EP0864743A2 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP0864743A2
EP0864743A2 EP97120314A EP97120314A EP0864743A2 EP 0864743 A2 EP0864743 A2 EP 0864743A2 EP 97120314 A EP97120314 A EP 97120314A EP 97120314 A EP97120314 A EP 97120314A EP 0864743 A2 EP0864743 A2 EP 0864743A2
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EP
European Patent Office
Prior art keywords
valve
piston
fuel injection
hydraulic
valve member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP97120314A
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German (de)
French (fr)
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EP0864743A3 (en
EP0864743B1 (en
Inventor
Katsuoki Itoh
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0864743A3 publication Critical patent/EP0864743A3/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/046—Fluid pressure acting on injection-valve in the period of injection to open it
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
  • Fuel injection valve is a piston-shaped valve member axially slidably disposed in a valve body with its free end in the combustion chamber of the one to be supplied Internal combustion engine protrudes.
  • the valve member points to his end on the combustion chamber side with a valve sealing surface which is used to control an injection cross section with a Valve seat surface cooperates on the valve body, one of which Injection opening leads into the combustion chamber of the internal combustion engine.
  • the valve member is operated by an electrical actuator, preferably axially actuated a piezo actuator, wherein the actuating movement of the piezo actuator via a hydraulic Working space is transferred to the valve member.
  • an electrical actuator preferably axially actuated a piezo actuator, wherein the actuating movement of the piezo actuator via a hydraulic Working space is transferred to the valve member.
  • the known fuel injection valve the disadvantage that there are overshoots in dynamic operation and bouncing of the valve member can come result in an unwanted opening of the injection valve.
  • natural vibrations occur in the known fuel injection valve of the piezo actuator via the hydraulic amplifier room transferred to the valve member, so that this too begins to oscillate and thus falsifies the injection process.
  • Another disadvantage of the known fuel injection valve occurs during the reset movement of the piezo actuator on, with the rapid increase in volume of the hydraulic Working space the pressure of the inside Fuel can drop below the vapor pressure and thus cavitation damage may occur.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that the use a second electrical actuator a very fast and direct valve member actuation is possible with which is the cross section of the injection opening and thus the course of the injection on the fuel injection valve optimally over the Injection time forms.
  • the mechanical one takes place or temperature compensation of the piezo actuator and the hydraulic Amplification of the adjustment movement of the piezo actuator via a hydraulic work area.
  • This work space is included divided into two sub-rooms, each by one Pistons of the piezo actuator and the valve member are limited and which are separated from each other by a throttling point, so that vibrations occurring at the piezo actuator do not affect the Valve element are transmitted and an overshoot or Bouncers on the valve member itself are suppressed.
  • Through the Separation of the electric actuator and its adjusting piston will also create a negative pressure at fast Resetting the electrical actuators avoided, whereby then lift them off the adjusting piston.
  • Particularly advantageous is the use of two in the opposite direction the valve actuator acting electrical actuators, because thus in addition to a very fast and controlled opening stroke the closing stroke of the valve member is very quick and controlled can be executed.
  • the electrical actuator can alternatively as a piezoelectric or magnetostrictive actuator.
  • Fuel injection valve as an outward opening injection valve or inward opening injection valve, e.g. B. hole or tenon nozzle.
  • FIG. 1 shows a first embodiment in a simplified schematic representation, in which the two piezo actuators in the same direction of adjustment via a common hydraulic work area on the Valve member act
  • Figure 2 shows a second embodiment, in which the two electrical actuators in each opposite direction of adjustment via a common hydraulic working space on the valve member of the fuel injector attack
  • Figure 3 a third Embodiment analogous to the representation of Figure 2, at a separate hydraulic one for each electric actuator Working space is assigned to the valve member.
  • Fuel injection valve for internal combustion engines has one Valve body 1 on, with its lower free end in the combustion chamber, not shown, to be supplied Internal combustion engine protrudes.
  • the valve body 1 In the valve body 1 is one axial blind hole 3 is provided, in which a not shown injection line leading away from a fuel injection pump flows.
  • a piston-shaped is in the valve body 1
  • Valve member 5 is arranged axially displaceable a valve sealing surface 7 at its lower end near the combustion chamber with which it is used to control an injection cross section cooperates with a valve seat surface 9 on the valve body 1, formed at the closed end of the blind hole 3 is. Two lead from the valve seat 9 Injection openings 11 in the combustion chamber to be supplied Internal combustion engine.
  • valve member 5 reduces at its the end facing away from the valve sealing surface 7 has its cross section forming an annular shoulder 13 on which one on the other hand, valve spring 15 which is fixed to the housing attacks such that it engages the valve member 5 in the Valve seat 9 holds.
  • Valve member 5 is a valve piston enlarged in cross section 17, which for the axial actuation of the valve member 5 protrudes into a hydraulic working space 19 and this with its lower piston ring end face facing the valve seat 9 21 limited.
  • electrical actuators are also preferably designed as piezo actuators electrical actuators are provided, a first of which Actuator 23 via an axially adjacent first Adjusting piston 25 also in the hydraulic work space 19 protrudes.
  • first actuator 23 is a too this second actuator 27 arranged offset, the also with the interposition of a second Adjusting piston 29 projects into the hydraulic working space 19.
  • the hydraulic work space 19 is in three sub-rooms divided, of which a first sub-space 31 from the first adjusting piston 25, a second partial space 33 from the second adjusting piston 29 and a third subspace 35 from the valve piston 17 is limited.
  • the third subspace 35 is over each a throttle point 37 with the other two subspaces 31 and 33 connected.
  • the first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines works in the following way.
  • the adjusting pistons 25 and 29 are through the Return springs 41 in contact with the actuators 23 and 27 held so that in the hydraulic working space 19 only a stand pressure is built up.
  • This on the piston ring face 21 of the valve piston fixedly connected to the valve member 5 17 attacking in the opening direction of the valve member 5 Stand pressure is, however, less than the closing force the valve spring 15, which the valve member 5 with its valve sealing surface 7 sealingly on the valve seat 9 that the injection openings 11 from the valve sealing surface 7 be kept closed.
  • the actuators 23 and 27 are energized and extend in length.
  • the adjusting pistons 25 become more hydraulic in the direction Working space 19 moved so that the hydraulic medium the subspaces 31 and 33 via the throttling points 37 in the third subspace 35 is displaced.
  • There the inflowing takes hold hydraulic pressure medium on the end face 21 of the Valve piston 17 and moves it against the Closing force of the valve spring 15 in that facing away from the valve seat 9 Direction so that the valve member 5 from the valve seat 9th takes off and the flow cross-section between that with high pressure fuel filled blind hole 3 to the injection openings 11 releases.
  • This causes vibrations on the valve member 5 through a targeted step-like movement of the electrical Actuators 23 and 27 damped.
  • the axial expansion adjustment movement of the actuators 23 and 27 triggered gradually, with an actuator short each time is controlled after the second actuator.
  • the temporal Displacement of the adjustment movements of the actuators 23 and 27 to each other is about a few 10 ⁇ s.
  • the electric actuators 23 and 27 again de-energized so that they are back in very quickly return to their axially shortened starting position. This is done the actuation of the electric actuators 23 and 27 again with a slight time difference.
  • the respective Adjusting pistons 25 and 29 are by the force of Return springs 41 also in the direction of actuators 23, 27 moved back so that the volume in the hydraulic The workspace is quickly enlarged and the pressure is quickly reduced the closing pressure of the valve spring 15 drops. Consequently the valve member 5 is in again by the valve spring 15 System moved to the valve seat 9, so that the opening cross section closed again on the fuel injector and the injection is finished.
  • This avoidance of cavitation can also be caused by a delay in the reset speed of the electrical Actuators 23 and 27 and by increasing the system pressure in the hydraulic working space 19 well above the Vapor pressure of the hydraulic medium are supported.
  • the second embodiment shown in Figure 2 differs from the first one shown in FIG Embodiment in that now two hydraulic Working spaces are provided, which are by the valve piston 17th are so delimited from each other that they are the valve piston 17 of the valve member 5 each in the opposite direction of adjustment act upon.
  • the two are hydraulic Workspaces in a common cylindrical Chamber 43 arranged by the slidably guided therein Valve piston 17 in a first upper hydraulic work space 45 and a second lower hydraulic work space 47 is divided.
  • a first upper limit Valve piston face 49 the first upper hydraulic Working space 45 and a second lower valve piston end face 21 the second lower hydraulic working space 47 hydraulic work spaces 45 and 47 are each in two Sub-rooms divided, of which a sub-room on the adjusting piston 25, 29 of the electric actuator 23, 27 and another sub-space opens onto the valve piston 17 and the again connected to one another via a throttle cross section 37 are.
  • the second embodiment shown in Figure 2 works in the following way.
  • the fuel injector is the first actuator 23 axially extended. This can be done by feeding one Control voltage axially expanding piezo element to be energized or a contracting one under supply of a control voltage Piezo element to be de-energized.
  • the first actuator 23 becomes the first Adjusting piston 25 in the direction of the first hydraulic working space 45 moved, this adjustment movement of the first Adjusting piston 25 via the upper valve piston end face 49 of the adjusting piston 17 so transmitted to the valve member 5 is that this with its valve sealing surface 7 sealing in System is pressed against the valve seat surface 9.
  • the second Actuator 27 is when the fuel injector is closed switched so that it has its smallest axial extent having.
  • the second adjusting piston 29 is thereby Return spring 41 held in contact with the actuator 27 and is largely from the second lower hydraulic work space 47 dived.
  • the first actuator 23 is now switched so that it reduces its axial extent.
  • the second actuator 27 switched such that its axial extension increased, so that the second adjusting piston 29 from the second actuator 27 in the direction of the second lower hydraulic work space 47 is moved.
  • This Adjustment movement of the second adjusting piston 29 is hydraulic on the lower piston ring end face 21 of the adjusting piston 17 transmitted so that the valve member 5 from the valve seat 9 is lifted off and the injection cross section in the Releases the combustion chamber of the internal combustion engine.
  • the third exemplary embodiment of the fuel injection valve according to the invention shown in FIG. 3 differs from the second exemplary embodiment shown in FIG. 2 by the design of the valve piston 17, which is now formed in two parts.
  • a first upper piston part 61 delimits the upper hydraulic working space 45 with its upper valve piston end face 49, which acts on the valve member 5 in the closing direction.
  • a second lower piston part 63 of the valve piston 17 delimits, with its lower piston ring end face 21, the lower hydraulic working space 47, which acts in the opening direction on the valve member 5 of the inward opening fuel injection valve.
  • the two piston parts 61 and 63 can be brought into contact with one another at a certain distance from one another by a piston rod 65 which is preferably arranged on the upper piston part 61, with a preliminary stroke h v of the valve member 5 in over the free distance between the piston rod 65 and the lower piston part 63 Can open the opening direction.
  • the fuel injector shown in FIG. 3 without the actuators and the corresponding return springs of the adjusting pistons works analogously to the second exemplary embodiment.
  • the valve member 5 At the beginning of the opening stroke phase, when the second actuator 27 is displaced in the direction of the lower hydraulic working space 47, the valve member 5 first runs through a very rapid forward stroke path h v , in which only the force of the valve spring 15, not shown, has to be overpressed. After traveling through the preliminary stroke path h v , the lower valve piston part 63 comes into contact with the upper valve piston part 61 and now has to overcome a greater restoring force in the course of the further adjustment stroke movement.
  • the opening stroke curve of the valve member 5 following the pre-injection can be adjusted by the corresponding actuation of the first actuator 23 which actuates the first adjusting piston 25.
  • the hydraulic working spaces 45 and 47 are preferably separated from one another by the valve piston 17.

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

Abstract

The fuel injection valve has in a valve body (1) an axially sliding valve member (5) which has a sealing face (7) at one end. With this face it works together with a valve seating face (9) on the valve body to control an injection cross-section. From the seating face, at least one injection opening leads into the combustion chamber. There is an electrical control member (23) operating the valve member axially through a hydraulic working chamber (19). A second electrical control member (27) is provided to operate the valve member, controlled independently of the first one. The hydraulic working chamber is bounded by a valve piston (17) connected to the valve member and by adjusting pistons (25,29) connected to the control members.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einem solchen aus der DE 195 00 706 A1 bekannten Kraftstoffeinspritzventil ist ein kolbenförmiges Ventilglied axial verschiebbar in einem Ventilkörper angeordnet, der mit seinem freien Ende in den Brennraum der zu versorgenden Brennkraftmaschine ragt. Das Ventilglied weist dabei an seinem brennraumseitigen Ende eine Ventildichtfläche auf, mit der es zur Steuerung eines Einspritzquerschnittes mit einer Ventilsitzfläche am Ventilkörper zusammenwirkt, von der eine Einspritzöffnung in den Brennraum der Brennkraftmaschine abführt. Das Ventilglied wird von einem elektrischen Stellglied, vorzugsweise einem Piezoaktor axial betätigt, wobei die Stellbewegung des Piezoaktors über einen hydraulischen Arbeitsraum auf das Ventilglied übertragen wird. Dies hat dabei den Vorteil, daß z. B. temperaturabhängige Schwankungen des Piezoaktors ausgeglichen werden können und zudem die Stellbewegung des Piezoaktors in eine größere Stellbewegung des Ventilgliedes übersetzt werden kann. The invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out. In such a known from DE 195 00 706 A1 Fuel injection valve is a piston-shaped valve member axially slidably disposed in a valve body with its free end in the combustion chamber of the one to be supplied Internal combustion engine protrudes. The valve member points to his end on the combustion chamber side with a valve sealing surface which is used to control an injection cross section with a Valve seat surface cooperates on the valve body, one of which Injection opening leads into the combustion chamber of the internal combustion engine. The valve member is operated by an electrical actuator, preferably axially actuated a piezo actuator, wherein the actuating movement of the piezo actuator via a hydraulic Working space is transferred to the valve member. this has the advantage that z. B. temperature-dependent fluctuations of the piezo actuator can be compensated and also the Actuating movement of the piezo actuator in a larger actuating movement of the valve member can be translated.

Dabei weist das bekannte Kraftstoffeinspritzventil jedoch den Nachteil auf, daß es beim dynamischen Betrieb zu Überschwingungen und Prellern des Ventilgliedes kommen kann, die ein ungewolltes Öffnen des Einspritzventils zur Folge haben. Zudem werden bei dem bekannten Kraftstoffeinspritzventil Eigenschwingungen des Piezoaktors über den hydraulischen Verstärkerraum auf das Ventilglied übertragen, so daß auch dieses zu schwingen beginnt und somit den Einspritzverlauf verfälscht. Ein weiterer Nachteil des bekannten Kraftstoffeinspritzventils tritt bei der Rückstellbewegung des Piezoaktors auf, wobei durch die rasche Volumenvergrößerung des hydraulischen Arbeitsraumes der Druck des darin befindlichen Kraftstoffes unter den Dampfdruck sinken kann und somit Kavitationsschäden auftreten können.However, the known fuel injection valve the disadvantage that there are overshoots in dynamic operation and bouncing of the valve member can come result in an unwanted opening of the injection valve. In addition, natural vibrations occur in the known fuel injection valve of the piezo actuator via the hydraulic amplifier room transferred to the valve member, so that this too begins to oscillate and thus falsifies the injection process. Another disadvantage of the known fuel injection valve occurs during the reset movement of the piezo actuator on, with the rapid increase in volume of the hydraulic Working space the pressure of the inside Fuel can drop below the vapor pressure and thus cavitation damage may occur.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch die Verwendung eines zweiten elektrischen Stellgliedes eine sehr schnelle und direkte Ventilgliedbetätigung möglich ist, mit der sich der Einspritzöffnungsquerschnitt und somit der Einspritzverlauf am Kraftstoffeinspritzventil optimal über die Einspritzzeit formen läßt. Dabei erfolgt der mechanische bzw. Temperaturausgleich des Piezoaktors sowie die hydraulische Verstärkung der Verstellbewegung des Piezoaktors über einen hydraulischen Arbeitsraum. Dieser Arbeitsraum ist dabei in zwei Teilräume unterteilt, die jeweils durch einen Kolben des Piezoaktors und des Ventilgliedes begrenzt werden und die über eine Drosselstelle voneinander getrennt sind, so daß am Piezoaktor auftretende Schwingungen nicht auf das Ventilglied übertragen werden und ein Überschwingen bzw. Preller am Ventilglied selbst unterdrückt werden. Durch die Trennung von elektrischem Stellglied und dessen Verstellkolben wird zudem das Entstehen eines Unterdruckes bei schnellem Rückstellen der elektrischen Stellglieder vermieden, wobei diese dann vom Verstellkolben abheben. Besonders vorteilhaft ist die Verwendung von zwei in Gegenrichtung auf das Ventilglied wirkenden elektrischen Stellgliedern, da somit neben einem sehr schnellen und gesteuerten Öffnungshub auch der Schließhub des Ventilgliedes sehr rasch und gesteuert ausgeführt werden kann. Dabei kann durch die Verwendung dieser in Gegenrichtung wirkenden elektrischen Stellglieder auch eine Dämpfung des Ventilgliedes erreicht werden, da der zweite in Gegenrichtung zum ersten wirkende Aktor einen dynamischen Kräfteausgleich im hydraulischen Arbeitsraum bewirkt. Ein weiterer Vorteil wird durch die zweiteilige Ausbildung des mit dem Ventilglied verbundenen Ventilkolbens erreicht, bei der jeder Ventilkolbenteil einen in Gegenrichtung auf das Ventilglied wirkenden Arbeitsraum begrenzt. Dabei läßt sich durch einen vorgegebenen Abstand zwischen den beiden Kolbenteilen ein Vorhub am Ventilglied realisieren.The fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that the use a second electrical actuator a very fast and direct valve member actuation is possible with which is the cross section of the injection opening and thus the course of the injection on the fuel injection valve optimally over the Injection time forms. The mechanical one takes place or temperature compensation of the piezo actuator and the hydraulic Amplification of the adjustment movement of the piezo actuator via a hydraulic work area. This work space is included divided into two sub-rooms, each by one Pistons of the piezo actuator and the valve member are limited and which are separated from each other by a throttling point, so that vibrations occurring at the piezo actuator do not affect the Valve element are transmitted and an overshoot or Bouncers on the valve member itself are suppressed. Through the Separation of the electric actuator and its adjusting piston will also create a negative pressure at fast Resetting the electrical actuators avoided, whereby then lift them off the adjusting piston. Particularly advantageous is the use of two in the opposite direction the valve actuator acting electrical actuators, because thus in addition to a very fast and controlled opening stroke the closing stroke of the valve member is very quick and controlled can be executed. This can be done by using this electrical actuators acting in the opposite direction damping of the valve member can also be achieved since the second actuator acting in the opposite direction to the first one dynamic Equalization of forces in the hydraulic work area. Another advantage is the two-part training of the valve piston connected to the valve member reached, in which each valve piston part one in the opposite direction limited working space acting on the valve member. Here can be determined by a predetermined distance between the Realize a forward stroke on the valve member for both piston parts.

Durch eine gezielte stufenförmige Verstellbewegung der elektrischen Stellglieder ist es zudem möglich, ein Schwingen des Ventilgliedes zu unterdrücken bzw. zu dämpfen.Through a targeted step-like adjustment movement of the electrical Actuators are also able to swing to suppress or dampen the valve member.

Das elektrische Stellglied kann dabei alternativ als piezoelektrischer oder magnetostriktiver Aktor ausgebildet sein. Zudem kann das von den elektrischen Stellgliedern betägtigte Kraftstoffeinspritzventil als nach außen öffnendes Einspritzventils oder nach innen öffnendes Einspritzventil, z. B. Loch- oder Zapfendüse ausgebildet sein.The electrical actuator can alternatively as a piezoelectric or magnetostrictive actuator. In addition, that actuated by the electrical actuators Fuel injection valve as an outward opening injection valve or inward opening injection valve, e.g. B. hole or tenon nozzle.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar. Further advantages and advantageous configurations of the object the invention are the description, the drawing and the patent claims.

Zeichnungdrawing

Drei Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen die Figur 1 ein erstes Ausführungsbeispiel in einer vereinfachten Schemadarstellung, bei dem die beiden Piezoaktoren in gleicher Verstellrichtung über einen gemeinsamen hydraulischen Arbeitsraum auf das Ventilglied wirken, die Figur 2 ein zweites Ausführungsbeispiel, bei dem die beiden elektrischen Stellglieder in jeweils entgegengesetzter Verstellrichtung über einen gemeinsamen hydraulischen Arbeitsraum am Ventilglied des Kraftstoffeinspritzventils angreifen, und die Figur 3 ein drittes Ausführungsbeispiel analog zur Darstellung der Figur 2, bei dem jedem elektrischen Stellglied ein separater hydraulischer Arbeitsraum zum Ventilglied zugeordnet ist.Three embodiments of the fuel injection valve according to the invention for internal combustion engines are in the drawing are shown and are described in the following description explained in more detail. 1 shows a first embodiment in a simplified schematic representation, in which the two piezo actuators in the same direction of adjustment via a common hydraulic work area on the Valve member act, Figure 2 shows a second embodiment, in which the two electrical actuators in each opposite direction of adjustment via a common hydraulic working space on the valve member of the fuel injector attack, and Figure 3 a third Embodiment analogous to the representation of Figure 2, at a separate hydraulic one for each electric actuator Working space is assigned to the valve member.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Das in der Figur 1 in einer vereinfachten Schemadarstellung gezeigte erste Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen weist einen Ventilkörper 1 auf, der mit seinem unteren freien Ende in den nicht näher dargestellten Brennraum der zu versorgenden Brennkraftmaschine ragt. Im Ventilkörper 1 ist eine axiale Sackbohrung 3 vorgesehen, in die eine nicht gezeigte, von einer Kraftstoffeinspritzpumpe abführende Einspritzleitung mündet. Desweiteren ist im Ventilkörper 1 ein kolbenförmiges Ventilglied 5 axial verschiebbar angeordnet, das an seinem unteren, brennraumnahen Ende eine Ventildichtfläche 7 aufweist, mit der es zur Steuerung eines Einspritzquerschnittes mit einer Ventilsitzfläche 9 am Ventilkörper 1 zusammenwirkt, die am geschlossenen Ende der Sackbohrung 3 gebildet ist. Dabei führen von der Ventilsitzfläche 9 zwei Einspritzöffnungen 11 in den Brennraum der zu versorgenden Brennkraftmaschine ab. Das Ventilglied 5 verringert an seinem der Ventildichtfläche 7 abgewandten Ende seinen Querschnitt unter Bildung einer Ringschulter 13, an der eine sich andererseits gehäusefest abstützende Ventilfeder 15 derart angreift, daß sie das Ventilglied 5 in Anlage an der Ventilsitzfläche 9 hält.1 in a simplified schematic representation shown first embodiment of the invention Fuel injection valve for internal combustion engines has one Valve body 1 on, with its lower free end in the combustion chamber, not shown, to be supplied Internal combustion engine protrudes. In the valve body 1 is one axial blind hole 3 is provided, in which a not shown injection line leading away from a fuel injection pump flows. Furthermore, a piston-shaped is in the valve body 1 Valve member 5 is arranged axially displaceable a valve sealing surface 7 at its lower end near the combustion chamber with which it is used to control an injection cross section cooperates with a valve seat surface 9 on the valve body 1, formed at the closed end of the blind hole 3 is. Two lead from the valve seat 9 Injection openings 11 in the combustion chamber to be supplied Internal combustion engine. The valve member 5 reduces at its the end facing away from the valve sealing surface 7 has its cross section forming an annular shoulder 13 on which one on the other hand, valve spring 15 which is fixed to the housing attacks such that it engages the valve member 5 in the Valve seat 9 holds.

An seinem der Ventildichtfläche 7 abgewandten Ende weist das Ventilglied 5 einen im Querschnitt vergrößerten Ventilkolben 17 auf, der zur axialen Betätigung des Ventilgliedes 5 in einen hydraulischen Arbeitsraum 19 ragt und diesen mit seiner unteren, dem Ventilsitz 9 zugewandten Kolbenringstirnfläche 21 begrenzt. Zur Betätigung des Ventilgliedes 5 sind weiterhin zwei vorzugsweise als Piezoaktoren ausgebildete elektrische Stellglieder vorgesehen, von denen ein erstes Stellglied 23 über einen axial daran anliegenden ersten Verstellkolben 25 ebenfalls in den hydraulischen Arbeitsraum 19 ragt. Zusätzlich zum ersten Stellglied 23 ist ein zu diesem versetzt angeordnetes zweites Stellglied 27 vorgesehen, das ebenfalls unter Zwischenschaltung eines zweiten Verstellkolbens 29 in den hydraulischen Arbeitsraum 19 ragt. Dabei ist der hydraulische Arbeitsraum 19 in drei Teilräume unterteilt, von denen ein erster Teilraum 31 vom ersten Verstellkolben 25, ein zweiter Teilraum 33 vom zweiten Verstellkolben 29 und ein dritter Teilraum 35 vom Ventilkolben 17 begrenzt ist. Dabei ist der dritte Teilraum 35 über jeweils eine Drosselstelle 37 mit den beiden anderen Teilräumen 31 und 33 verbunden.At its end facing away from the valve sealing surface 7, this has Valve member 5 is a valve piston enlarged in cross section 17, which for the axial actuation of the valve member 5 protrudes into a hydraulic working space 19 and this with its lower piston ring end face facing the valve seat 9 21 limited. To actuate the valve member 5 are also preferably designed as piezo actuators electrical actuators are provided, a first of which Actuator 23 via an axially adjacent first Adjusting piston 25 also in the hydraulic work space 19 protrudes. In addition to the first actuator 23 is a too this second actuator 27 arranged offset, the also with the interposition of a second Adjusting piston 29 projects into the hydraulic working space 19. The hydraulic work space 19 is in three sub-rooms divided, of which a first sub-space 31 from the first adjusting piston 25, a second partial space 33 from the second adjusting piston 29 and a third subspace 35 from the valve piston 17 is limited. The third subspace 35 is over each a throttle point 37 with the other two subspaces 31 and 33 connected.

Für eine sichere ständige Anlage der Verstellkolben 25 und 29 an den elektrischen Stellgliedern 23 und 27 sind zwischen den Verstellkolben 25 und 29 und dem diese führenden Gehäuse Rückstellfedern 41 eingespannt, die die Verstellkolben 25 und 29 in vom hydraulischen Arbeitsraum 19 abgewandter Richtung beaufschlagen und diese so in ständiger Anlage an den elektrischen Stellgliedern 23 und 27 halten.For a safe permanent system of the adjusting pistons 25 and 29 on the electric actuators 23 and 27 are between the adjusting pistons 25 and 29 and the housing that guides them Return springs 41 clamped, which the adjusting piston 25th and 29 in the direction facing away from the hydraulic working space 19 act and so this in constant attachment to the hold electric actuators 23 and 27.

Das in der Figur 1 dargestellte erste Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen arbeitet in folgender Weise. In Ausgangslage des geschlossenen Kraftstoffeinspritzventils sind die als Piezoaktoren ausgebildeten elektrischen Stellglieder 23 und 27 stromlos geschalten und weisen ihre kleinste axiale Erstreckung auf. Die Verstellkolben 25 und 29 sind durch die Rückstellfedern 41 in Anlage an den Stellgliedern 23 und 27 gehalten, so daß im hydraulischen Arbeitsraum 19 lediglich ein Standdruck aufgebaut ist. Dieser an der Kolbenringstirnfläche 21 des fest mit dem Ventilglied 5 verbundenen Ventilkolben 17 in Öffnungsrichtung des Ventilgliedes 5 angreifende Standdruck ist dabei jedoch kleiner als die Schließkraft der Ventilfeder 15, die das Ventilglied 5 mit seiner Ventildichtfläche 7 dichtend an der Ventilsitzfläche 9 hält, so daß die Einspritzöffnungen 11 von der Ventildichtfläche 7 verschlossen gehalten werden. Soll eine Einspritzung am Kraftstoffeinspritzventil erfolgen, werden die Stellglieder 23 und 27 bestromt und dehnen sich in ihrer Länge aus. Dabei werden die Verstellkolben 25 in Richtung hydraulischer Arbeitsraum 19 verschoben, so daß das Hydraulikmedium aus den Teilräumen 31 und 33 über die Drosselstellen 37 in den dritten Teilraum 35 verdrängt wird. Dort greift das zuströmende hydraulische Druckmittel an der Stirnfläche 21 des Ventilkolbens 17 an und verschiebt diesen entgegen der Schließkraft der Ventilfeder 15 in die vom Ventilsitz 9 abgewandte Richtung, so daß das Ventilglied 5 vom Ventilsitz 9 abhebt und den Durchströmquerschnitt zwischen der mit Hochdruckkraftstoff gefüllten Sackbohrung 3 zu den Einspritzöffnungen 11 freigibt. Dabei werden Schwingungen am Ventilglied 5 durch eine gezielte stufenförmige Bewegung der elektrischen Stellglieder 23 und 27 gedämpft. Dazu wird die axiale Ausdehnungsstellbewegung der Stellglieder 23 und 27 stufenweise ausgelöst, wobei ein Stellglied jeweils kurz nach dem zweiten Stellglied angesteuert wird. Die zeitliche Verschiebung der Verstellbewegungen der Stellglieder 23 und 27 zueinander beträgt dabei etwa einige 10 µs.The first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines works in the following way. In the starting position of the closed fuel injector are the as Piezoactuators trained electrical actuators 23 and 27 de-energized and have their smallest axial extent on. The adjusting pistons 25 and 29 are through the Return springs 41 in contact with the actuators 23 and 27 held so that in the hydraulic working space 19 only a stand pressure is built up. This on the piston ring face 21 of the valve piston fixedly connected to the valve member 5 17 attacking in the opening direction of the valve member 5 Stand pressure is, however, less than the closing force the valve spring 15, which the valve member 5 with its valve sealing surface 7 sealingly on the valve seat 9 that the injection openings 11 from the valve sealing surface 7 be kept closed. Should an injection on Fuel injection valve, the actuators 23 and 27 are energized and extend in length. The adjusting pistons 25 become more hydraulic in the direction Working space 19 moved so that the hydraulic medium the subspaces 31 and 33 via the throttling points 37 in the third subspace 35 is displaced. There the inflowing takes hold hydraulic pressure medium on the end face 21 of the Valve piston 17 and moves it against the Closing force of the valve spring 15 in that facing away from the valve seat 9 Direction so that the valve member 5 from the valve seat 9th takes off and the flow cross-section between that with high pressure fuel filled blind hole 3 to the injection openings 11 releases. This causes vibrations on the valve member 5 through a targeted step-like movement of the electrical Actuators 23 and 27 damped. For this, the axial expansion adjustment movement of the actuators 23 and 27 triggered gradually, with an actuator short each time is controlled after the second actuator. The temporal Displacement of the adjustment movements of the actuators 23 and 27 to each other is about a few 10 µs.

Zur Beendigung des Einspritzvorganges am Kraftstoffeinspritzventil werden die elektrischen Stellglieder 23 und 27 erneut stromlos geschaltet, so daß sie wieder sehr rasch in ihre axial verkürzte Ausgangslage zurückkehren. Dabei erfolgt das Ansteuern der elektrischen Stellglieder 23 und 27 erneut mit einer geringen zeitlichen Verschiebung. Die jeweiligen Verstellkolben 25 und 29 werden durch die Kraft der Rückstellfedern 41 ebenfalls in Richtung Stellglieder 23, 27 zurückverschoben, so daß sich das Volumen im hydraulischen Arbeitsraum rasch vergrößert und der Druck somit schnell unter den Schließdruck der Ventilfeder 15 absinkt. Infolgedessen wird das Ventilglied 5 von der Ventilfeder 15 erneut in Anlage an den Ventilsitz 9 verschoben, so daß der Öffnungsquerschnitt am Kraftstoffeinspritzventil wieder verschlossen und die Einspritzung beendet ist. Dabei wird durch die Trennung der Verstellkolben 25, 29 von den elektrischen Stellgliedern 23 und 27 die Rückstellbewegung der Verstellkolben 25 und 29 derart verzögert, daß der Druck im hydraulischen Arbeitsraum nicht unter den Dampfdruck abfällt und somit keine Kavitationsschäden auslösende Unterdruckgebiete entstehen. Diese Vermeidung von Kavitation kann zudem durch eine Verzögerung der Rückstellgeschwindigkeit der elektrischen Stellglieder 23 und 27 und durch eine Erhöhung des Systemdruckes im hydraulischen Arbeitsraum 19 weit über den Dampfdruck des hydraulischen Mediums unterstützt werden.To end the injection process on the fuel injector the electric actuators 23 and 27 again de-energized so that they are back in very quickly return to their axially shortened starting position. This is done the actuation of the electric actuators 23 and 27 again with a slight time difference. The respective Adjusting pistons 25 and 29 are by the force of Return springs 41 also in the direction of actuators 23, 27 moved back so that the volume in the hydraulic The workspace is quickly enlarged and the pressure is quickly reduced the closing pressure of the valve spring 15 drops. Consequently the valve member 5 is in again by the valve spring 15 System moved to the valve seat 9, so that the opening cross section closed again on the fuel injector and the injection is finished. In doing so, the separation the adjusting piston 25, 29 from the electrical actuators 23 and 27 the return movement of the adjusting piston 25 and 29 delayed such that the pressure in the hydraulic Work space does not drop below the steam pressure and thus no negative pressure areas causing cavitation damage arise. This avoidance of cavitation can also be caused by a delay in the reset speed of the electrical Actuators 23 and 27 and by increasing the system pressure in the hydraulic working space 19 well above the Vapor pressure of the hydraulic medium are supported.

Das in der Figur 2 dargestellte zweite Ausführungsbeispiel unterscheidet sich vom in der Figur 1 dargestellten ersten Ausführungsbeispiel dadurch, daß nunmehr zwei hydraulische Arbeitsräume vorgesehen sind, die durch den Ventilkolben 17 derart voneinander abgegrenzt sind, daß sie den Ventilkolben 17 des Ventilgliedes 5 jeweils in entgegengesetzter Verstellrichtung beaufschlagen. Dazu sind die zwei hydraulischen Arbeitsräume in einer gemeinsamen zylinderförmigen Kammer 43 angeordnet, die durch den gleitend darin geführten Ventilkolben 17 in einen ersten oberen hydraulischen Arbeitsraum 45 und einen zweiten unteren hydraulischen Arbeitsraum 47 unterteilt ist. Dabei begrenzt eine erste obere Ventilkolbenstirnfläche 49 den ersten oberen hydraulischen Arbeitsraum 45 und eine zweite untere Ventilkolbenstirnfläche 21 den zweiten unteren hydraulischen Arbeitsraum 47. Die hydraulischen Arbeiträume 45 und 47 sind jeweils in zwei Teilräume unterteilt, von denen je ein Teilraum an den Verstellkolben 25, 29 des elektrischen Stellgliedes 23, 27 und ein anderer Teilraum an den Ventilkolben 17 mündet und die wiederum über einen Drosselquerschnitt 37 miteinander verbunden sind.The second embodiment shown in Figure 2 differs from the first one shown in FIG Embodiment in that now two hydraulic Working spaces are provided, which are by the valve piston 17th are so delimited from each other that they are the valve piston 17 of the valve member 5 each in the opposite direction of adjustment act upon. The two are hydraulic Workspaces in a common cylindrical Chamber 43 arranged by the slidably guided therein Valve piston 17 in a first upper hydraulic work space 45 and a second lower hydraulic work space 47 is divided. A first upper limit Valve piston face 49 the first upper hydraulic Working space 45 and a second lower valve piston end face 21 the second lower hydraulic working space 47 hydraulic work spaces 45 and 47 are each in two Sub-rooms divided, of which a sub-room on the adjusting piston 25, 29 of the electric actuator 23, 27 and another sub-space opens onto the valve piston 17 and the again connected to one another via a throttle cross section 37 are.

Das in der Figur 2 dargestellte zweite Ausführungsbeispiel arbeitet in folgender Weise. In Ausgangslage bei geschlossenem Kraftstoffeinspritzventil ist das erste Stellglied 23 axial ausgedehnt. Dazu kann ein sich unter Zuführung einer Steuerspannung axial ausdehnendes Piezoelement bestromt sein oder ein sich unter Zuführung einer Steuerspannung zusammenziehendes Piezoelement stromlos geschaltet sein. Durch die axiale Ausdehnung des ersten Stellgliedes 23 wird der erste Verstellkolben 25 in Richtung erster hydraulischer Arbeitsraum 45 verschoben, wobei diese Verstellbewegung des ersten Verstellkolbens 25 über die obere Ventilkolbenstirnfläche 49 des Verstellkolbens 17 so auf das Ventilglied 5 übertragen wird, daß dieses mit seiner Ventildichtfläche 7 dichtend in Anlage an die Ventilsitzfläche 9 gepreßt wird. Das zweite Stellglied 27 ist bei geschlossenem Kraftstoffeinspritzventil so geschaltet, daß es seine kleinste axiale Erstreckung aufweist. Der zweite Verstellkolben 29 wird dabei durch die Rückstellfeder 41 in Anlage am Stellglied 27 gehalten und ist weitgehend aus dem zweiten unteren hydraulischen Arbeitsraum 47 ausgetaucht.The second embodiment shown in Figure 2 works in the following way. In the starting position with the door closed The fuel injector is the first actuator 23 axially extended. This can be done by feeding one Control voltage axially expanding piezo element to be energized or a contracting one under supply of a control voltage Piezo element to be de-energized. Through the axial extension of the first actuator 23 becomes the first Adjusting piston 25 in the direction of the first hydraulic working space 45 moved, this adjustment movement of the first Adjusting piston 25 via the upper valve piston end face 49 of the adjusting piston 17 so transmitted to the valve member 5 is that this with its valve sealing surface 7 sealing in System is pressed against the valve seat surface 9. The second Actuator 27 is when the fuel injector is closed switched so that it has its smallest axial extent having. The second adjusting piston 29 is thereby Return spring 41 held in contact with the actuator 27 and is largely from the second lower hydraulic work space 47 dived.

Soll eine Einspritzung am Kraftstoffeinspritzventil erfolgen, wird nunmehr das erste Stellglied 23 so geschaltet, daß es seine axiale Erstreckung verringert. Gleichzeitig wird das zweite Stellglied 27 derart geschaltet, daß sich seine axiale Erstreckung vergrößert, so daß der zweite Verstellkolben 29 vom zweiten Stellglied 27 in Richtung zweiter unterer hydraulischer Arbeitsraum 47 verschoben wird. Diese Stellbewegung des zweiten Verstellkolbens 29 wird hydraulisch auf die untere Kolbenringstirnfläche 21 des Verstellkolbens 17 übertragen, so daß das Ventilglied 5 vom Ventilsitz 9 abgehoben wird und den Einspritzquerschnitt in den Brennraum der Brennkraftmaschine freigibt. Um dabei Schwingungen am Ventilglied 5 zu vermeiden kann die Verstellung des Ventilgliedes erneut durch ein stufenweises Ansteuern der Stellglieder 23 und 27 erfolgen, wobei der in Schließrichtung wirkende Verstellkolben 25 jeweils kurzzeitig vom Stellglied 23 in seiner Lage fixiert wird und so kurzzeitig eine dämpfende Gegenkraft aufbaut. Dabei werden zudem durch den Drosseleffekt an den Drosselstellen 37 die Übertragung von Eigenschwingungen der Stellglieder 23 und 27 gedämpft.If the fuel injection valve is to be injected, the first actuator 23 is now switched so that it reduces its axial extent. At the same time the second actuator 27 switched such that its axial extension increased, so that the second adjusting piston 29 from the second actuator 27 in the direction of the second lower hydraulic work space 47 is moved. This Adjustment movement of the second adjusting piston 29 is hydraulic on the lower piston ring end face 21 of the adjusting piston 17 transmitted so that the valve member 5 from the valve seat 9 is lifted off and the injection cross section in the Releases the combustion chamber of the internal combustion engine. To make vibrations on the valve member 5 can avoid the adjustment of the valve member again by a stepwise control the actuators 23 and 27 take place, the in the closing direction acting adjusting piston 25 each for a short time from Actuator 23 is fixed in its position and so briefly builds a damping counterforce. In addition, through the throttling effect at the throttling points 37 the transmission damped by natural vibrations of the actuators 23 and 27.

Das in der Figur 3 dargestellte dritte Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils unterscheidet sich zum in der Figur 2 dargestellten zweiten Ausführungsbeispiel durch die Ausbildung des Ventilkolbens 17, der nunmehr zweiteilig ausgebildet ist. Dabei begrenzt ein erster oberer Kolbenteil 61 mit seiner oberen Ventilkolbenstirnfläche 49 den oberen hydraulischen Arbeitsraum 45, der in Schließrichtung auf das Ventilglied 5 wirkt. Ein zweiter unterer Kolbenteil 63 des Ventilkolbens 17 begrenzt mit seiner unteren Kolbenringstirnfläche 21 den unteren hydraulischen Arbeitsraum 47, der in Öffnungsrichtung auf das Ventilglied 5 des nach innen öffnenden Kraftstoffeinspritzventils wirkt. Die beiden Kolbenteile 61 und 63 sind durch eine vorzugsweise am oberen Kolbenteil 61 angeordnete Kolbenstange 65 in einem bestimmten Abstand zueinander miteinander in Anlage bringbar, wobei sich über den freien Abstand zwischen der Kolbenstange 65 und dem unteren Kolbenteil 63 ein Vorhub hv des Ventilgliedes 5 in Öffnungsrichtung einstellen läßt.The third exemplary embodiment of the fuel injection valve according to the invention shown in FIG. 3 differs from the second exemplary embodiment shown in FIG. 2 by the design of the valve piston 17, which is now formed in two parts. A first upper piston part 61 delimits the upper hydraulic working space 45 with its upper valve piston end face 49, which acts on the valve member 5 in the closing direction. A second lower piston part 63 of the valve piston 17 delimits, with its lower piston ring end face 21, the lower hydraulic working space 47, which acts in the opening direction on the valve member 5 of the inward opening fuel injection valve. The two piston parts 61 and 63 can be brought into contact with one another at a certain distance from one another by a piston rod 65 which is preferably arranged on the upper piston part 61, with a preliminary stroke h v of the valve member 5 in over the free distance between the piston rod 65 and the lower piston part 63 Can open the opening direction.

Das in der Figur 3 ohne die Stellglieder und die entsprechenden Rückstellfedern der Verstellkolben dargestellte Kraftstoffeinspritzventil arbeitet analog zum zweiten Ausführungsbeispiel. Dabei durchläuft das Ventilglied 5 zu Beginn der Öffnungshubphase bei Verschieben des zweiten Stellgliedes 27 in Richtung unterer hydraulischer Arbeitsraum 47 zunächst einen sehr raschen Vorhubweg hv, bei dem lediglich die Kraft der nicht dargestellten Ventilfeder 15 überdrückt werden muß. Nach Durchfahren des Vorhubweges hv gelangt der untere Ventilkolbenteil 63 in Anlage an den oberen Ventilkolbenteil 61 und hat nunmehr im Verlauf der weiteren Verstellhubbewegung eine größere Rückstellkraft zu überwinden. Dabei kann der sich an die Voreinspritzung anschließende Öffnungshubverlauf des Ventilgliedes 5 durch die entsprechende Ansteuerung des den ersten Verstellkolben 25 betätigende erste Stellglied 23 eingestellt werden. Um dabei eine gegenseitige Beeinflussung der Stellbewegung der Kolbenteile 61 und 63 zu vermeiden, sind die hydraulischen Arbeitsräume 45 und 47 durch den Ventilkolben 17 vorzugsweise voneinander getrennt.The fuel injector shown in FIG. 3 without the actuators and the corresponding return springs of the adjusting pistons works analogously to the second exemplary embodiment. At the beginning of the opening stroke phase, when the second actuator 27 is displaced in the direction of the lower hydraulic working space 47, the valve member 5 first runs through a very rapid forward stroke path h v , in which only the force of the valve spring 15, not shown, has to be overpressed. After traveling through the preliminary stroke path h v , the lower valve piston part 63 comes into contact with the upper valve piston part 61 and now has to overcome a greater restoring force in the course of the further adjustment stroke movement. The opening stroke curve of the valve member 5 following the pre-injection can be adjusted by the corresponding actuation of the first actuator 23 which actuates the first adjusting piston 25. In order to avoid mutual influencing of the actuating movement of the piston parts 61 and 63, the hydraulic working spaces 45 and 47 are preferably separated from one another by the valve piston 17.

Claims (9)

Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem in einem Ventilkörper (1) axial verschiebbaren Ventilglied (5), das an seinem einen Ende eine Ventildichtfläche (7) aufweist, mit der es zur Steuerung eines Einspritzquerschnittes mit einer Ventilsitzfläche (9) am Ventilkörper (1) zusammenwirkt, von der wenigstens eine Einspritzöffnung (11) in den Brennraum der zu versorgenden Brennkraftmaschine abführt und mit einem das Ventilglied (5) axial betätigenden elektrischen Stellglied (23), das über einen hydraulischen Arbeitsraum (19) auf das Ventilglied (5) wirkt, dadurch gekennzeichnet, daß ein zweites elektrisches Stellglied 27 zur Betätigung des Ventilgliedes (5) vorgesehen ist, das unabhängig vom ersten elektrischen Stellglied (23) ansteuerbar ist.Fuel injection valve for internal combustion engines with one in a valve body (1) axially displaceable valve member (5) that has a valve sealing surface at one end (7) with which it is used to control an injection cross section with a valve seat surface (9) on the valve body (1) cooperates, of which at least one injection opening (11) in the combustion chamber of the supply Removes internal combustion engine and with a valve member (5) axially actuating electrical actuator (23) which a hydraulic working space (19) on the valve member (5) acts, characterized in that a second electrical Actuator 27 is provided for actuating the valve member (5) is independent of the first electrical actuator (23) can be controlled. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der hydraulische Arbeitsraum (19) durch einen mit dem Ventilglied (5) verbundenen Ventilkolben (17) und durch mit den elektrischen Stellgliedern (23, 27) verbundene Verstellkolben (25, 29) begrenzt ist, wobei die an die Verstellkolben (25, 29) und den Ventilkolben (17) angrenzenden Räume des hydraulischen Arbeitsraumes (19) jeweils Teilräume (31, 33, 35) bilden, die durch Drosselquerschnitte (37) voneinander abgeteilt sind. Fuel injection valve according to claim 1, characterized in that that the hydraulic working space (19) through a valve piston (17) connected to the valve member (5) and connected to the electric actuators (23, 27) Adjusting piston (25, 29) is limited, the at the adjusting pistons (25, 29) and the valve piston (17) adjoining Rooms of the hydraulic work space (19) each Form subspaces (31, 33, 35) through throttle cross sections (37) are divided from each other. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der Ventilkolben (17) direkt am Ventilglied (5) befestigt ist und daß die Verstellkolben (25, 29) mittels Rückstellfedern (41) mit ihren, den hydraulischen Teilräumen (31, 33) abgewandten Stirnflächen in Anlage an den jeweiligen elektrischen Stellgliedern (23, 27) gehalten werden.Fuel injection valve according to claim 2, characterized in that that the valve piston (17) directly on the valve member (5) is fixed and that the adjusting pistons (25, 29) by means of return springs (41) with their hydraulic ones Partial spaces (31, 33) facing away from end faces in the system the respective electrical actuators (23, 27) held will. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die elektrischen Stellglieder (23, 27) als Piezoaktoren ausgebildet sind.Fuel injection valve according to claim 1, characterized in that that the electrical actuators (23, 27) as Piezo actuators are formed. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß das erste und zweite Stellglied (23, 27) in gleicher Verstellrichtung über den hydraulischen Arbeitsraum (19) am Ventilkolben (17) des Ventilgliedes (5) angreifen.Fuel injection valve according to claim 2, characterized in that that the first and second actuators (23, 27) in the same direction of adjustment via the hydraulic work area (19) on the valve piston (17) of the valve element (5). Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß zwei hydraulische Arbeitsräume (45, 47) vorgesehen sind, die durch den Ventilkolben (17) derart voneinander abgegrenzt sind, daß sie das Ventilglied (5) jeweils in entgegensetzter Verstellrichtung beaufschlagen.Fuel injection valve according to claim 2, characterized in that that two hydraulic work spaces (45, 47) are provided which are separated from each other by the valve piston (17) are delimited that they the valve member (5) each Act in the opposite direction of adjustment. Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß die zwei hydraulischen Arbeitsräume (45, 47) in einer gemeinsamen zylinderförmigen Kammer (43) angeordnet sind, die durch den gleitend darin geführten Ventilkolben (17) in einen ersten oberen und einen zweiten unteren hydraulischen Arbeitsraum (45, 47) unterteilt ist, wobei eine erste obere Ventilkolbenstirnfläche (49) den ersten oberen Arbeitsraum (45) und eine zweite untere Ventilkolbenstirnfläche (21) den zweiten unteren Arbeitsraum (47) begrenzt. Fuel injection valve according to Claim 6, characterized in that that the two hydraulic work rooms (45, 47) arranged in a common cylindrical chamber (43) are caused by the sliding valve piston inside (17) into a first upper and a second lower hydraulic work space (45, 47) is divided, one first upper valve piston face (49) the first upper Work space (45) and a second lower valve piston face (21) limits the second lower working space (47). Kraftstoffeinspritzventil nach Anspruch 7, dadurch gekennzeichnet, daß die hydraulischen Arbeitsräume (45, 47) jeweils in zwei Teilräume unterteilt sind, von denen je ein Teilraum an den Verstellkolben (25, 29) des elektrischen Stellgliedes (23, 27) und ein anderer Teilraum an den Ventilkolben (17) mündet und die über einen Drosselquerschnitt miteinander verbunden sind.Fuel injection valve according to claim 7, characterized in that that the hydraulic working spaces (45, 47) are each divided into two sub-rooms, one of each Subspace on the adjusting piston (25, 29) of the electrical Actuator (23, 27) and another subspace on the valve piston (17) opens out through a throttle cross-section are interconnected. Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß der Ventilkolben (17) zweiteilig ausgebildet ist und mit einem ersten oberen Kolbenteil (61) einen ersten oberen hydraulischen Arbeitsraum (45) und mit einem zweiten unteren Kolbenteil (63) einen zweiten unteren hydraulischen Arbetisraum (47) begrenzt, wobei die Kolbenteile (61, 63) vorzugsweise über eine an einem Kolbenteil befestigte Kolbenstange (65) miteinander in Anlage bringbar sind.Fuel injection valve according to Claim 6, characterized in that that the valve piston (17) is in two parts and with a first upper piston part (61) first upper hydraulic work space (45) and with a second lower piston part (63) a second lower hydraulic Working space (47) limited, the piston parts (61, 63) preferably via one attached to a piston part Piston rod (65) can be brought into contact with each other are.
EP97120314A 1997-03-10 1997-11-20 Fuel injection valve for internal combustion engines Expired - Lifetime EP0864743B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19709795 1997-03-10
DE19709795A DE19709795A1 (en) 1997-03-10 1997-03-10 Fuel injection valve for internal combustion engines

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EP0864743A2 true EP0864743A2 (en) 1998-09-16
EP0864743A3 EP0864743A3 (en) 2001-08-08
EP0864743B1 EP0864743B1 (en) 2003-06-11

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JP (1) JPH10252598A (en)
DE (2) DE19709795A1 (en)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000017508A1 (en) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Fuel injection valve
WO2000017510A1 (en) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Fuel injection valve
WO2001029403A1 (en) * 1999-10-21 2001-04-26 Robert Bosch Gmbh Fuel injection valve
WO2002053958A1 (en) * 2001-01-05 2002-07-11 Robert Bosch Gmbh Valve for controlling liquids
EP1167746A3 (en) * 2000-06-22 2003-12-10 Nippon Soken, Inc. Fuel injection device
DE10333427B3 (en) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Fuel injection system for internal combustion engine receives high-pressure fuel from common rail which passes to injection valve and working space under piston
DE10333693B3 (en) * 2003-07-24 2004-09-30 Robert Bosch Gmbh Fuel injection device for an internal combustion engine comprises a filling chamber arranged between two pistons and connected to a feed line
DE10333573B3 (en) * 2003-07-24 2004-11-18 Robert Bosch Gmbh Fuel injection arrangement has hydraulic coupler piston(s) with central fill volume connected to guide gap and to fuel feed line, one piston fixed to actuator and one to valve needle via piston rod
WO2005026531A1 (en) * 2003-09-10 2005-03-24 Siemens Aktiengesellschaft Injection valve for injecting fuel into an internal combustion engine
WO2006128751A1 (en) * 2005-05-30 2006-12-07 Robert Bosch Gmbh Common rail injector
EP2500550A1 (en) * 2011-03-16 2012-09-19 Siemens Aktiengesellschaft Stroke transmitter for gas turbine
WO2013087475A1 (en) * 2011-12-12 2013-06-20 Continental Automotive Gmbh Injection valve
WO2015044420A2 (en) * 2013-09-27 2015-04-02 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
WO2016045989A1 (en) * 2014-09-26 2016-03-31 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
CN110440046A (en) * 2019-09-06 2019-11-12 厦门赛尔特电子有限公司 A kind of liquid transmitting stroke amplifying type Piezoelectric switches valve

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JP5024322B2 (en) * 2009-03-25 2012-09-12 株式会社デンソー Fuel injection valve
JP5024321B2 (en) * 2009-03-25 2012-09-12 株式会社デンソー Fuel injection valve
JP5024320B2 (en) * 2009-03-25 2012-09-12 株式会社デンソー Fuel injection valve
KR101314991B1 (en) * 2012-01-25 2013-10-04 홍종한 Piezo injector for vehicle
US20160377040A1 (en) * 2015-06-24 2016-12-29 Great Plains Diesel Technologies, L.C. Fuel injection rate modulation by magnetostrictive actuator and fluidomechanical coupler
GB2560513A (en) * 2017-03-13 2018-09-19 Ap Moeller Maersk As Fuel injection system

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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000017508A1 (en) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Fuel injection valve
WO2000017510A1 (en) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Fuel injection valve
US6460779B1 (en) 1998-09-23 2002-10-08 Robert Bosch Gmbh Fuel injection valve
WO2001029403A1 (en) * 1999-10-21 2001-04-26 Robert Bosch Gmbh Fuel injection valve
US6685105B1 (en) 1999-10-21 2004-02-03 Robert Bosch Gmbh Fuel injection valve
EP1167746A3 (en) * 2000-06-22 2003-12-10 Nippon Soken, Inc. Fuel injection device
WO2002053958A1 (en) * 2001-01-05 2002-07-11 Robert Bosch Gmbh Valve for controlling liquids
DE10333427B3 (en) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Fuel injection system for internal combustion engine receives high-pressure fuel from common rail which passes to injection valve and working space under piston
DE10333693B3 (en) * 2003-07-24 2004-09-30 Robert Bosch Gmbh Fuel injection device for an internal combustion engine comprises a filling chamber arranged between two pistons and connected to a feed line
DE10333573B3 (en) * 2003-07-24 2004-11-18 Robert Bosch Gmbh Fuel injection arrangement has hydraulic coupler piston(s) with central fill volume connected to guide gap and to fuel feed line, one piston fixed to actuator and one to valve needle via piston rod
WO2005026531A1 (en) * 2003-09-10 2005-03-24 Siemens Aktiengesellschaft Injection valve for injecting fuel into an internal combustion engine
WO2006128751A1 (en) * 2005-05-30 2006-12-07 Robert Bosch Gmbh Common rail injector
EP2500550A1 (en) * 2011-03-16 2012-09-19 Siemens Aktiengesellschaft Stroke transmitter for gas turbine
WO2012123264A1 (en) * 2011-03-16 2012-09-20 Siemens Aktiengesellschaft Stroke transmitter for gas turbine
CN103459808A (en) * 2011-03-16 2013-12-18 西门子公司 Stroke transmitter for gas turbine
CN103459808B (en) * 2011-03-16 2016-03-30 西门子公司 For the stroke transmitter of gas turbine
US10156191B2 (en) 2011-03-16 2018-12-18 Siemens Aktiengesellschaft Stroke transmitter for gas turbine
WO2013087475A1 (en) * 2011-12-12 2013-06-20 Continental Automotive Gmbh Injection valve
WO2015044420A2 (en) * 2013-09-27 2015-04-02 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
WO2015044420A3 (en) * 2013-09-27 2015-05-21 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
US10355622B2 (en) 2013-09-27 2019-07-16 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
WO2016045989A1 (en) * 2014-09-26 2016-03-31 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
CN110440046A (en) * 2019-09-06 2019-11-12 厦门赛尔特电子有限公司 A kind of liquid transmitting stroke amplifying type Piezoelectric switches valve

Also Published As

Publication number Publication date
EP0864743A3 (en) 2001-08-08
DE19709795A1 (en) 1998-09-17
JPH10252598A (en) 1998-09-22
EP0864743B1 (en) 2003-06-11
DE59710265D1 (en) 2003-07-17

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