EP2205852B1 - Method of operating an internal combustion engine with a fuel injector - Google Patents

Method of operating an internal combustion engine with a fuel injector Download PDF

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Publication number
EP2205852B1
EP2205852B1 EP08804376A EP08804376A EP2205852B1 EP 2205852 B1 EP2205852 B1 EP 2205852B1 EP 08804376 A EP08804376 A EP 08804376A EP 08804376 A EP08804376 A EP 08804376A EP 2205852 B1 EP2205852 B1 EP 2205852B1
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EP
European Patent Office
Prior art keywords
pressure
fuel
injection valve
injection
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08804376A
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German (de)
French (fr)
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EP2205852A2 (en
Inventor
Andreas Rau
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2205852A2 publication Critical patent/EP2205852A2/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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/2003—Output circuits, e.g. for controlling currents in command coils using means for creating a boost voltage, i.e. generation or use of a voltage higher than the battery voltage, e.g. to speed up injector opening
    • 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
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention relates to a method for operating an internal combustion engine having a fuel injection valve according to the preamble of claim 1.
  • a fuel injection valve in which an actuator via a pressure chamber in hydraulic operative connection with an injection valve member, which is also referred to as a nozzle needle.
  • a control valve which controls the pressure in a control chamber by pressure relief to the low pressure area in otherwise conventional manner is not provided in this embodiment.
  • the from the DE 103 52 736 Known type of operation of the nozzle needle is referred to as a direct needle control.
  • fuel injection valves with direct needle control are off DE 10 2006 036 444 A1 and DE 103 52 736 A1 known.
  • a driving method for driving a piezoelectric actuator of a fuel injection valve is known.
  • it is proposed to reduce the voltage applied to the actuator between two injections.
  • the gradient of the voltage change (dU / dt) is so small that the change in length of the actuator is compensated by leakage at the piston.
  • the reduced voltage must therefore be increased relatively early before the next injection cycle, so that at a given maximum permissible gradient of the voltage change (dU / dt) at the right time the voltage level required to achieve an injection is reached.
  • the method according to the invention with the characterizing features of claim 1 has the advantage that the increase in pressure associated with the rise of the voltage in the pressure chamber, which can not be compensated by leakage because of the high gradient of the voltage change dU / dt, because of the Druckbastungsventils not to an inadmissible high pressure rise in the pressure chamber leads.
  • This makes it possible to reduce the voltage level between two injections in quick succession, for example, between a main injection and a post-injection, so as to additionally protect the piezoelectric actuator.
  • fuel injection valve 1 after FIG. 1 First, fuel from a fuel tank 2 by means of a high pressure pump 3 via a high pressure line 4 in a high-pressure fuel storage 5.
  • terminals 6 are arranged, each leading to a cylinder of the internal combustion engine.
  • Each of the terminals 6 is connected via a fuel supply line 7 with a fuel injection valve 1 designed according to the invention.
  • the fuel injection valve 1 comprises a piston 8 designed as a piston, which is guided in a coupler housing 9, and an injection valve member 10, which may also be referred to as a nozzle needle.
  • the injection valve member 10 is divided in a preferred embodiment of the fuel injection valve 1 into a translator section 11, a guide section 12 and a needle section 13.
  • the piston 8, the coupler housing 9 and the injection valve member 10 are accommodated in a housing.
  • the housing is divided into an injector housing part 14 and a nozzle housing part 15.
  • the connection of the Injektorgepuruseteils 14 and the nozzle housing part 15 is preferably carried out non-positively by means of a nozzle clamping nut, not shown here.
  • the fuel injection valve 1 comprises at least one injection opening 16, which can be closed by the needle portion 13 of the injection valve member 10.
  • the needle section 13 of the injection valve member 10 is placed on a seat 17 arranged above the injection opening 16.
  • An axial movement for opening and closing the at least one injection opening 16 is ensured by the fact that the injection valve member 10 is guided with its guide portion 12 in a needle guide 18 arranged in the nozzle housing part 15.
  • the translator section 11 of the injection valve member 10 is enclosed by a sleeve 19.
  • the sleeve 19 serves as a lateral boundary of a pressure chamber 20.
  • the sleeve 19 is provided with a sealing edge 21 against a serving as a sealing seat paragraph 22 of the coupler housing 9 or as in Fig.
  • the pressure chamber 20 is divided into a coupler space 20a and a control chamber 20b, wherein the piston 8, the coupler space 20a and the translator section 11 limit the control chamber 20b.
  • a spring element 24 is supported.
  • the spring element 24 is annular and surrounds the translator portion 11 of the injection valve member 10.
  • spring elements 24 are, for example, coil springs, coil springs or other known in the art, annularly shaped spring elements. With its other side, the spring element 24 is supported against a ring 25, which is preferably arranged in a recess 26 which is located between the translator section 11 and the guide section 12 of the injection valve member 10
  • the coupler housing 9 is surrounded by a second spring element 27 which is supported with one side on a step 28 on the coupler housing 9 and with its other side on a ring 29 which rests against a step 30 on the piston 8.
  • the step 28 serves at the same time as a guide of the coupler housing 9 in the injector housing part 14.
  • the spring element 27 is accommodated in a first spring chamber 32, which is arranged between the coupler housing 9 and the inner wall 33 of the injector housing part 14.
  • at least one groove 34 which is preferably axially aligned, is received.
  • the first spring chamber 32 with a the translator section 11 of the injection valve member 10 surrounding the second spring chamber 39 in hydraulic communication.
  • the at least one groove 34 and the grooves 35 in paragraph 31 of the nozzle housing part 15 are preferably aligned so that their positions coincide radially and axially.
  • the second spring chamber 39 is connected via at least one channel, which is formed between at least one bevel 40 in the guide portion 12 of the injection valve member 10 and the needle guide 18, in hydraulic communication with a nozzle chamber 41st
  • actuator which acts on an upper end face 42 of the piston 8.
  • a piezoelectric actuator 43 is preferably used. But there are also electromagnet or hydraulic / mechanical actuator.
  • the operation of the fuel injection valve 1 takes place hydraulically with fuel under system pressure.
  • the fuel is provided by the high-pressure fuel storage 5.
  • the fuel flows into an annular space 44, which surrounds the piezoelectric actuator 43.
  • the fuel under system pressure passes into the first spring chamber 32.
  • the fuel flows into the second spring chamber 39. From there, the fuel passes along the at least one bevel 40 in the nozzle chamber 41.
  • the piezoelectric actuator 43 For injecting fuel into the combustion chamber 52 of the internal combustion engine, the piezoelectric actuator 43 is discharged and the voltage U applied to the piezoelectric actuator 43 is lowered. As a result, the piezocrystals contract and the piezoactuator 43 contracts. Supported by the force exerted by the spring element 27 spring force, the piston 8 moves in the with the arrow 46 marked direction of movement. As a result, the lower end face 47 of the piston 8 moves out of the pressure chamber 20, which increases its volume. Due to the increasing volume of the pressure chamber 20, the pressure in the pressure chamber 20 decreases. Since the pressure in the pressure chamber 20 in this case drops below the system pressure, it is necessary that the connection between the sleeve 19 and the shoulder 22 in the coupler housing 9 is pressure-tight. The filling of the pressure chamber 20 takes place by guide leakage between the coupler housing 9 and the piston 8 and between the inside 43 of the sleeve 19 and the translator section 11 of the injection valve member 10th
  • the piezoelectric actuator 43 For closing the at least one injection opening 16, the piezoelectric actuator 43 is energized again. The piezocrystals thereby expand and the piezoactuator 43 lengthens. As a result, the piston 8 again moves against the direction of movement indicated by the arrow 46 into the pressure chamber 20, whereby the volume of the pressure chamber 20 is reduced. This in turn increases the pressure in the pressure chamber 20 and thus the force acting on the end face 48 of the translator portion 11 of the injection valve member 10 hydraulic force.
  • the injection valve member 10 moves in the direction the at least one injection opening 16 and is placed on the seat 17. As a result, the at least one injection opening 16 is closed and the injection process into the combustion chamber 52 is terminated.
  • the sleeve 19 is designed such that a pressure application surface 55 is formed on it, acts on the pressure prevailing in the pressure chamber 20 pressure and exerts a counter to the spring 24 directed force.
  • the pressure application surface 55 is formed by a chamfer, which is arranged on the pressure chamber side on the inside of the sleeve 19.
  • the force of the spring 24 and the size of the pressure stage are dimensioned so that a pressure relief valve 56 is formed, which opens at pressure above system pressure in the pressure chamber 20 to the high-pressure fuel area out by the sealing edge 21 upon reaching the opening pressure of paragraph 31 against the force the spring 24 lifts and releases a gap to the high pressure area behind it. In this way, an overpressure in the pressure chamber 20 is avoided.
  • FIG. 2 a second embodiment of the invention is shown, which differs from the first embodiment in that between the coupler chamber 20a and the control chamber 20b, a throttle 57 is arranged.
  • FIG. 3 shows a third embodiment of the invention, in which the pressure relief valve 56 is arranged in the coupler space 20b.
  • a sleeve 19a is guided for this purpose, which is acted upon by a spring element 24a in a closed position.
  • a sealing edge 21a is formed, which cooperates with a corresponding sealing seat.
  • Coupler space side is formed on the sleeve 19a, a pressure application surface 55a in the form of a chamfer.
  • the pressure application surface 55a and the spring element 24a are dimensioned so that the pressure relief valve 56 opens at a fuel pressure above the fuel inlet pressure, so that a pressure reduction takes place to the fuel inlet channel 7 out.
  • the injection valve member 10 could be made in several parts and the translator section 11 could be connected to a push rod which actuates the injection valve member 10.
  • the pressure relief valve 56 may also be formed by a conventional pressure relief valve of known type.

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

Abstract

The invention relates to a fuel injection valve for an internal combustion engine. Said fuel injection valve comprises at least one injection port (16), an injection valve member (10), which controls the injection of fuel via the injection port (16), an actuator (43), which actuates a piston (8) on which a pressure surface (47) is configured, a pressure compartment (20), which is filled with fuel and which is delimited by the pressure surface (47), and a fuel inlet duct (7), which is connected to the injection port depending on the piston of the injection valve member (10), a fuel pressure in the pressure compartment (20) exerting a force on the injection valve member (10). The invention is characterized in that the pressure compartment (20) is connected to the fuel inlet duct (7) via a pressure relief valve (56).

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Verfahren zum Betreiben einer Brennkraftmaschine mit einem Kraftstoffeinspritzventil nach dem Oberbegriff des Anspruchs 1.The invention relates to a method for operating an internal combustion engine having a fuel injection valve according to the preamble of claim 1.

Aus der DE 103 52 736 A1 ist ein Kraftstoffeinspritzventil bekannt, bei dem ein Aktor über einen Druckraum in hydraulischer Wirkverbindung mit einem Einspritzventilglied steht, das auch als Düsennadel bezeichnet wird. Ein Steuerventil, das in sonst üblicher Weise den Druck in einem Steuerraum durch Druckentlastung zum Niederdruckbereich steuert, ist bei dieser Ausführung nicht vorgesehen. Die aus der DE 103 52 736 bekannte Art der Betätigung der Düsennadel wird als direkte Nadelsteuerung bezeichnet. Weiterhin sind Kraftstoffeinspritzventile mit direkter Nadelsteuerung aus DE 10 2006 036 444 A1 und DE 103 52 736 A1 bekannt.From the DE 103 52 736 A1 a fuel injection valve is known in which an actuator via a pressure chamber in hydraulic operative connection with an injection valve member, which is also referred to as a nozzle needle. A control valve which controls the pressure in a control chamber by pressure relief to the low pressure area in otherwise conventional manner is not provided in this embodiment. The from the DE 103 52 736 Known type of operation of the nozzle needle is referred to as a direct needle control. Furthermore, fuel injection valves with direct needle control are off DE 10 2006 036 444 A1 and DE 103 52 736 A1 known.

Aus der DE 10 2005 032 841 A1 ist ein Ansteuerverfahren zur Ansteuerung eines piezoelektrischen Aktors eines Kraftstoffeinspritzventils bekannt. Um Alterungserscheinungen des Aktors zu vermeiden, wird vorgeschlagen, die am Aktor anliegende Spannung zwischen zwei Einspritzungen zu reduzieren. Dabei soll jedoch darauf geachtet werden, dass der Gradient der Spannungsänderung (dU/dt) so gering ist, dass die Längenänderung des Aktors durch Leckage am Kolben ausgeglichen wird. Die reduzierte Spannung muss also schon relativ früh vor dem nächsten Einspritzzyklus erhöht werden, damit bei gegebenem maximal zulässigem Gradienten der Spannungsänderung (dU/dt) zum richtigen Zeitpunkt das für die Erzielung einer Einspritzung erforderliche Spannungsniveau erreicht ist.From the DE 10 2005 032 841 A1 a driving method for driving a piezoelectric actuator of a fuel injection valve is known. In order to avoid aging phenomena of the actuator, it is proposed to reduce the voltage applied to the actuator between two injections. However, care should be taken that the gradient of the voltage change (dU / dt) is so small that the change in length of the actuator is compensated by leakage at the piston. The reduced voltage must therefore be increased relatively early before the next injection cycle, so that at a given maximum permissible gradient of the voltage change (dU / dt) at the right time the voltage level required to achieve an injection is reached.

Um die Lebensdauer der Aktoren noch weiter zu erhöhe, wäre es wünschenswert, wenn man die Spannungsänderung schneller durchführen könnte, um insgesamt eine zeitlich längere Spannungsabsenkung zu erzielen bzw. die Spannungsabsenkung auch zwischen zwei kurz hintereinander erfolgenden Einspritzungen durchführen zu können. Fährt man die Spannung jedoch erst kurz vor dem Beginn einer Einspritzung schnell auf das erforderliche Niveau hoch, wird die Längenänderung des Aktors nicht rechtzeitig kompensiert. Es entsteht dann ein Überdruck im Druckraum, mit der Folge, dass die Düsennadel und andere Bauteile stärker beansprucht werden. Bei anschließender schneller Absenkung der Spannung zur Erzielung der Einspritzung wird dann zunächst lediglich der Überdruck im Druckraum abgebaut, so dass dann nicht das volle Spannungsniveau zur Betätigung der Düsennadel zur Verfügung steht.In order to increase the life of the actuators even further, it would be desirable if one could carry out the voltage change faster, in order to achieve an overall longer voltage reduction or to be able to perform the voltage reduction between two successive injections. However, if the voltage is quickly increased to the required level shortly before the beginning of an injection, the change in length of the actuator is not compensated in time. It then creates an overpressure in the pressure chamber, with the result that the nozzle needle and other components are more stressed. In subsequent rapid lowering of the voltage to achieve the injection, only the overpressure in the pressure chamber is then initially reduced, so that then not the full voltage level for actuating the nozzle needle is available.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Verfahren mit den kennzeichnenden Maßnahmen des Anspruchs 1 hat den Vorteil, dass der mit dem Hochfahren der Spannung einhergehende Druckanstieg im Druckraum, der wegen des hohen Gradienten der Spannungsänderung dU/dt nicht durch Leckage ausgeglichen werden kann, wegen des Druckenbastungsventils nicht zu einem unzulässig hohen Druckanstieg im Druckraum führt. Damit ist es möglich, das Spannungsniveau auch zwischen zwei kurz hintereinander liegenden Einspritzungen zu senken, beispielsweise zwischen einer Haupt- und einer Nacheinspritzung, um so den Piezoaktor zusätzlich zu schonen.The method according to the invention with the characterizing features of claim 1 has the advantage that the increase in pressure associated with the rise of the voltage in the pressure chamber, which can not be compensated by leakage because of the high gradient of the voltage change dU / dt, because of the Druckbastungsventils not to an inadmissible high pressure rise in the pressure chamber leads. This makes it possible to reduce the voltage level between two injections in quick succession, for example, between a main injection and a post-injection, so as to additionally protect the piezoelectric actuator.

Zeichnungendrawings

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.

Es zeigen:

  • Figur 1 eine Längsschnittdarstellung eines erfindungsgemäßen Kraftstoffeinspritzventils gemäß einem ersten Ausführungsbeispiel,
  • Figur 2 eine Längsschnittdarstellung eines erfindungsgemäßen Kraftstoffeinspritzventils gemäß einem zweiten Ausführungsbeispiel,
  • Figur 3 eine Längsschnittdarstellung eines erfindungsgemäßen Kraftstoffeinspritzventils gemäß einem dritten Ausführungsbeispiel.
Show it:
  • FIG. 1 a longitudinal sectional view of a fuel injection valve according to the invention according to a first embodiment,
  • FIG. 2 a longitudinal sectional view of a fuel injection valve according to the invention according to a second embodiment,
  • FIG. 3 a longitudinal sectional view of a fuel injection valve according to the invention according to a third embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In der nachfolgenden Beschreibung sind gleiche bzw. gleichwirkende Teile mit den gleichen Bezugszeichen gekennzeichnet.In the following description, identical or equivalent parts are marked with the same reference numerals.

Bei dem erfindungsgemäß ausgebildeten Kraftstoffeinspritzventil 1 nach Figur 1 gelangt zunächst Kraftstoff aus einem Kraftstoffvorratsbehälter 2 mittels einer Hochdruckpumpe 3 über eine Hochdruckleitung 4 in einen Kraftstoffhochdruckspeicher 5. Am Kraftstoffhochdruckspeicher 5 sind Anschlüsse 6 angeordnet, die jeweils zu einem Zylinder der Brennkraftmaschine führen. Jeder der Anschlüsse 6 ist über eine Kraftstoffzuleitung 7 mit einem erfindungsgemäß ausgebildeten Kraftstoffeinspritzventil 1 verbunden. Das Kraftstoffeinspritzventil 1 umfasst einen als Kolben 8 ausgebildeten Kolben, der in einem Kopplergehäuse 9 geführt ist, sowie ein Einspritzventilglied 10, das auch als Düsennadel bezeichnet werden kann. Das Einspritzventilglied 10 ist in einer bevorzugten Ausführungsform des Kraftstoffeinspritzventils 1 in einen Übersetzerabschnitt 11, einen Führungsabschnitt 12 und einen Nadelabschnitt 13 unterteilt.In the inventively designed fuel injection valve 1 after FIG. 1 First, fuel from a fuel tank 2 by means of a high pressure pump 3 via a high pressure line 4 in a high-pressure fuel storage 5. At high-pressure fuel storage 5 terminals 6 are arranged, each leading to a cylinder of the internal combustion engine. Each of the terminals 6 is connected via a fuel supply line 7 with a fuel injection valve 1 designed according to the invention. The fuel injection valve 1 comprises a piston 8 designed as a piston, which is guided in a coupler housing 9, and an injection valve member 10, which may also be referred to as a nozzle needle. The injection valve member 10 is divided in a preferred embodiment of the fuel injection valve 1 into a translator section 11, a guide section 12 and a needle section 13.

Der Kolben 8, das Kopplergehäuse 9 und das Einspritzventilglied 10 sind in einem Gehäuse aufgenommen. In einer bevorzugten Ausführungsform ist das Gehäuse in ein Injektorgehäuseteil 14 und ein Düsengehäuseteil 15 aufgeteilt. Die Verbindung des Injektorgehäuseteils 14 und des Düsengehäuseteils 15 erfolgt vorzugsweise kraftschlüssig mittels einer hier nicht dargestellten Düsenspannmutter.The piston 8, the coupler housing 9 and the injection valve member 10 are accommodated in a housing. In a preferred embodiment, the housing is divided into an injector housing part 14 and a nozzle housing part 15. The connection of the Injektorgehäuseteils 14 and the nozzle housing part 15 is preferably carried out non-positively by means of a nozzle clamping nut, not shown here.

Weiterhin umfasst das Kraftstoffeinspritzventil 1 mindestens eine Einspritzöffnung 16, welche durch den Nadelabschnitt 13 des Einspritzventilgliedes 10 verschlossen werden kann. Zum Verschließen der Einspritzöffnung 16 wird der Nadelabschnitt 13 des Einspritzventilgliedes 10 an einen oberhalb der Einspritzöffnung 16 angeordneten Sitz 17 gestellt. Eine axiale Bewegung zum Öffnen und Verschließen der mindestens einen Einspritzöffnung 16 wird dadurch gewährleistet, dass das Einspritzventilglied 10 mit seinem Führungsabschnitt 12 in einer im Düsengehäuseteil 15 angeordneten Nadelführung 18 geführt ist Der Übersetzerabschnitt 11 des Einspritzventilgliedes 10 ist von einer Hülse 19 umschlossen. Die Hülse 19 dient als seitliche Begrenzung eines Druckraumes 20. Die Hülse 19 ist mit einer Dichtkante 21 versehen, die gegen einen als Dichtsitz dienenden Absatz 22 des Kopplergehäuses 9 oder wie in Fig. 2 dargestellt gegen eine dazwischen angeordnete Drosselplatte gepresst wird. Hierdurch wird eine flüssigkeits- und damit druckdichte Verbindung der Hülse 19 mit dem Absatz 22 des Kopplergehäuses 9 erreicht. Der Druckraum 20 ist dabei in einen Kopplerraum 20a und einen Steuerraum 20b unterteilt, wobei der Kolben 8 den Kopplerraum 20a und der Übersetzerabschnitt 11 den Steuerraum 20b begrenzen.Furthermore, the fuel injection valve 1 comprises at least one injection opening 16, which can be closed by the needle portion 13 of the injection valve member 10. For closing the injection opening 16, the needle section 13 of the injection valve member 10 is placed on a seat 17 arranged above the injection opening 16. An axial movement for opening and closing the at least one injection opening 16 is ensured by the fact that the injection valve member 10 is guided with its guide portion 12 in a needle guide 18 arranged in the nozzle housing part 15. The translator section 11 of the injection valve member 10 is enclosed by a sleeve 19. The sleeve 19 serves as a lateral boundary of a pressure chamber 20. The sleeve 19 is provided with a sealing edge 21 against a serving as a sealing seat paragraph 22 of the coupler housing 9 or as in Fig. 2 is pressed against a disposed therebetween throttle plate. As a result, a liquid and thus pressure-tight connection of the sleeve 19 with the shoulder 22 of the coupler housing 9 is achieved. The pressure chamber 20 is divided into a coupler space 20a and a control chamber 20b, wherein the piston 8, the coupler space 20a and the translator section 11 limit the control chamber 20b.

An einer der Dichtkante 21 gegenüberliegenden Stirnfläche 23 der Hülse 19 stützt sich ein Federelement 24 ab. Das Federelement 24 ist ringförmig ausgebildet und umschließt den Übersetzerabschnitt 11 des Einspritzventilgliedes 10. Als Federelemente 24 eignen sich zum Beispiel Spiralfedern, Rohrfedern oder weitere dem Fachmann bekannte, ringförmig ausgebildete Federelemente. Mit seiner anderen Seite stützt sich das Federelement 24 gegen einen Ring 25, welcher vorzugsweise in einem Einstich 26, der sich zwischen dem Übersetzerabschnitt 11 und dem Führungsabschnitt 12 des Einspritzventilgliedes 10 befindet, angeordnet istAt one of the sealing edge 21 opposite end face 23 of the sleeve 19, a spring element 24 is supported. The spring element 24 is annular and surrounds the translator portion 11 of the injection valve member 10. As spring elements 24 are, for example, coil springs, coil springs or other known in the art, annularly shaped spring elements. With its other side, the spring element 24 is supported against a ring 25, which is preferably arranged in a recess 26 which is located between the translator section 11 and the guide section 12 of the injection valve member 10

Das Kopplergehäuse 9 ist von einem zweiten Federelement 27 umgeben, welches sich mit einer Seite auf einer Stufe 28 am Kopplergehäuse 9 und mit seiner anderen Seite an einem Ring 29, welcher an einer Stufe 30 am Kolben 8 anliegt, abstützt. Die Stufe 28 dient dabei gleichzeitig als Führung des Kopplergehäuses 9 im Injektorgehäuseteil 14. Durch die von dem Federelement 27 aufgebrachte Federkraft wird das Kopplergehäuse 9 auf einem Absatz 31 am Düsengehäuseteil 15 fixiert. Das Federelement 27 ist in einem ersten Federraum 32 aufgenommen, welcher zwischen dem Kopplergehäuse 9 und der Innenwand 33 des Injektorgehäuseteils 14 angeordnet ist. In der Stufe 28 des Kopplergehäuses 9 ist mindestens eine Nut 34, die vorzugsweise axial ausgerichtet ist, aufgenommen. Über die mindestens eine Nut 34, im Absatz 31 am Düsengehäuseteil 15 ausgebildete Nuten 35 und einen mindestens eine Ringspalt 36, der zwischen der Außenwand 37 der Hülse 19 und der Innenwand 38 des Düsengehäuseteils 15 ausgebildet ist, steht der erste Federraum 32 mit einem den Übersetzerabschnitts 11 des Einspritzventilgliedes 10 umgebenden zweiten Federraum 39 in hydraulischer Verbindung. Hierzu sind die mindestens eine Nut 34 und die Nuten 35 im Absatz 31 des Düsengehäuseteils 15 vorzugsweise so ausgerichtet, dass ihre Positionen radial und axial übereinstimmen. Der zweite Federraum 39 steht über mindestens einen Kanal, der zwischen mindestens einem Anschliff 40 im Führungsabschnitt 12 des Einspritzventilgliedes 10 und der Nadelführung 18 ausgebildet ist, in hydraulischer Verbindung mit einem Düsenraum 41.The coupler housing 9 is surrounded by a second spring element 27 which is supported with one side on a step 28 on the coupler housing 9 and with its other side on a ring 29 which rests against a step 30 on the piston 8. The step 28 serves at the same time as a guide of the coupler housing 9 in the injector housing part 14. By the spring force applied by the spring element 27, the coupler housing 9 is fixed on a shoulder 31 on the nozzle housing part 15. The spring element 27 is accommodated in a first spring chamber 32, which is arranged between the coupler housing 9 and the inner wall 33 of the injector housing part 14. In stage 28 of the coupler housing 9, at least one groove 34, which is preferably axially aligned, is received. Via the at least one groove 34, formed in paragraph 31 on the nozzle housing part 15 grooves 35 and at least one annular gap 36 which is formed between the outer wall 37 of the sleeve 19 and the inner wall 38 of the nozzle housing part 15, the first spring chamber 32 with a the translator section 11 of the injection valve member 10 surrounding the second spring chamber 39 in hydraulic communication. For this purpose, the at least one groove 34 and the grooves 35 in paragraph 31 of the nozzle housing part 15 are preferably aligned so that their positions coincide radially and axially. The second spring chamber 39 is connected via at least one channel, which is formed between at least one bevel 40 in the guide portion 12 of the injection valve member 10 and the needle guide 18, in hydraulic communication with a nozzle chamber 41st

Die Steuerung des Kraftstoffeinspritzventils 1 erfolgt über einen Aktor, welcher auf eine obere Stirnfläche 42 des Kolbens 8 wirkt. Als Aktor wird vorzugsweise ein Piezoaktor 43 eingesetzt. Es eignen sich aber auch Elektromagneten oder hydraulisch/mechanische Steller.The control of the fuel injection valve 1 via an actuator, which acts on an upper end face 42 of the piston 8. As actuator, a piezoelectric actuator 43 is preferably used. But there are also electromagnet or hydraulic / mechanical actuator.

Der Betrieb des Kraftstoffeinspritzventils 1 erfolgt hydraulisch mit unter Systemdruck stehendem Kraftstoff. Der Kraftstoff wird durch den Kraftstoffhochdruckspeicher 5 bereitgestellt. Über die Kraftstoffzuleitung 7 strömt der Kraftstoff in einen Ringraum 44, der den Piezoaktor 43 umgibt. Über einen Spalt 45 zwischen dem Kolben 8 und der Innenwand 33 des Injektorgehäuseteils 14 gelangt der unter Systemdruck stehende Kraftstoff in den ersten Federraum 32. Über die mindestens eine Nut 34, die Nuten 35 im Absatz 31 des Düsengehäuseteils 15 und den Ringspalt 36 strömt der Kraftstoff in den zweiten Federraum 39. Von dort gelangt der Kraftstoff entlang dem mindestens einen Anschliff 40 in den Düsenraum 41. Aufgrund der hydraulischen Verbindungen zwischen dem Ringraum 44, dem ersten Federraum 32, dem zweiten Federraum 39 und dem Düsenraum 41 herrscht sowohl im Ringraum 44, als auch im ersten Federraum 32, dem zweiten Federraum 39 und dem Düsenraum 41 Systemdruck. Die genannten Kanäle der Kraftstoffzuleitung 7 bis zum Düsenraum 41 bilden somit insgesamt einen Kraftstoffhochdruckbereich im Kraftstoffeinspritzventil 1, in dem Systemdruck herrscht.The operation of the fuel injection valve 1 takes place hydraulically with fuel under system pressure. The fuel is provided by the high-pressure fuel storage 5. Via the fuel supply line 7, the fuel flows into an annular space 44, which surrounds the piezoelectric actuator 43. Via a gap 45 between the piston 8 and the inner wall 33 of the injector housing part 14, the fuel under system pressure passes into the first spring chamber 32. On the at least one groove 34, the grooves 35 in paragraph 31 of the nozzle housing part 15 and the annular gap 36, the fuel flows into the second spring chamber 39. From there, the fuel passes along the at least one bevel 40 in the nozzle chamber 41. Due to the hydraulic Connections between the annular space 44, the first spring chamber 32, the second spring chamber 39 and the nozzle chamber 41 prevails both in the annular space 44, and in the first spring chamber 32, the second spring chamber 39 and the nozzle chamber 41 system pressure. The said channels of the fuel supply line 7 to the nozzle chamber 41 thus form a total of a high-pressure fuel area in the fuel injection valve 1, prevails in the system pressure.

Zum Erzielen einer Längenänderung wird der Piezoaktor 43 mit einem Strom (I) geladen, wobei eine entsprechende Spannung (U) anliegt. Eine Längenänderung des Piezoaktors wirkt wie folgt:

  • Wird der Kolben 8 beispielsweise entgegen der mit dem Pfeil 46 gekennzeichneten Bewegungsrichtung mit einer unteren Stirnseite 47 in den Druckraum 20 bewegt, verringert sich das Volumen im Druckraum 20, wodurch der Druck darin steigt. Hierdurch steigt die hydraulische Kraft, die auf eine Stirnfläche 48 am Ãœbersetzerabschnitt 11 des Einspritzventilgliedes 10 wirkt. Die auf die Stirnfläche 48 wirkende hydraulische Kraft ist einer auf das Einspritzventilglied 10 infolge von Druckstufen 50, 51 wirkenden hydraulischen Kraft entgegengerichtet. Das Verschließen der mindestens einen Einspritzöffnung 16 wird durch die Federkraft des Federelementes 24 unterstützt.
  • Hierzu wirkt das Federelement 24 auf eine Stirnfläche 54 des Ringes 25. Um auch bei Druckschwankungen im Kraftstoffhochdruckbereich stets eine Schließstellung des Einspritzventilgliedes 10 sicherzustellen, liegt am Piezoaktor 43 zwischen zwei Einspritzungen stets eine ausreichende positive Haltespannung U an.
To achieve a change in length, the piezoelectric actuator 43 is charged with a current (I), wherein a corresponding voltage (U) is applied. A change in length of the piezo actuator acts as follows:
  • If, for example, the piston 8 is moved against the direction of movement indicated by the arrow 46 with a lower end face 47 into the pressure chamber 20, the volume in the pressure chamber 20 decreases, as a result of which the pressure in it increases. This increases the hydraulic force acting on an end face 48 on the translator section 11 of the injection valve member 10. The force acting on the end face 48 hydraulic force is directed towards the injection valve member 10 due to pressure levels 50, 51 acting hydraulic force. The closing of the at least one injection opening 16 is assisted by the spring force of the spring element 24.
  • For this purpose, the spring element 24 acts on an end face 54 of the ring 25. In order always to ensure a closed position of the injection valve member 10 even with pressure fluctuations in the high-pressure fuel area, is always a sufficient positive holding voltage U at the piezoelectric actuator 43 between two injections.

Zum Einspritzen von Kraftstoff in den Brennraum 52 der Verbrennungskraftmaschine wird der Piezoaktors 43 entladen und die am Piezoaktor 43 anliegende Spannung U wird gesenkt. Hierdurch kontrahieren die Piezokristalle und der Piezoaktor 43 zieht sich zusammen. Unterstützt durch die von dem Federelement 27 ausgeübte Federkraft bewegt sich der Kolben 8 in die mit dem Pfeil 46 gekennzeichnete Bewegungsrichtung. Hierdurch bewegt sich die untere Stirnfläche 47 des Kolbens 8 aus dem Druckraum 20, wodurch sich dessen Volumen vergrößert. Aufgrund des sich vergrößernden Volumens des Druckraumes 20 nimmt der Druck im Druckraum 20 ab. Da der Druck im Druckraum 20 hierbei unter den Systemdruck sinkt, ist es erforderlich, dass die Verbindung zwischen der Hülse 19 und dem Absatz 22 im Kopplergehäuse 9 druckdicht ist. Die Befüllung des Druckraumes 20 erfolgt durch Führungsleckage zwischen dem Kopplergehäuse 9 und dem Kolben 8 bzw. zwischen der Innenseite 43 der Hülse 19 und dem Übersetzerabschnitt 11 des Einspritzventilgliedes 10.For injecting fuel into the combustion chamber 52 of the internal combustion engine, the piezoelectric actuator 43 is discharged and the voltage U applied to the piezoelectric actuator 43 is lowered. As a result, the piezocrystals contract and the piezoactuator 43 contracts. Supported by the force exerted by the spring element 27 spring force, the piston 8 moves in the with the arrow 46 marked direction of movement. As a result, the lower end face 47 of the piston 8 moves out of the pressure chamber 20, which increases its volume. Due to the increasing volume of the pressure chamber 20, the pressure in the pressure chamber 20 decreases. Since the pressure in the pressure chamber 20 in this case drops below the system pressure, it is necessary that the connection between the sleeve 19 and the shoulder 22 in the coupler housing 9 is pressure-tight. The filling of the pressure chamber 20 takes place by guide leakage between the coupler housing 9 and the piston 8 and between the inside 43 of the sleeve 19 and the translator section 11 of the injection valve member 10th

Aufgrund des sinkenden Drucks im Druckraum 20 bei nicht geladenem Piezoaktor 43 nimmt die auf die Stirnfläche 38 des Übersetzerabschnitt 11 des Einspritzventilgliedes 10 wirkende hydraulische Kraft ab. Sobald die auf die Druckstufen 50 und 51 wirkende hydraulische Kraft größer ist als die hydraulische Kraft auf die Stirnfläche 38 und die Federkraft des Federelementes 34, hebt das Einspritzventilglied 10 ab und gibt so die mindestens eine Einspritzöffnung 16 frei. Hierbei strömt Kraftstoff aus dem Düsenraum 41 über die Einspritzöffnung 16 in den Brennraum 52.Due to the falling pressure in the pressure chamber 20 when the piezoelectric actuator 43 is not loaded, the hydraulic force acting on the end face 38 of the translator section 11 of the injection valve member 10 decreases. As soon as the hydraulic force acting on the pressure stages 50 and 51 is greater than the hydraulic force on the end face 38 and the spring force of the spring element 34, the injection valve member 10 lifts and thus releases the at least one injection opening 16. In this case, fuel flows out of the nozzle chamber 41 via the injection opening 16 into the combustion chamber 52.

Zum Verschließen der mindestens einen Einspritzöffnung 16 wird der Piezoaktor 43 wieder bestromt. Die Piezokristalle dehnen sich dadurch aus und der Piezoaktor 43 längt sich. Hierdurch fährt der Kolben 8 wieder entgegen der mit dem Pfeil 46 gekennzeichneten Bewegungsrichtung in den Druckraum 20 ein, wodurch sich das Volumen des Druckraumes 20 verringert. Hierdurch vergrößert sich wiederum der Druck im Druckraum 20 und damit die auf die Stirnfläche 48 des Übersetzerabschnitt 11 des Einspritzventilgliedes 10 wirkende hydraulische Kraft. Sobald die auf den Ring 25 wirkende Federkraft des Federelementes 24 und die hydraulische Kraft, die auf die Stirnfläche 48 am Übersetzerabschnitt 11 des Einspritzventilgliedes 10 wirkt, größer ist als die auf die Druckstufen 50 und 51 wirkende hydraulische Kraft, bewegt sich das Einspritzvenfilglied 10 in Richtung der mindestens eine Einspritzöffnung 16 und wird an den Sitz 17 gestellt. Hierdurch wird die mindestens eine Einspritzöffnung 16 verschlossen und der Einspritzvorgang in den Brennraum 52 wird beendet.For closing the at least one injection opening 16, the piezoelectric actuator 43 is energized again. The piezocrystals thereby expand and the piezoactuator 43 lengthens. As a result, the piston 8 again moves against the direction of movement indicated by the arrow 46 into the pressure chamber 20, whereby the volume of the pressure chamber 20 is reduced. This in turn increases the pressure in the pressure chamber 20 and thus the force acting on the end face 48 of the translator portion 11 of the injection valve member 10 hydraulic force. As soon as the spring force of the spring element 24 acting on the ring 25 and the hydraulic force acting on the face 48 on the translator section 11 of the injection valve member 10 is greater than the hydraulic force acting on the pressure stages 50 and 51, the injection valve member 10 moves in the direction the at least one injection opening 16 and is placed on the seat 17. As a result, the at least one injection opening 16 is closed and the injection process into the combustion chamber 52 is terminated.

Erfindungsgemäß ist die Hülse 19 so ausgebildet, dass an ihr eine Druckangriffsfläche 55 ausgebildet ist, auf die der im Druckraum 20 herrschende Druck wirkt und eine entgegen der Feder 24 gerichtete Kraft ausübt. Im Beispielfall ist die Druckangriffsfläche 55 durch eine Fase gebildet, die druckraumseitig an der Innenseite der Hülse 19 angeordnet ist. Die Kraft der Feder 24 und die Größe der Druckstufe sind dabei so dimensioniert, dass ein Druckentlastungsventil 56 gebildet wird, das bei über Systemdruck liegendem Druck im Druckraum 20 zum Kraftstoffhochdruckbereich hin öffnet, indem die Dichtkante 21 bei Erreichen des Öffnungsdruckes vom Absatz 31 entgegen der Kraft der Feder 24 abhebt und einen Spalt zum dahinter liegenden Hochdruckbereich freigibt. Auf diese Weise wird ein Überdruck im Druckraum 20 vermieden.According to the invention, the sleeve 19 is designed such that a pressure application surface 55 is formed on it, acts on the pressure prevailing in the pressure chamber 20 pressure and exerts a counter to the spring 24 directed force. In the example, the pressure application surface 55 is formed by a chamfer, which is arranged on the pressure chamber side on the inside of the sleeve 19. The force of the spring 24 and the size of the pressure stage are dimensioned so that a pressure relief valve 56 is formed, which opens at pressure above system pressure in the pressure chamber 20 to the high-pressure fuel area out by the sealing edge 21 upon reaching the opening pressure of paragraph 31 against the force the spring 24 lifts and releases a gap to the high pressure area behind it. In this way, an overpressure in the pressure chamber 20 is avoided.

Mit Hilfe des Druckentiastungsventils 56 ist es möglich, die Spannung von einer den Piezoaktor 43 schonenden, abgesenkten Haltespannung aus kurzfristig auf das vor der Einspritzung erforderliche Spannungsniveau hoch zu fahren. Der mit dem Hochfahren der Spannung einhergehende Druckanstieg im Druckraum 20, der wegen des hohen Gradienten der Spannungsänderung dU/dt nicht durch Leckage ausgeglichen werden kann, führt wegen des Druckentlastungsventils 56 nicht zu einem unzulässig hohen Druckanstieg im Druckraum 20. Damit ist es möglich, das Spannungsniveau auch zwischen zwei kurz hintereinander liegenden Einspritzungen zu senken, beispielsweise zwischen einer Haupt- und einer Nacheinspritzung, und so den Piezoaktors zusätzlich zu schonen.With the help of Druckentiastungsventils 56, it is possible to drive the voltage of a piezoelectric actuator 43 gentle, lowered holding voltage from short to the required before the injection voltage level. Due to the high gradient of the voltage change dU / dt can not be compensated by leakage due to the high gradient of the voltage change dU / dt does not lead to an unacceptably high pressure rise in the pressure chamber 20 because of the pressure relief valve 56. Thus, it is possible that To reduce voltage level between two short successive injections, for example, between a main and a post-injection, and thus to spare the piezoelectric actuator in addition.

In Figur 2 ist ein zweites Ausführungsbeispiel der Erfindung gezeigt, das sich vom ersten Ausführungsbeispiel dahingehend unterscheidet, dass zwischen dem Kopplerraum 20a und dem Steuerraum 20b eine Drossel 57 angeordnet ist.In FIG. 2 a second embodiment of the invention is shown, which differs from the first embodiment in that between the coupler chamber 20a and the control chamber 20b, a throttle 57 is arranged.

Die Figur 3 zeigt ein drittes Ausführungsbeispiel der Erfindung, bei dem das Druckentlastungsventil 56 im Kopplerraum 20b angeordnet ist. Am Kolben 8 ist hierzu eine Hülse 19a geführt, die von einem Federelement 24a in eine Schließstellung beaufschlagt ist. An der Hülse 19a ist eine Dichtkante 21a ausgebildet, die mit einem korrespondierenden Dichtsitz zusammenwirkt. Kopplerraumseitig ist an der Hülse 19a eine Druckangriffsfläche 55a in Form einer Fase ausgebildet. Die Druckangriffsfläche 55a und dass Federelement 24a sind dabei so dimensioniert, dass das Druckentlastungsventil 56 bei einem Kraftstoffdruck oberhalb des Kraftstoffzulaufdrucks öffnet, so dass ein Druckabbau zum Kraftstoffzulaufkanal 7 hin erfolgt.The FIG. 3 shows a third embodiment of the invention, in which the pressure relief valve 56 is arranged in the coupler space 20b. On the piston 8 a sleeve 19a is guided for this purpose, which is acted upon by a spring element 24a in a closed position. On the sleeve 19a, a sealing edge 21a is formed, which cooperates with a corresponding sealing seat. Coupler space side is formed on the sleeve 19a, a pressure application surface 55a in the form of a chamfer. The pressure application surface 55a and the spring element 24a are dimensioned so that the pressure relief valve 56 opens at a fuel pressure above the fuel inlet pressure, so that a pressure reduction takes place to the fuel inlet channel 7 out.

Die Anwendbarkeit der vorliegenden Erfindung ist nicht auf die vorstehend beschriebenen Ausführungsformen beschränkt. So sind zahlreiche Änderungsmöglichkeiten bei der konkreten Ausführung denkbar, die den Sinngehalt der Erfindung nicht wesentlich verändern. So könnte beispielsweise das Einspritzventilglied 10 mehrteilig ausgeführt sein und der Übersetzerabschnitt 11 könnte mit einer Druckstange verbunden sein, die das Einspritzventilglied 10 betätigt. Das Druckentlastungsventil 56 kann auch durch ein konventionelles Überdruckventil bekannter Bauart gebildet sein.The applicability of the present invention is not limited to the embodiments described above. Thus, numerous possible modifications in the concrete execution are conceivable that do not significantly change the meaning of the invention. For example, the injection valve member 10 could be made in several parts and the translator section 11 could be connected to a push rod which actuates the injection valve member 10. The pressure relief valve 56 may also be formed by a conventional pressure relief valve of known type.

Claims (1)

  1. Method for operating an internal combustion engine having a fuel injection valve (1) which comprises an actuator (43), which actuator is hydraulically operatively connected via a piston (8) and a pressure chamber (20) to an injection valve member (10) and which actuator is acted on with an electrical voltage which determines the position of the piston (8), the electrical voltage being increased shortly before the start of an injection, characterized in that a pressure increase occurring in the pressure chamber (20) as a result of the voltage increase is dissipated into a fuel supply duct (7) by means of a pressure relief valve (56).
EP08804376A 2007-10-29 2008-09-18 Method of operating an internal combustion engine with a fuel injector Not-in-force EP2205852B1 (en)

Applications Claiming Priority (2)

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DE102007051554A DE102007051554A1 (en) 2007-10-29 2007-10-29 Fuel injection valve for an internal combustion engine
PCT/EP2008/062436 WO2009056395A2 (en) 2007-10-29 2008-09-18 Fuel injection valve for an internal combustion engine

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EP2205852A2 EP2205852A2 (en) 2010-07-14
EP2205852B1 true EP2205852B1 (en) 2011-08-03

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EP08804376A Not-in-force EP2205852B1 (en) 2007-10-29 2008-09-18 Method of operating an internal combustion engine with a fuel injector

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AT (1) ATE519032T1 (en)
DE (1) DE102007051554A1 (en)
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DE102012212614A1 (en) 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement
DE102012222509A1 (en) 2012-12-07 2014-06-12 Continental Automotive Gmbh piezoinjector
DE102012223934B4 (en) 2012-12-20 2015-10-15 Continental Automotive Gmbh piezoinjector
GB201420017D0 (en) * 2014-11-11 2014-12-24 Delphi International Operations Luxembourg S.�.R.L. Hydraulic lash adjuster arrangement ina servo injector

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DE10352736A1 (en) 2003-11-12 2005-07-07 Robert Bosch Gmbh Fuel injector with direct needle injection
DE102005032841B4 (en) 2005-07-14 2017-06-14 Robert Bosch Gmbh Pulling operation of an injection valve with voltage reduction between injections
DE102005059169A1 (en) * 2005-12-12 2007-06-14 Robert Bosch Gmbh Fuel injector with directly actuatable injection valve member
DE102006036444A1 (en) 2006-03-30 2007-10-04 Robert Bosch Gmbh Injector for injecting fuel into a combustion chamber of an internal combustion engine comprises a high pressure translation unit arranged parallel to a control piston and having a translation chamber connected to a control valve

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WO2009056395A2 (en) 2009-05-07
WO2009056395A3 (en) 2009-06-18
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ATE519032T1 (en) 2011-08-15
EP2205852A2 (en) 2010-07-14

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