossel 60 geringer als der Raildruck. Durch die unterschiedlichen Druckniveaus in dem Ventilraum 36 und dem Hochdruckraum 20 wird eine schließende Kraft auf beide Nadeln ausgeübt. Dadurch, dass die Druckstufe 50 als Mitnehmer wirkt, schließen die innere Düsennadel 26 und die äußere Düsennadel 24 im Wesentlichen gleichzeitig.When an injection of fuel into the combustion chamber is to be terminated, the valve closing member 74 is moved by the piezoelectric actuator in the closed position, so that the pressure in the valve control chamber 36 increases again to the rail pressure. At this time, the one in the High pressure chamber 20 prevailing pressure due to the throttling means of the fuel throttle 60 is less than the rail pressure. Due to the different pressure levels in the valve chamber 36 and the high-pressure chamber 20, a closing force is exerted on both needles. Characterized in that the pressure stage 50 acts as a driver, close the inner nozzle needle 26 and the outer nozzle needle 24 substantially simultaneously.

Wenn nur die innere Düsennadel 26 geöffnet werden soll, wird der piezoelektrische Aktor in eine Zwischenstellung verfahren, wodurch aufgrund der Wirkung des über den Bypass-Kanal in den Ventilraum 66 strömenden Kraftstoffs der Druck in dem Ventilsteuerraum 36 nicht soweit absinkt, dass die äußere Düsennadel 24 öffnet. Auch kann ein Öffnen der äußeren Düsennadel 24 durch eine Mehrfachbestromung des piezoelektrischen Aktors verhindert werden.If only the inner nozzle needle 26 is to be opened, the piezoelectric actuator is moved to an intermediate position, whereby due to the effect of flowing over the bypass channel into the valve chamber 66 fuel, the pressure in the valve control chamber 36 does not drop so far that the outer nozzle needle 24th opens. Also, an opening of the outer nozzle needle 24 can be prevented by a Mehrfachbestromung the piezoelectric actuator.

Claims (5)

  1. Fuel injection valve, having a nozzle module (12) in which an outer nozzle needle (24), which interacts with at least one first injection opening (32) and which is surrounded by a high-pressure space (20) which is connected to a fuel supply duct (62), and an inner nozzle needle (26), which interacts with at least one second injection opening (34) and which is guided in a duct which extends axially through the outer nozzle needle (24), are guided in an axially movable manner, and having a valve control module (12) which is designed in the manner of a valve and which controls a fluid pressure prevailing in a valve control space (36) which is provided with an inflow throttle (64) and an outflow throttle (68), and the level of which fluid pressure defines the position of the outer nozzle needle (24) and of the inner nozzle needle (26), with the outer nozzle needle (24) having at least one transverse duct (46) via which fuel can be conducted out of the high-pressure space (20) to the periphery and an inner pressure stage (50) of the inner nozzle needle (26), characterized in that the transverse duct (46) has a throttle (52) and the throttle (52) is designed to adapt the fuel pressure acting on the inner pressure stage (50).
  2. Fuel injection valve according to Claim 1, characterized in that the inner nozzle needle (26) is preloaded in the closing direction by means of a closing spring (42).
  3. Fuel injection valve according to one of Claims 1 or 2, characterized in that the inner pressure stage (50) of the inner nozzle needle (26) serves as a driver for the outer nozzle needle (24).
  4. Fuel injection valve according to one of Claims 1 to 3, characterized in that the inner nozzle needle (26), in the open state, acts as a throttle for a fuel inflow into the valve control space (36).
  5. Fuel injection valve according to one of Claims 1 to 4, characterized in that a fuel throttle (60) is arranged in the fuel supply duct (62).
EP05701507A 2004-03-06 2005-01-13 Fuel-injection valve Not-in-force EP1727977B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004011095A DE102004011095A1 (en) 2004-03-06 2004-03-06 Fuel injection valve
PCT/EP2005/050122 WO2005085624A1 (en) 2004-03-06 2005-01-13 Fuel-injection valve

Publications (2)

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EP1727977A1 EP1727977A1 (en) 2006-12-06
EP1727977B1 true EP1727977B1 (en) 2008-03-19

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EP05701507A Not-in-force EP1727977B1 (en) 2004-03-06 2005-01-13 Fuel-injection valve

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EP (1) EP1727977B1 (en)
AT (1) ATE389796T1 (en)
DE (2) DE102004011095A1 (en)
WO (1) WO2005085624A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006037175A1 (en) * 2006-08-09 2008-02-14 Robert Bosch Gmbh An automotive fuel injection valve has concentric spring with elastic side-extensions subjected to lateral shift
DE102006051583A1 (en) * 2006-11-02 2008-05-08 Robert Bosch Gmbh Fuel injector with storage volume segment
GB0801997D0 (en) 2007-05-01 2008-03-12 Delphi Tech Inc Fuel injector
DE102009046336A1 (en) 2009-11-03 2011-05-05 Robert Bosch Gmbh Valve arrangement for controlling lifting movements and positions of nozzle needle in fuel injector, has compression spring with spring brackets that are arranged within circular-cylindrical surface and extended in circumferential direction
US8690075B2 (en) 2011-11-07 2014-04-08 Caterpillar Inc. Fuel injector with needle control system that includes F, A, Z and E orifices

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5899389A (en) * 1997-06-02 1999-05-04 Cummins Engine Company, Inc. Two stage fuel injector nozzle assembly
US6705543B2 (en) * 2001-08-22 2004-03-16 Cummins Inc. Variable pressure fuel injection system with dual flow rate injector
DE10155227A1 (en) * 2001-11-09 2003-05-22 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10205970A1 (en) * 2002-02-14 2003-09-04 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10254186A1 (en) * 2002-11-20 2004-06-17 Siemens Ag Injector with a directly driven register nozzle needle for fuel injection into an internal combustion engine

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DE502005003321D1 (en) 2008-04-30
ATE389796T1 (en) 2008-04-15
WO2005085624A1 (en) 2005-09-15
EP1727977A1 (en) 2006-12-06

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