EP1036271B1 - Injection valve for intermittent fuel injection - Google Patents

Injection valve for intermittent fuel injection Download PDF

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Publication number
EP1036271B1
EP1036271B1 EP98965750A EP98965750A EP1036271B1 EP 1036271 B1 EP1036271 B1 EP 1036271B1 EP 98965750 A EP98965750 A EP 98965750A EP 98965750 A EP98965750 A EP 98965750A EP 1036271 B1 EP1036271 B1 EP 1036271B1
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EP
European Patent Office
Prior art keywords
valve
actuator
injection
pressure
valve actuator
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Expired - Lifetime
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EP98965750A
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German (de)
French (fr)
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EP1036271A1 (en
Inventor
Wolfgang Scheibe
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LOrange GmbH
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LOrange GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • 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
    • 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

Definitions

  • the invention relates to an injection valve for intermittent fuel injection in the combustion chamber of an internal combustion engine with a in a valve housing between a closed and open position axially movably guided valve actuator, which in Closed position is pressed against a substantially conical valve seat and so the closes in a blind hole downstream of the valve seat injection openings and with a control chamber that has at least one inlet throttle bore with a high pressure leading fuel supply line is connected and via an outlet throttle bore with a drain line under low pressure, the pressure in the control room is controllable via an electromagnetically actuated control valve element and depends on Control room pressure the valve actuator is actuated.
  • valve actuator is designed as a nozzle needle with its tip on presses the conical nozzle needle seat to close the injector Keep condition.
  • the dynamic stress on the nozzle tip is correspondingly high with the nozzle needle seat, which depends on the mass of the moving nozzle needle at each Closing process of the nozzle occurs as an impact load. A reduction in the impact load the slower closing movement of the nozzle needle is therefore out of the question, because this means that inaccurate metering and, above all, dripping of the nozzle are accepted should be.
  • the object of the present invention is therefore to provide an injection valve of the type mentioned at the beginning To improve the genus so that even at extremely high injection pressures and high required accuracy with regard to the injection quantities an impermissibly large load between valve actuator and valve seat is avoided and thus long service life of an injection valve can be reached.
  • the object is achieved in that a valve actuator holder in the valve housing is arranged, which has a lower end in the immediate Extends near the valve seat, the valve actuator in the lower end of the valve actuator holder the actuating movement is permitted and the control chamber as a bore in the valve actuator holder is guided to the valve actuator and this is pressurized.
  • the inventive design of an injection valve ensures that the extremely high pressure level and valve actuator operating at high actuating speeds can have the lowest possible mass and thus the dynamic forces at the valve seat be significantly reduced.
  • the fixed arrangement of a valve actuator holder extends into the immediate vicinity of the valve seat and receives the valve actuator there the prerequisite for the small dimensions and thus the low mass of the valve actuator.
  • a valve actuator in the arrangement according to the invention available, the dimension of which is very small in the direction of the actuating movement.
  • valve actuator is a ball. It
  • cylindrical valve actuators in the form of pistons are also possible, the extension in the axial direction is not chosen to be significantly larger than the diameter.
  • the injection valve can be designed in such a way that the Spring force acts on the valve actuator in the closing direction, as well as in the opposite manner so that a spring applies a permanent force to the valve actuator in the opening direction.
  • the control and the exact movement of the valve actuator is controlled by hydrauli pressure.
  • the force are by appropriate geometric design of the valve head member with pressure surfaces established.
  • the injection valve shown in section in Fig. 1 has a valve housing 9 with a connecting piece 29 for a high-pressure fuel line.
  • a nozzle body 11 of an injection nozzle is screwed by means of a nozzle nut 10.
  • a fuel feed line 13 leads from the connecting piece 29 through the valve housing 9 and through the nozzle body 11 to a valve seat 6 of the injection nozzle.
  • an essentially cylindrical valve actuator holder 14 used, which has a control chamber 2 formed as a central bore. The valve actuator holder 14 extends down to the valve seat 6.
  • an inlet throttle bore 3 is provided, which the fuel inlet line 13 connects to the control room 2.
  • an outlet throttle bore 18 is provided, which in control room 2 has a fuel outlet line 12 connects.
  • the cross section of the discharge throttle bore 18 is larger than the cross section the inlet throttle bore 3.
  • valve actuator holder 14 On his is centered in the conical valve seat 6 via a centering collar 16.
  • the control room 2 of the valve actuator holder 14 extends downward to a bore in which Valve actuator 4, which is designed as a ball, is axially movable.
  • Valve actuator 4 which is designed as a ball
  • valve actuator 4 As in 2, when the injector is closed, the valve actuator 4, namely the Ball acted upon by the pressure in the control chamber 2, this pressure via the inlet throttle bore 3 is equal to the high pressure in the fuel feed line 13.
  • the outlet throttle bore 18 of the control room 2 is closed by the control valve element 8. If the control valve element 8 is now raised by the electromagnet 28 and thus the Drain throttle bore opened against the drain line 12, the pressure in the control chamber drops 2 from and the spherical valve actuator 4 is due to the partial cross-section from below of the valve actuator acting high pressure is lifted from the valve seat 6. The valve cross section is released and there is an injection that continues until the Pressure in the control chamber 2 by closing the outlet throttle bore 18 by means of the control valve element 8 rises again and presses the valve actuating element onto the valve seat. How from 2 easily recognizable, the stress on the valve seat 6 is even at the highest Pressures and pressure differences and extremely high actuating speeds of the valve actuator 4 remain low because the mass of the valve actuator 4 is considerably less than that a conventional nozzle needle.
  • valve actuator 4 it may be desirable to additionally for actuation via hydraulic pressure or differential pressure to provide the valve actuator 4 by spring force.
  • Fig. 3 an embodiment is provided in which the spherical valve actuator 4 by means of a compression spring 24 in the closed position is held on the valve seat 6. In the closed position shown acts on Valve actuator from above the pressure force of the spring and resulting from the free cross-sectional area and the hydraulic pressure force resulting in the control chamber. opposite the closing pressure force acts on a pressure force resulting from the lower cross-sectional projection of the spherical valve actuator 4 between the valve seat 6 and the largest results in a free cross-section and the associated pressure of the high pressure in the fuel feed line equivalent.
  • the valve actuator 4 is not in the closing direction of a Compression spring is applied but against the closing direction, d. H. the compression spring would then be placed in blind hole 7.
  • FIG. 4 largely resembles the image according to FIG. 3 and differs only in that a stepped cylindrical piston instead of a ball as a valve actuator 4a is used.
  • the piston 4a acts as described above with the conical valve seat 6 together and is acted upon in the closing direction by a compression spring 24.
  • the remaining Elements of the injection nozzle correspond to the description above for FIGS. 1 to 3.
  • the axial extent of the piston 4a is only slightly larger than the diameter of the Valve seat. This causes the mass of the piston 4a and, in turn, the occurrence dynamic forces during opening and closing are kept low.

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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)

Description

Die Erfindung bezieht sich auf ein Einspritzventil zur intermittierenden Brennstoffeinspritzung in den Brennraum einer Brennkraftmaschine mit einem in einem Ventilgehäuse zwischen einer Schließ- und Offenstellung axial beweglich geführten Ventilstellglied, welches in Schließstellung gegen einen im wesentlichen konischen Ventilsitz angedrückt wird und so die in einem Sackloch stromabwärts des Ventilsitzes befindlichen Einspritzöffnungen verschließt und mit einem Steuerraum, der über wenigstens eine Zulaufdrosselbohrnung mit einer Hockdruck führenden Brennstoffzulaufleitung in Verbindung steht und über eine Ablaufdrosselbohrung mit einer unter Niederdruck stehenden Ablaufleitung, wobei der Druck im Steuerraum über ein elektromagnetisch betätigtes Steuerventilelement steuerbar ist und abhängig vom Steuerraumdruck das Ventilstellglied betätigt wird.The invention relates to an injection valve for intermittent fuel injection in the combustion chamber of an internal combustion engine with a in a valve housing between a closed and open position axially movably guided valve actuator, which in Closed position is pressed against a substantially conical valve seat and so the closes in a blind hole downstream of the valve seat injection openings and with a control chamber that has at least one inlet throttle bore with a high pressure leading fuel supply line is connected and via an outlet throttle bore with a drain line under low pressure, the pressure in the control room is controllable via an electromagnetically actuated control valve element and depends on Control room pressure the valve actuator is actuated.

Ein Einspritzventil mit den vorstehend genannten Merkmalen ist aus der US-PS 3 610 529, dort Fig. 3, und die zugehörige Beschreibung bekannt. Wie auch bei anderen herkömmlichen Einspritzventilen ist das Ventilstellglied als Düsennadel ausgebildet, die mit ihrer Spitze auf den konisch ausgebildeten Düsennadelsitz drückt, um das Einspritzventil in geschlossenem Zustand zu halten. Je höher die Einspritzdrücke liegen, die beim Betrieb eines solchen Einspritzventils auftreten, desto höher liegen die Schließkräfte zwischen Düsennadel und Düsennadelsitz. Dementsprechend hoch ist die dynamische Beanspruchung der Düsenspitze mit dem Düsennadelsitz, die abhängig von der Masse der bewegten Düsennadel bei jedem Schließvorgang der Düse als Schlagbelastung auftritt. Ein Herabsetzen der Schlagbelastung etwa durch langsamere Schließbewegung der Düsennadel kommt deshalb nicht in Betracht, weil dadurch ein unexaktes Zumessen und vor allem ein Nachtropfen der Düse in Kauf genommen werden müßte.An injection valve with the features mentioned above is known from US Pat. No. 3,610,529, there Fig. 3, and the associated description known. As with other conventional ones Injectors, the valve actuator is designed as a nozzle needle with its tip on presses the conical nozzle needle seat to close the injector Keep condition. The higher the injection pressures are when operating such an injection valve occur, the higher the closing forces between the nozzle needle and the nozzle needle seat. The dynamic stress on the nozzle tip is correspondingly high with the nozzle needle seat, which depends on the mass of the moving nozzle needle at each Closing process of the nozzle occurs as an impact load. A reduction in the impact load the slower closing movement of the nozzle needle is therefore out of the question, because this means that inaccurate metering and, above all, dripping of the nozzle are accepted should be.

Aufgabe der vorliegenden Erfindung ist es deshalb, ein Einspritzventil der eingangs bezeichneten Gattung so zu verbessern, daß auch bei extrem hohen Einspritzdrücken und hoher geforderter Genauigkeit bezüglich der Einspritzmengen eine unzuläßig große Beanspruchung zwischen Ventilstellglied und Ventilsitz vermieden wird und somit lange Standzeiten eines Einspritzventils erreichbar sind.The object of the present invention is therefore to provide an injection valve of the type mentioned at the beginning To improve the genus so that even at extremely high injection pressures and high required accuracy with regard to the injection quantities an impermissibly large load between valve actuator and valve seat is avoided and thus long service life of an injection valve can be reached.

Erfindungsgemäß wird die gestellte Aufgabe dadurch gelöst, daß im Ventilgehäuse ein Ventilstellgliedhalter angeordnet ist, welcher sich mit einem unteren Ende bis in unmittelbare Nähe des Ventilsitzes erstreckt, das Ventilstellglied im unteren Ende des Ventilstellgliedhalters die Stellbewegung zulassend geführt ist und der Steuerraum als Bohrung im Ventilstellgliedhalter bis zum Ventilstellglied geführt ist und dieses druckbeaufschlagt.According to the invention the object is achieved in that a valve actuator holder in the valve housing is arranged, which has a lower end in the immediate Extends near the valve seat, the valve actuator in the lower end of the valve actuator holder the actuating movement is permitted and the control chamber as a bore in the valve actuator holder is guided to the valve actuator and this is pressurized.

Durch die erfindungsgemäße Ausbildung eines Einspritzventils wird erreicht, daß das bei extrem hohem Druckniveau und mit hohen Stellgeschwindigkeiten arbeitende Ventilstellglied geringstmögliche Masse aufweisen kann und somit die dynamischen Kräfte am Ventilsitz maßgeblich reduziert werden. Die ortsfeste Anordnung eines Ventilstellgliedhalters, der sich bis in unmittelbare Nähe des Ventilsitzes erstreckt und dort das Ventilstellglied aufnimmt, ist die Voraussetzung für die geringe Abmessung und damit die geringe Masse des Ventilstellgliedes. Anstelle einer im Stand der Technik bekannten Düsennadel, deren Länge verglichen mit der Ausdehnung des Düsennadelsitzes ein Vielfaches beträgt und die dementsprechend beachtliche Masse aufweist, ist bei der erfindungsgemäßen Anordnung ein Ventilstellglied vorhanden, dessen Abmessung in Richtung der Stellbewegung nur sehr gering ist.The inventive design of an injection valve ensures that the extremely high pressure level and valve actuator operating at high actuating speeds can have the lowest possible mass and thus the dynamic forces at the valve seat be significantly reduced. The fixed arrangement of a valve actuator holder extends into the immediate vicinity of the valve seat and receives the valve actuator there the prerequisite for the small dimensions and thus the low mass of the valve actuator. Instead of a nozzle needle known in the prior art, the length of which is compared with the expansion of the nozzle needle seat is a multiple and accordingly has considerable mass, is a valve actuator in the arrangement according to the invention available, the dimension of which is very small in the direction of the actuating movement.

Bei einer bevorzugten Ausführungsform der Erfindung ist das Ventilstellglied eine Kugel. Es sind jedoch auch zylindrische Ventilsteliglieder in Form von Kolben möglich, wobei die Erstreckung in Achsrichtung nicht wesentlich größer gewählt wird als der Durchmesser. Zur Erzielung eines exakt schließenden Ventilsitzes wird gemäß weiterer Ausbildung der Erfindung vorgeschlagen, daß der Ventilstellgliedhalter am unteren Ende in dem Ventilsitz selbst zentriert ist.In a preferred embodiment of the invention, the valve actuator is a ball. It However, cylindrical valve actuators in the form of pistons are also possible, the extension in the axial direction is not chosen to be significantly larger than the diameter. to Achieving an exactly closing valve seat is according to a further embodiment of the invention suggested that the valve actuator holder at the lower end in the valve seat itself is centered.

Zur Sicherung exakter Stellbewegungen des Ventilstellgliedes kann es vorteilhaft sein, wie an sich bekannt, das Ventilstellglied zusätzlich zum hydraulischen Druck mit Federkraft zu beaufschlagen. Dabei kann das Einspritzventil sowohl in der Weise ausgebildet sein, daß die Federkraft das Ventilstellglied in Schließrichtung beaufschlagt, als auch in gegenteiliger Weise so, daß eine Feder eine dauernde Kraft auf das Ventilstellglied in Öffnungsrichtung aufbringt. Die Steuerung und die exakte Bewegung des Ventilstellglieds wird durch hydrauli schen Druck bewirkt. Dabei steht einerseits der Hochdruck aus der Brennstoffzulaufleitung zur Verfügung, zum andern der Niederdruck aus der Brennstoffablaufleitung. Die Stellkrafte werden durch entsprechende geometrische Ausbildung des Ventilsfellgliedes mit Druckangriffsflächen festgelegt.To ensure exact actuating movements of the valve actuator, it can be advantageous as to it is known to apply spring force to the valve actuator in addition to the hydraulic pressure. The injection valve can be designed in such a way that the Spring force acts on the valve actuator in the closing direction, as well as in the opposite manner so that a spring applies a permanent force to the valve actuator in the opening direction. The control and the exact movement of the valve actuator is controlled by hydrauli pressure. On the one hand, there is the high pressure from the fuel feed line available, on the other hand the low pressure from the fuel drain line. The force are by appropriate geometric design of the valve head member with pressure surfaces established.

Anhand der beigefügten Zeichnungen werden Ausführungsbeispiele der Erfindung erläutert.Exemplary embodiments of the invention are explained with reference to the attached drawings.

In den Zeichnungen zeigt:

Fig. 1
ein erfindungsgemäßes Einspritzventil im Mittellängsschnitt,
Fig. 2
den unteren Bereich des in Fig. 1 dargestellten Einspritzventils in vergrößerter Darstellung,
Fig. 3
eine gegenüber Fig. 2 noch einmal vergrößerte Darstellung des Ventilsitzbereiches des Einspritzventils nach den Fig. 1 und 2 und
Fig. 4
den unteren Bereich eines Einspritzventils entsprechend Fig. 1, jedoch mit einem als zylindrischer Kolben ausgebildeten Ventilstellglied.
In the drawings:
Fig. 1
an injection valve according to the invention in the central longitudinal section,
Fig. 2
the lower area of the injection valve shown in Fig. 1 in an enlarged view,
Fig. 3
a once again enlarged view of FIG. 2 of the valve seat area of the injection valve according to FIGS. 1 and 2 and
Fig. 4
the lower region of an injection valve according to FIG. 1, but with a valve actuator designed as a cylindrical piston.

Das in Fig. 1 im Schnitt dargestellte Einspritzventil weist ein Ventilgehäuse 9 mit einem Anschlußstutzen 29 für eine Brennstoffhochdruckleitung auf. An das untere Ende des Ventilgehäuses 9 ist mittels einer Düsenmutter 10 ein Düsenkörper 11 einer Einspritzdüse verschraubt. Vom Anschlußstutzen 29 führt eine Brennstoffzulaufleitung 13 durch das Ventilgehäuse 9 und durch den Düsenkörper 11 bis zu einem Ventilsitz 6 der Einspritzdüse. Anstelle der bei herkömmlichen Einspritzdüsen zentrisch angeordneten üblichen Düsennadel ist in den Düsenkörper 11 ein im wesentlichen zylindrisch ausgebildeter Ventilstellgliedhalter 14 eingesetzt, der einen als zentrale Bohrung ausgebildeten Steuerraum 2 aufweist. Der Ventilstellgliedhalter 14 erstreckt sich nach unten bis zum Ventilsitz 6. Im mittleren Bereich des Ventilstellgliedhalters 14 ist eine Zulaufdrosselbohrung 3 vorgesehen, die die Brennstoffzulaufleitung 13 mit dem Steuerraum 2 verbindet. Am oberen Ende des Ventilstellgliedhalters 14 ist eine Ablaufdrosselbohrung 18 vorgesehen, die im Steuerraum 2 mit einer Brennstoffablaufleitung 12 verbindet. Der Querschnitt der Ablaufdrosslbohrung 18 ist größer als der Querschnitt der Zulaufdrosselbohrung 3. In Ruhestellung des Einspritzventils, d. h. wenn kein Kraftstoff eingespritzt wird, ist die Ablaufdrosselbohrung 18 durch ein Steuerventilelement 8, welches die Form einer zylindrischen Nadel aufweist, verschlossen. Das Steuerventilelement 8 ist in Axialrichtung durch einen Elektromagneten 28 bewegbar. The injection valve shown in section in Fig. 1 has a valve housing 9 with a connecting piece 29 for a high-pressure fuel line. To the lower end of the valve body 9, a nozzle body 11 of an injection nozzle is screwed by means of a nozzle nut 10. A fuel feed line 13 leads from the connecting piece 29 through the valve housing 9 and through the nozzle body 11 to a valve seat 6 of the injection nozzle. Instead of the usual nozzle needle arranged centrally in conventional injection nozzles is in the nozzle body 11 is an essentially cylindrical valve actuator holder 14 used, which has a control chamber 2 formed as a central bore. The valve actuator holder 14 extends down to the valve seat 6. In the central area of the Valve actuator holder 14, an inlet throttle bore 3 is provided, which the fuel inlet line 13 connects to the control room 2. At the top of the valve actuator bracket 14, an outlet throttle bore 18 is provided, which in control room 2 has a fuel outlet line 12 connects. The cross section of the discharge throttle bore 18 is larger than the cross section the inlet throttle bore 3. In the rest position of the injection valve, d. H. if no Fuel is injected, the outlet throttle bore 18 through a control valve element 8, which has the shape of a cylindrical needle, closed. The control valve element 8 is movable in the axial direction by an electromagnet 28.

Die Funktion des Einspritzventils wird anhand der vergrößerten Darstellung des unteren Bereichs gemäß Fig. 2 erläutert. Gleiche Bauteile sind mit gleichen Bezugszeichen wie in Fig. 1 versehen. Aus dieser Darstellung ist erkennbar, daß der Ventilstellgliedhalter 14 an seinem unteren Ende über einen Zentrierbund 16 im konischen Ventilsitz 6 zentriert ist. Der Steuerraum 2 des Ventilstellgliedhalters 14 erweitert sich nach unten zu einer Bohrung, in der das Ventilstellglied 4, welches als Kugel ausgebildet ist, axial beweglich gefaßt ist. In geschlossener Stellung der Kraftstoffdüse sitzt die Kugel auf dem konischen Ventilsitz 6 auf, so daß das stromabwärtige Sackloch 7, von dem Spritzlöcher 17 ausgehen, drucklos bleibt. Wie in der Fig. 2 dargestellt, ist bei geschlossener Einspritzdüse das Ventilstellglied 4, nämlich die Kugel durch den Druck im Steuerraum 2 beaufschlagt, wobei dieser Druck über die Zulaufdrosselbohrung 3 gleich dem Hochdruck in der Brennstoffzulaufleitung 13 ist. Die Ablaufdrosselbohrung 18 des Steuerraums 2 wird von dem Steuerventilelement 8 abgeschlossen. Wird nun durch den Elektromagneten 28 das Steuerventilelement 8 angehoben und somit die Ablaufdrosselbohrung gegen die Ablaufleitung 12 geöffnet, so fällt der Druck im Steuerraum 2 ab und das kugelförmige Ventilstellglied 4 wird infolge des von unten auf einen Teilquerschnitt des Ventilstellglieds wirkenden Hochdrucks vom Ventilsitz 6 abgehoben. Der Ventilquerschnitt wird freigegeben und es erfolgt eine Einspritzung, die solange andauert, bis der Druck im Steuerraum 2 durch Schließen der Ablaufdrosselbohrung 18 mittels des Steuerventilelements 8 wieder ansteigt und das Ventilstellelement auf den Ventilsitz preßt. Wie aus der Fig. 2 leicht erkennbar, wird die Beanspruchung des Ventilsitzes 6 selbst bei höchsten Drücken und Druckunterschieden und extrem hohen Stellgeschwindigkeiten des Ventilstellglieds 4 gering bleiben, da die Masse des Ventilstellglieds 4 erheblich geringer ist als die einer herkömmlichen Düsennadel.The function of the injection valve is based on the enlarged representation of the lower area 2 explained. The same components have the same reference numerals as in FIG. 1 Mistake. From this illustration it can be seen that the valve actuator holder 14 on his is centered in the conical valve seat 6 via a centering collar 16. The control room 2 of the valve actuator holder 14 extends downward to a bore in which Valve actuator 4, which is designed as a ball, is axially movable. In closed Position of the fuel nozzle, the ball sits on the conical valve seat 6, so that the downstream blind hole 7, from which spray holes 17 originate, remains depressurized. As in 2, when the injector is closed, the valve actuator 4, namely the Ball acted upon by the pressure in the control chamber 2, this pressure via the inlet throttle bore 3 is equal to the high pressure in the fuel feed line 13. The outlet throttle bore 18 of the control room 2 is closed by the control valve element 8. If the control valve element 8 is now raised by the electromagnet 28 and thus the Drain throttle bore opened against the drain line 12, the pressure in the control chamber drops 2 from and the spherical valve actuator 4 is due to the partial cross-section from below of the valve actuator acting high pressure is lifted from the valve seat 6. The valve cross section is released and there is an injection that continues until the Pressure in the control chamber 2 by closing the outlet throttle bore 18 by means of the control valve element 8 rises again and presses the valve actuating element onto the valve seat. How from 2 easily recognizable, the stress on the valve seat 6 is even at the highest Pressures and pressure differences and extremely high actuating speeds of the valve actuator 4 remain low because the mass of the valve actuator 4 is considerably less than that a conventional nozzle needle.

Zur Erzielung exakter Positionierung des Ventilstellglieds kann es wünschenswert sein, zusätzlich zur Betätigung über hydraulischen Druck bzw. Differenzdruck eine Beaufschlagung des Ventilstellglieds 4 durch Federkraft vorzusehen. In Fig. 3 ist eine Ausführungsform vorgesehen, bei der das kugelförmige Ventilstellglied 4 mittels einer Druckfeder 24 in Schließposition auf dem Ventilsitz 6 gehalten wird. In der dargestellten Schließposition wirkt auf das Ventilstellglied von oben die Druckkraft der Feder und die sich aus der freien Querschnittsfläche und dem im Steuerraum herrschenden Druck ergebende hydraulische Druckkraft. Entgegen der Schließdruckkraft wirkt eine Druckkraft, die sich aus der unteren Querschnittsprojektion des kugelförmigen Ventilstellglieds 4 zwischen dem Ventilsitz 6 und dem größten freien Querschnitt ergibt und dem zugehörigen Druck der dem Hochdruck in der Brennstoffzulaufleitung entspricht. Falls die geometrischen Verhältnisse es erfordern, ist es jedoch ohne weiteres denkbar, daß das Ventilstellelement 4 nicht in Schließrichtung von einer Druckfeder beaufschlagt wird sondern entgegen der Schließrichtung, d. h. die Druckfeder würde dann in Sackloch 7 angebracht sein.To achieve exact positioning of the valve actuator, it may be desirable to additionally for actuation via hydraulic pressure or differential pressure to provide the valve actuator 4 by spring force. In Fig. 3 an embodiment is provided in which the spherical valve actuator 4 by means of a compression spring 24 in the closed position is held on the valve seat 6. In the closed position shown acts on Valve actuator from above the pressure force of the spring and resulting from the free cross-sectional area and the hydraulic pressure force resulting in the control chamber. opposite the closing pressure force acts on a pressure force resulting from the lower cross-sectional projection of the spherical valve actuator 4 between the valve seat 6 and the largest results in a free cross-section and the associated pressure of the high pressure in the fuel feed line equivalent. However, if the geometric conditions require it, it is readily conceivable that the valve actuator 4 is not in the closing direction of a Compression spring is applied but against the closing direction, d. H. the compression spring would then be placed in blind hole 7.

Die Darstellung gemäß Fig. 4 gleicht weitgehend dem Bild nach Fig. 3 und unterscheidet sich nur dadurch, daß als Ventilstellglied anstelle einer Kugel ein abgesetzter zylindrischer Kolben 4a verwendet wird. Der Kolben 4a wirkt, wie oben beschrieben, mit dem konischen Ventilsitz 6 zusammen und wird in Schließrichtung von einer Druckfeder 24 beaufschlagt. Die übrigen Elemente der Einspritzdüse entsprechen der obigen Beschreibung zu den Fig. 1 bis 3. Die axiale Erstreckung des Kolbens 4a ist nur unwesentlich größer als der Durchmesser des Ventilsitzes. Dadurch wird die Masse des Kolbens 4a und damit wiederum das Auftreten dynamischer Kräfte beim Öffnungs- und Schließvorgang gering gehalten.The illustration according to FIG. 4 largely resembles the image according to FIG. 3 and differs only in that a stepped cylindrical piston instead of a ball as a valve actuator 4a is used. The piston 4a acts as described above with the conical valve seat 6 together and is acted upon in the closing direction by a compression spring 24. The remaining Elements of the injection nozzle correspond to the description above for FIGS. 1 to 3. The axial extent of the piston 4a is only slightly larger than the diameter of the Valve seat. This causes the mass of the piston 4a and, in turn, the occurrence dynamic forces during opening and closing are kept low.

Claims (5)

  1. Injection valve for intermittent fuel injection into the combustion space of an internal combustion engine, with a valve actuator (4) which is guided in an axially moveable manner in the injection valve between a closing position and an opening position and which, in the closing position, is pressed against an essentially conical valve seat (6) and thus closes the injection orifices (5) located in a blind hole (7), downstream of the valve seat (6), in a nozzle body (11) which is arranged at the lower end of a valve housing (9), and with a control space (2) which is connected, via at least one inflow throttle bore (3), to a fuel inflow line (13) carrying high pressure and, via an outflow throttle bore (18), to an outflow line which is under low pressure, the pressure in the control space (2) being capable of being controlled via an electromagnetically actuated control-valve element, and the valve actuator being actuated as a function of the control-space pressure,
    characterized in that
    a) the nozzle body (11) has arranged in it a valve-actuator holder (14) which extends with a lower end as far as into the immediate vicinity of the valve seat (6),
    b) the valve actuator (4) is guided in the lower end of the valve-actuator holder (14) so as to allow the actuating movement, and
    c) the control space (2), as a bore in the valve-actuator holder (14), is lead as far as the valve actuator (4) and subjects the latter to pressure.
  2. Injection valve according to Claim 1, characterized in that the valve actuator is a ball.
  3. Injection valve according to Claim 1 or Claim 2, characterized in that the valve-actuator holder is centred at the lower end in the valve seat (6).
  4. Injection valve according to one of Claims 1 to 3, characterized in that the valve actuator is additionally loaded in the closing direction by a compression spring.
  5. Injection valve according to Claim 1, 3 or 4, characterized in that the valve actuator is in the form of a piston (4a), of which the extent in the axial direction is only insignificantly greater than the diameter.
EP98965750A 1997-12-05 1998-12-03 Injection valve for intermittent fuel injection Expired - Lifetime EP1036271B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19754050 1997-12-05
DE19754050A DE19754050A1 (en) 1997-12-05 1997-12-05 Injector for intermittent fuel injection
PCT/EP1998/007857 WO1999030029A1 (en) 1997-12-05 1998-12-03 Injection valve for intermittent fuel injection

Publications (2)

Publication Number Publication Date
EP1036271A1 EP1036271A1 (en) 2000-09-20
EP1036271B1 true EP1036271B1 (en) 2002-03-27

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EP98965750A Expired - Lifetime EP1036271B1 (en) 1997-12-05 1998-12-03 Injection valve for intermittent fuel injection

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DE (2) DE19754050A1 (en)
WO (1) WO1999030029A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10058010A1 (en) 2000-11-23 2002-05-29 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10061571B4 (en) * 2000-12-11 2007-03-22 Robert Bosch Gmbh Fuel injector
DE102008000702A1 (en) 2008-03-17 2009-09-24 Robert Bosch Gmbh injector

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH495504A (en) 1968-08-28 1970-08-31 Sopromi Soc Proc Modern Inject Fuel injection valve with electromagnetic actuation
FR2580728B1 (en) * 1985-04-19 1989-05-05 Alsacienne Constr Meca FUEL INJECTION SYSTEM FOR DIESEL ENGINE
IT1261149B (en) * 1993-12-30 1996-05-09 Elasis Sistema Ricerca Fiat DOSING VALVE FOR THE CONTROL OF THE SHUTTER OF A FUEL INJECTOR

Also Published As

Publication number Publication date
WO1999030029A1 (en) 1999-06-17
DE59803566D1 (en) 2002-05-02
EP1036271A1 (en) 2000-09-20
DE19754050A1 (en) 1999-07-15

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