EP1831537B1 - Injector for a fuel-injection system in an internal combustion engine - Google Patents

Injector for a fuel-injection system in an internal combustion engine Download PDF

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Publication number
EP1831537B1
EP1831537B1 EP05808118A EP05808118A EP1831537B1 EP 1831537 B1 EP1831537 B1 EP 1831537B1 EP 05808118 A EP05808118 A EP 05808118A EP 05808118 A EP05808118 A EP 05808118A EP 1831537 B1 EP1831537 B1 EP 1831537B1
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EP
European Patent Office
Prior art keywords
valve body
valve
stepped bore
injector
section
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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
EP05808118A
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German (de)
French (fr)
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EP1831537A1 (en
Inventor
Rudolf Heinz
Wolfgang Stoecklein
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1831537A1 publication Critical patent/EP1831537A1/en
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Publication of EP1831537B1 publication Critical patent/EP1831537B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to an injector for an internal combustion engine according to the preamble of patent claim 1.
  • Such an injector is for example by the US-A-2004/0129804 known.
  • an injector for an internal combustion engine with a control valve for opening and closing a nozzle needle comprises a housing and an actuator, wherein in the housing a stepped bore having a second portion (spring chamber) is formed for receiving a valve body, wherein a first portion of the stepped bore as a bypass and a third portion of the stepped bore are formed as an outlet and wherein Outflow channel opens into the second section of the stepped bore.
  • a first valve seat is provided, wherein the valve body has a valve cone cooperating with the first valve seat.
  • valve body is pressed against a plunger of an actuator by a closing spring arranged in the second section of the stepped bore and is guided in the third section of the stepped bore, wherein one or more passages for the control quantity of the injector are present in this section.
  • valve body is guided in the second section (spring chamber) of the stepped bore, ensures that the valve cone of the Valve body always almost centric and slipping on the valve seat of the housing. This avoids, first, local overstressing of the valve plug and valve seat, and reduces wear of the valve seat and poppet. Both effects cause the valve lift changes only slightly during operation of the internal combustion engine, so that the operating behavior of the internal combustion engine remains approximately the same over the entire life.
  • the game between stepped bore and the guide portion of the valve body is so large that the valve body in the closed position of the control valve centered on the valve seat of the housing, as only then closes the control valve tight.
  • the injector according to the invention provide that the first section (inlet) of the stepped bore communicates with a control chamber of the injector, while the third section (outlet) of the stepped bore communicates with a fuel return.
  • the closing spring acts on the valve body against the actuating direction of the actuator. This ensures that the valve body always occupies a defined position and the control valve is closed when the actuator is de-energized.
  • the closing spring is at least indirectly supported against the housing and a spring plate of the valve body.
  • valve body is guided on the spring plate or that a sleeve is provided in the spring chamber and that the valve body is guided by the sleeve.
  • the passages are alternatively designed as grooves, flattenings and / or longitudinal bores extending in the longitudinal direction of the valve body.
  • the flow resistance of the control valve in the open state can be reduced so far that the function of the injector is not affected by the leadership of the valve body in the stepped bore.
  • the housing can be made in two parts. In this case, the control valve can be integrated both as a separate component and in the injector. In the latter case, the housing of the control valve is also the housing of the injector at the same time.
  • control valve can be designed as a 2/3-way control valve.
  • multiple injections can be realized more easily and there are additional possibilities of injection molding.
  • the valve body can be actuated by a piezoelectric actuator.
  • a piezoelectric actuator As a result, extremely fast control movements are possible.
  • the seat in the housing and the valve plug on the valve body does not wear appreciably, despite the short travel of a piezoelectric actuator, the function of the control valve over the entire life of the engine guaranteed.
  • the injector according to the invention is used in common rail fuel injection systems.
  • FIG. 1 an injector with a control valve 15 according to the invention is shown. Fuel is passed through a feed channel 5 to an injection nozzle 7 and through an inlet throttle 9 into a control chamber 11 via a high-pressure port 1.
  • the control chamber 11 is connected via a drain channel 12 and an outlet throttle 13 with a fuel return 17.
  • a bypass 14 establishes a hydraulic connection between the inlet channel 5 and an input of the control valve 15.
  • the control chamber 11 is bounded by a control piston 19.
  • a nozzle needle 21 connects, which prevents the pressurized fuel flows between the injections in the combustion chamber, not shown.
  • Control piston 19 and nozzle needle 21 may also be made in one piece.
  • the nozzle needle 21 has a change in cross section from a larger diameter 25 to a smaller diameter 27. With its larger diameter 25, the nozzle needle 21 is guided in a sleeve 28.
  • FIG. 2 is a first embodiment of a inventive control valve 15 shown enlarged.
  • the two-part housing which consists of the parts 29a and 29b, has a stepped bore 41.
  • a first portion 41a of the stepped bore forms the bypass 14 of the control valve 15.
  • This bypass 14 is hydraulically connected to the inlet channel 5 of the injector (not shown).
  • a second portion 41b forms a spring space, while a third portion 41c of the stepped bore 41 forms the outlet of the control valve 15. This outlet is connected to the fuel return 17 (see FIG. 1 ) hydraulically connected.
  • the outflow channel 12 opens into the second section 41b of the stepped bore with an outflow throttle 13.
  • the outflow channel 12 begins in the control chamber 11 of the injector.
  • a first valve seat 43 is formed between the sections 41b and 41c of the stepped bore 41.
  • a valve cone 47 is formed, which cooperates with the first valve seat 43.
  • a stub 49 is formed on the valve body 45, which abuts with its end face against a plunger 51 of a piezoelectric actuator (not shown).
  • a spring plate 53 is formed on the valve body 45. Between the spring plate 53 and the housing part 29b, a closing spring 55 is clamped, which presses the valve body 45 against the first valve seat 43 and / or against the plunger 51 of the piezoelectric actuator, not shown.
  • FIG. 2 illustrated embodiment of a control valve 15 is designed as a double-switching control valve.
  • formed as a flat seat second valve seat 57 is formed at the transition between the first portion 41 a and 41 b of the stepped bore 41.
  • This second valve seat 57 cooperates with an end face 59 of the valve body 45.
  • switching position of the control valve 15 is a hydraulic connection between the inlet channel 5 via the bypass 14, the flow channel 12 and the outlet throttle 13 to the control chamber eleventh
  • valve body 45 When the valve body 45 is held in this second switch position (not shown), the hydraulic connection is between the drain throttle 13 and the fuel return 17 is opened. As long as this hydraulic connection exists, the nozzle needle 21 of the injector lifts from its nozzle needle seat, so that fuel is injected into the combustion chamber of the internal combustion engine.
  • the spring plate 53 is tuned in its diameter to the diameter of the second portion 41b of the stepped bore 41 that a very small gap "s" between the spring plate 53 and the second portion 41b of the stepped bore remains.
  • This gap s is dimensioned so that the valve body 45 is guided laterally, so that the valve cone 47 always impinges at exactly the same location of the valve seat 43 when the control valve 15 is closed.
  • the slip and thus the wear on the valve cone 47 and the first valve seat 43 is significantly reduced.
  • the gap "s" must be sized so large that the valve cone 47 is centered in the first valve seat 43 itself.
  • the guide of the valve body 45 on the outer diameter of the spring plate 53 is only intended to prevent the valve body 45 is deflected appreciably laterally. If this should happen during operation of the internal combustion engine, would the poppet 47 eccentrically impinge on the valve seat 43, which may result in local overstress. By the force of the closing spring 45, the valve body 45 would then be centered in the first valve seat 43.
  • the resulting relative movement between the first valve seat 43 and valve cone 47 (slip) leads to wear of the components involved, so that the stroke of the valve body 45 significantly changes between the first switching position and the second switching position during the life of the internal combustion engine. This leads to a deteriorated performance and possibly even malfunctions, since, as is known, the travel of piezo actuators is relatively small.
  • a thickness of the gap "s" of less than 0.1 mm has proven to be advantageous.
  • FIG. 2a is a plan view of the spring plate 53 along the line AA shown. From this representation, it is clear that the gap s is not present over the entire circumference of the spring plate, but that the spring plate 53 has three flats 61. These flats 61 allow the outflow of the control amount past the spring plate 53.
  • FIGS. 2b and 2c Further embodiments of passages according to the invention are shown. In the embodiment according to FIG. 2b are four radially arranged grooves 63 provided in the spring plate 53, while in the embodiment according to Figure 2c four holes 65 in the spring plate 53 are present.
  • valve body 45 is guided in the third portion 41 c of the stepped bore 41.
  • the Diameter of the stub 49 is chosen so that again a gap "s" between the stub 49 and the third portion 41 c of the stepped bore 41 sets. Again, it has proved to be advantageous if the gap s is less than 0.05 mm.
  • FIGS. 3a and 3b are sectional views along the line BB of two different versions of inventive stub 49 shown.
  • Flats 61 are provided, while in the embodiment according to FIG. 3b Grooves 63 are provided which extend over the entire length of the guide portion between the stub 49 and the third portion 41 c of the stepped bore 41.
  • the invention is not limited to the explicitly illustrated forms of the flats 61, the grooves 63 and the holes 65.
  • FIG. 4 another embodiment of a control valve 15 according to the invention is shown.
  • the valve body 45 is guided in the region of the portion 41 b of the stepped bore through a sleeve 67.
  • the sleeve 67 is designed as a ring with approximately square cross section, while on the left side, the sleeve 67 has an L-shaped cross-section.
  • the main difference between these two embodiments is in the overlap H 1 and H 2 between the valve body 45 and the sleeve 67th
  • FIG. 5 another embodiment of a control valve 15 according to the invention is shown.
  • the sleeve 67 is disposed between the spring plate 53 and the closing spring 55.
  • two different shapes of sleeves 67 are shown. Both embodiments have in common that the passages are designed in the form of grooves 63.
  • grooves 63 are additionally provided in the valve body.
  • the spring plate 53 bores 65 which also serve to discharge the control and leakage amount from the injector (not shown) through the control valve 15 into the fuel return 17.

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

Abstract

An injector with a double-switching control valve in which a valve body is guided in the housing of the control valve in a way that reduces the wear on a valve cone of the valve body and on a first valve seat in the housing of the control valve.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor für eine Brennkraftmaschine nach dem Oberbegriff von Patentanspruch 1.The invention relates to an injector for an internal combustion engine according to the preamble of patent claim 1.

Ein derartiger Injektor ist beispielsweise durch die US-A-2004/0129804 bekannt geworden.Such an injector is for example by the US-A-2004/0129804 known.

Aus der nachveröffentlichten WO-A-2005/015003 ist weiterhin ein Injektor für eine Brennkraftmaschine mit einem Steuerventil zum Öffnen und Schließen einer Düsennadel bekannt. Das Steuerventil umfasst ein Gehäuse und einen Aktor, wobei in dem Gehäuse eine Stufenbohrung mit einem zweiten Abschnitt (Federraum) zur Aufnahme eines Ventilkörpers ausgebildet ist, wobei ein erster Abschnitt der Stufenbohrung als Bypass und ein dritter Abschnitt der Stufenbohrung als Auslass ausgebildet sind und wobei ein Abflusskanal in den zweiten Abschnitt der Stufenbohrung mündet. Außerdem ist ein erster Ventilsitz vorgesehen, wobei der Ventilkörper einen mit dem ersten Ventilsitz zusammenwirkenden Ventilkegel aufweist. Der Ventilkörper wird von einer in dem zweiten Abschnitt der Stufenbohrung angeordneten Schließfeder gegen einen Stempel eines Aktors gepresst und ist im dritten Abschnitt der Stufenbohrung geführt, wobei in diesem Abschnitt ein oder mehrere Durchlässe für die Steuermenge des Injektors vorhanden sind.From the post-published WO-A-2005/015003 Furthermore, an injector for an internal combustion engine with a control valve for opening and closing a nozzle needle is known. The control valve comprises a housing and an actuator, wherein in the housing a stepped bore having a second portion (spring chamber) is formed for receiving a valve body, wherein a first portion of the stepped bore as a bypass and a third portion of the stepped bore are formed as an outlet and wherein Outflow channel opens into the second section of the stepped bore. In addition, a first valve seat is provided, wherein the valve body has a valve cone cooperating with the first valve seat. The valve body is pressed against a plunger of an actuator by a closing spring arranged in the second section of the stepped bore and is guided in the third section of the stepped bore, wherein one or more passages for the control quantity of the injector are present in this section.

Vorteile der ErfindungAdvantages of the invention

Dadurch, dass der Ventilkörper im zweiten Abschnitt (Federraum) der Stufenbohrung geführt wird, ist gewährleistet, dass der Ventilkegel des Ventilkörpers immer nahezu zentrisch und schlupfarm auf den Ventilsitz des Gehäuses auftrifft. Dadurch werden erstens lokale Überbeanspruchungen von Ventilkegel und Ventilsitz vermieden und es wird der Verschleiß von Ventilsitz und Ventilkegel verringert. Beide Effekte führen dazu, dass sich der Ventilhub im Betrieb der Brennkraftmaschine nur geringfügig ändert, so dass das Betriebsverhalten der Brennkraftmaschine über die gesamte Lebensdauer annähernd gleich bleibt. Dabei ist das Spiel zwischen Stufenbohrung und dem Führungsabschnitt des Ventilkörpers so groß zu wählen, dass sich der Ventilkörper in der Schließstellung des Steuerventils am Ventilsitz des Gehäuses zentriert, da nur dann das Steuerventil dicht schließt.The fact that the valve body is guided in the second section (spring chamber) of the stepped bore, ensures that the valve cone of the Valve body always almost centric and slipping on the valve seat of the housing. This avoids, first, local overstressing of the valve plug and valve seat, and reduces wear of the valve seat and poppet. Both effects cause the valve lift changes only slightly during operation of the internal combustion engine, so that the operating behavior of the internal combustion engine remains approximately the same over the entire life. The game between stepped bore and the guide portion of the valve body is so large that the valve body in the closed position of the control valve centered on the valve seat of the housing, as only then closes the control valve tight.

Vorteilhafte Varianten des erfindungsgemäßen Injektors sehen vor, dass der erste Abschnitt (Einlass) der Stufenbohrung mit einem Steuerraum des Injektors in Verbindung steht, während der dritte Abschnitt (Auslass) der Stufenbohrung mit einem Kraftstoffrücklauf in Verbindung steht.Advantageous variants of the injector according to the invention provide that the first section (inlet) of the stepped bore communicates with a control chamber of the injector, while the third section (outlet) of the stepped bore communicates with a fuel return.

In weiterer vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, dass die Schließfeder auf den Ventilkörper entgegen der Betätigungsrichtung des Aktors einwirkt. Dadurch ist gewährleistet, dass der Ventilkörper stets eine definierte Position einnimmt und das Steuerventil bei stromlos geschaltetem Aktor geschlossen wird.In a further advantageous embodiment of the invention it is provided that the closing spring acts on the valve body against the actuating direction of the actuator. This ensures that the valve body always occupies a defined position and the control valve is closed when the actuator is de-energized.

Dabei hat es sich als vorteilhaft erwiesen, wenn die Schließfeder sich mindestens mittelbar gegen das Gehäuse und einen Federteller des Ventilkörpers abstützt.It has proven to be advantageous if the closing spring is at least indirectly supported against the housing and a spring plate of the valve body.

Dabei ist es alternativ möglich, dass der Ventilkörper am Federteller geführt wird oder dass im Federraum eine Hülse vorgesehen ist und dass der Ventilkörper von der Hülse geführt wird.It is alternatively possible that the valve body is guided on the spring plate or that a sleeve is provided in the spring chamber and that the valve body is guided by the sleeve.

Damit die Steuermenge das erfindungsgemäße Steuerventil trotz der Führung des Ventilkörpers in dem Gehäuse durchströmen kann, sind die Durchlässe alternativ als in Längsrichtung des Ventilkörpers verlaufende Nuten, Abflachungen und/oder Längsbohrungen ausgebildet. Dadurch kann der Strömungswiderstand des Steuerventils in geöffnetem Zustand so weit reduziert werden, dass die Funktion des Injektors nicht durch die Führung des Ventilkörpers in der Stufenbohrung beeinträchtigt wird. Um die Herstellung und Montage zu vereinfachen, kann das Gehäuse zweiteilig ausgeführt sein. Dabei kann das Steuerventil sowohl als separates Bauteil als auch in den Injektor integriert werden. Im letztgenannten Fall ist das Gehäuse des Steuerventils gleichzeitig auch das Gehäuse des Injektors.In order for the control quantity to be able to flow through the control valve according to the invention in the housing despite the guidance of the valve body, the passages are alternatively designed as grooves, flattenings and / or longitudinal bores extending in the longitudinal direction of the valve body. Thereby, the flow resistance of the control valve in the open state can be reduced so far that the function of the injector is not affected by the leadership of the valve body in the stepped bore. To the manufacture and To simplify assembly, the housing can be made in two parts. In this case, the control valve can be integrated both as a separate component and in the injector. In the latter case, the housing of the control valve is also the housing of the injector at the same time.

Vorteilhafterweise kann das Steuerventil als 2/3-Wege-Steuerventil ausgeführt sein. Dadurch können Mehrfacheinspritzungen leichter realisiert werden und es bestehen zusätzliche Möglichkeiten der Einspritzverlaufsformung.Advantageously, the control valve can be designed as a 2/3-way control valve. As a result, multiple injections can be realized more easily and there are additional possibilities of injection molding.

Um die Vorteile des erfindungsgemäßen Injektors mit dem erfindungsgemäßen Steuerventil bestmöglich auszunutzen, kann der Ventilkörper von einem Piezoaktor betätigt werden. Dadurch sind extrem schnelle Steuerbewegungen möglich. Weil durch die konstruktive Ausgestaltung des erfindungsgemäßen Steuerventils der Sitz im Gehäuse und der Ventilkegel am Ventilkörper nicht nennenswert verschleißt, ist trotz der kurzen Stellwege eines Piezoaktors die Funktion des Steuerventils über die gesamte Lebensdauer der Brennkraftmaschine gewährleistet.To best exploit the advantages of the injector according to the invention with the control valve according to the invention, the valve body can be actuated by a piezoelectric actuator. As a result, extremely fast control movements are possible. Because of the structural design of the control valve according to the invention, the seat in the housing and the valve plug on the valve body does not wear appreciably, despite the short travel of a piezoelectric actuator, the function of the control valve over the entire life of the engine guaranteed.

Bevorzugt wird der erfindungsgemäße Injektor in Common-Rail-Kraftstoffeinspritzsystemen eingesetzt.Preferably, the injector according to the invention is used in common rail fuel injection systems.

Weitere Vorteile und vorteilhafte Ausgestaltungen sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the following drawings, the description and the claims can be removed.

Zeichnungendrawings

Es zeigen:

Figur 1
die schematische Darstellung eines Injektors und
Figuren
2, 4 und 5 Ausführungsbeispiele erfindungsgemäßer Steuerventile.
Show it:
FIG. 1
the schematic representation of an injector and
characters
2, 4 and 5 embodiments of inventive control valves.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Injektor mit einem erfindungsgemäßen Steuerventil 15 dargestellt. Über einen Hochdruckanschluss 1 wird Kraftstoff durch einen Zulaufkanal 5 zu einer Einspritzdüse 7 sowie durch eine Zulaufdrossel 9 in einen Steuerraum 11 geleitet. Der Steuerraum 11 ist über einen Abflusskanal 12 und eine Ablaufdrossel 13 mit einem Kraftstoffrücklauf 17 verbunden. Ein Bypass 14 stellt eine hydraulische Verbindung zwischen dem Zulaufkanal 5 und einem Eingang des Steuerventils 15 her.In FIG. 1 an injector with a control valve 15 according to the invention is shown. Fuel is passed through a feed channel 5 to an injection nozzle 7 and through an inlet throttle 9 into a control chamber 11 via a high-pressure port 1. The control chamber 11 is connected via a drain channel 12 and an outlet throttle 13 with a fuel return 17. A bypass 14 establishes a hydraulic connection between the inlet channel 5 and an input of the control valve 15.

Der Steuerraum 11 wird von einem Steuerkolben 19 begrenzt. An den Steuerkolben 19 schließt eine Düsennadel 21 an, die verhindert, dass der unter Druck stehende Kraftstoff zwischen den Einspritzungen in den nicht dargestellten Brennraum fließt. Steuerkolben 19 und Düsennadel 21 können auch einstückig ausgeführt sein. Die Düsennadel 21 weist eine Querschnittsänderung von einem größeren Durchmesser 25 auf einen kleineren Durchmesser 27 auf. Mit ihrem größeren Durchmesser 25 ist die Düsennadel 21 in einer Hülse 28 geführt.The control chamber 11 is bounded by a control piston 19. To the control piston 19, a nozzle needle 21 connects, which prevents the pressurized fuel flows between the injections in the combustion chamber, not shown. Control piston 19 and nozzle needle 21 may also be made in one piece. The nozzle needle 21 has a change in cross section from a larger diameter 25 to a smaller diameter 27. With its larger diameter 25, the nozzle needle 21 is guided in a sleeve 28.

Bei geschlossener Ablaufdrossel 13 ist die auf eine Stirnfläche 33 des Steuerkolbens 19 wirkende hydraulische Kraft größer als die auf die Querschnittsänderung wirkende hydraulische Kraft, weil die Stirnfläche des Steuerkolbens 19 größer als die Ringfläche der Querschnittsänderung ist. In Folge dessen wird die Düsennadel 21 in einen Düsennadelsitz 35 gepresst und dichtet den Zulaufkanal 5 zum nicht dargestellten Brennraum ab.When the outlet throttle 13 is closed, the hydraulic force acting on an end surface 33 of the control piston 19 is greater than the hydraulic force acting on the change in cross section, because the end face of the control piston 19 is larger than the annular surface of the change in cross section. As a result, the nozzle needle 21 becomes a nozzle needle seat Pressed 35 and seals the inlet channel 5 to the combustion chamber, not shown.

Wenn die nicht dargestellte Hochdruckpumpe des Kraftstoffeinspritzsystems nicht angetrieben wird, weil der Motor steht, dann presst eine auf einen Absatz 37 der Düsennadel 21 wirkende Düsenfeder 39 die Einspritzdüse 7 gegen den Düsennadelsitz 35, so dass der Injektor geschlossen wird.When the high-pressure pump, not shown, of the fuel injection system is not driven because the engine is stopped, then acting on a shoulder 37 of the nozzle needle 21 nozzle spring 39 presses the injector 7 against the nozzle needle seat 35, so that the injector is closed.

Wenn durch eine geeignete Ansteuerung des Steuerventils 15 eine hydraulische Verbindung zwischen der Ablaufdrossel 13 und dem Kraftstoffrücklauf 17 hergestellt wird, sinkt der Druck im Steuerraum 11 und damit die auf die Stirnfläche 33 des Steuerkolbens 19 wirkende hydraulische Kraft. Sobald diese hydraulische Kraft kleiner ist als die auf die Querschnittsänderung wirkende hydraulische Kraft, öffnet die Düsennadel 21, so dass der Kraftstoff 3 durch die nicht dargestellten Spritzlöcher in den Brennraum gelangen kann. Diese indirekte Ansteuerung der Düsennadel 21 über ein hydraulisches Kraftverstärkersystem ist notwendig, weil die zu einem schnellen Öffnen der Düsennadel 21 benötigten Kräfte mit dem Steuerventil 15 nicht direkt erzeugt werden können. Die dabei zusätzlich zu der in den Brennraum eingespritzten Kraftstoffmenge benötigte sogenannte "Steuermenge" gelangt über die Zulaufdrossel 9, den Steuerraum 11 und das Steuerventil 15 in den Kraftstoffrücklauf 17. Zwischen den Einspritzungen wird die Ablaufdrossel 13 durch das Steuerventil 15 verschlossen. Das Steuerventil 15 kann durch elektromagnetische oder piezoelektrische Aktoren betätigt werden.If a hydraulic connection between the outlet throttle 13 and the fuel return 17 is produced by a suitable control of the control valve 15, the pressure in the control chamber 11 and thus the force acting on the end face 33 of the control piston 19 hydraulic force decreases. As soon as this hydraulic force is less than the hydraulic force acting on the cross-sectional change, the nozzle needle 21 opens so that the fuel 3 can enter the combustion chamber through the injection holes (not shown). This indirect control of the nozzle needle 21 via a hydraulic power amplifier system is necessary because the forces required to rapidly open the nozzle needle 21 with the control valve 15 can not be generated directly. The so-called "control quantity" required in addition to the amount of fuel injected into the combustion chamber passes via the inlet throttle 9, the control chamber 11 and the control valve 15 into the fuel return 17. Between the injections, the outlet throttle 13 is closed by the control valve 15. The control valve 15 can be actuated by electromagnetic or piezoelectric actuators.

In Figur 2 ist ein erstes Ausführungsbeispiel eines erfindungsgemäßen Steuerventils 15 vergrößert dargestellt. Das zweiteilige Gehäuse, welches aus den Teilen 29a und 29b besteht, weist eine Stufenbohrung 41 auf. Ein erster Abschnitt 41a der Stufenbohrung bildet den Bypass 14 des Steuerventils 15. Dieser Bypass 14 ist mit dem Zulaufkanal 5 des Injektors (nicht dargestellt) hydraulisch verbunden. Ein zweiter Abschnitt 41b bildet einen Federraum, während ein dritter Abschnitt 41c der Stufenbohrung 41 den Auslass des Steuerventils 15 bildet. Dieser Auslass ist mit dem Kraftstoffrücklauf 17 (siehe Figur 1) hydraulisch verbunden.In FIG. 2 is a first embodiment of a inventive control valve 15 shown enlarged. The two-part housing, which consists of the parts 29a and 29b, has a stepped bore 41. A first portion 41a of the stepped bore forms the bypass 14 of the control valve 15. This bypass 14 is hydraulically connected to the inlet channel 5 of the injector (not shown). A second portion 41b forms a spring space, while a third portion 41c of the stepped bore 41 forms the outlet of the control valve 15. This outlet is connected to the fuel return 17 (see FIG. 1 ) hydraulically connected.

In den zweiten Abschnitt 41b der Stufenbohrung mündet der Abflusskanal 12 mit einer Ablaufdrossel 13. Der Abflusskanal 12 beginnt im Steuerraum 11 des Injektors.The outflow channel 12 opens into the second section 41b of the stepped bore with an outflow throttle 13. The outflow channel 12 begins in the control chamber 11 of the injector.

Zwischen den Abschnitten 41b und 41c der Stufenbohrung 41 ist ein erster Ventilsitz 43 ausgebildet. An einem Ventilkörper 45 ist ein Ventilkegel 47 ausgebildet, der mit dem ersten Ventilsitz 43 zusammenwirkt. Oberhalb des Ventilkegels 47 ist an dem Ventilkörper 45 ein Stummel 49 ausgebildet, der mit seiner Stirnfläche an einem Stempel 51 eines Piezoaktors (nicht dargestellt) anliegt. Unterhalb des Ventilkegels 47 ist ein Federteller 53 an dem Ventilkörper 45 ausgebildet. Zwischen dem Federteller 53 und dem Gehäuseteil 29b ist eine Schließfeder 55 eingespannt, welche den Ventilkörper 45 gegen den ersten Ventilsitz 43 und/oder gegen den Stempel 51 des nicht dargestellten Piezoaktors drückt. In der in Figur 2 dargestellten ersten Schaltstellung des Steuerventils 15 ist der Piezoaktor (nicht dargestellt) nicht bestromt, so dass der Ventilkegel 47 des Ventilkörpers 55 an dem ersten Ventilsitz aufliegt. Infolgedessen ist das Steuerventil 15 geschlossen. Der Ventilkörper 45 ist also zwischen dem Stempel 51 und der Schließfeder 55 eingespannt.Between the sections 41b and 41c of the stepped bore 41, a first valve seat 43 is formed. On a valve body 45, a valve cone 47 is formed, which cooperates with the first valve seat 43. Above the valve cone 47, a stub 49 is formed on the valve body 45, which abuts with its end face against a plunger 51 of a piezoelectric actuator (not shown). Below the valve cone 47, a spring plate 53 is formed on the valve body 45. Between the spring plate 53 and the housing part 29b, a closing spring 55 is clamped, which presses the valve body 45 against the first valve seat 43 and / or against the plunger 51 of the piezoelectric actuator, not shown. In the in FIG. 2 shown first switching position of the control valve 15, the piezoelectric actuator (not shown) is not energized, so that the valve cone 47 of the valve body 55 rests against the first valve seat. As a result, the control valve 15 closed. The valve body 45 is thus clamped between the punch 51 and the closing spring 55.

Das in Figur 2 dargestellte Ausführungsbeispiel eines erfindungsgemäßen Steuerventils 15 ist als doppelt schaltendes Steuerventil ausgeführt. Zu diesem Zweck ist an dem Übergang zwischen dem ersten Abschnitt 41a und 41b der Stufenbohrung 41 ein als Flachsitz ausgebildeter zweiter Ventilsitz 57 ausgebildet. Dieser zweite Ventilsitz 57 wirkt mit einer Stirnfläche 59 des Ventilkörpers 45 zusammen. In der in Figur 2 dargestellten Schaltstelllung des Steuerventils 15 besteht eine hydraulische Verbindung zwischen dem Zulaufkanal 5 über den Bypass 14, den Ablaufkanal 12 und die Ablaufdrossel 13 zu dem Steuerraum 11.This in FIG. 2 illustrated embodiment of a control valve 15 according to the invention is designed as a double-switching control valve. For this purpose, formed as a flat seat second valve seat 57 is formed at the transition between the first portion 41 a and 41 b of the stepped bore 41. This second valve seat 57 cooperates with an end face 59 of the valve body 45. In the in FIG. 2 illustrated switching position of the control valve 15 is a hydraulic connection between the inlet channel 5 via the bypass 14, the flow channel 12 and the outlet throttle 13 to the control chamber eleventh

Wenn der nicht dargestellte Piezoaktor bestromt wird, bewegt sich der Stempel 51 in Figur 2 nach unten, so dass der Ventilkegel 47 des Ventilkörpers 45 vom ersten Ventilsitz 43 abhebt und kurzzeitig in der Schaltphase eine hydraulische Verbindung zwischen dem Abschnitt 41a der Stufenbohrung und dem Kraftstoffrücklauf 17 hergestellt wird. Wenn nun der Ventilkörper 45 so weit in Richtung des zweiten Ventilsitzes 57 bewegt wird, dass die Stirnfläche 59 des Ventilkörpers 45 auf dem zweiten Ventilsitz aufliegt, wird die hydraulische Verbindung zwischen dem Abschnitt 41a der Stufenbohrung, bzw. dem Bypass 14, und dem Kraftstoffrücklauf 17 wieder verschlossen. Bei offenem ersten Ventilsitz 43 und geschlossenem zweiten Ventilsitz 57 ist die Ablaufdrossel 13 geöffnet.When the piezoelectric actuator, not shown, is energized, the punch 51 moves in FIG. 2 down, so that the valve cone 47 of the valve body 45 lifts from the first valve seat 43 and briefly in the switching phase, a hydraulic connection between the portion 41 a of the stepped bore and the fuel return 17 is made. Now, when the valve body 45 is moved so far in the direction of the second valve seat 57, that the end face 59 of the valve body 45 rests on the second valve seat, the hydraulic connection between the portion 41 a of the stepped bore, or the bypass 14, and the fuel return 17th closed again. With open first valve seat 43 and closed second valve seat 57, the outlet throttle 13 is opened.

Wenn der Ventilkörper 45 in dieser zweiten Schaltstellung (nicht dargestellt) gehalten wird, ist die hydraulische Verbindung zwischen der Ablaufdrossel 13 und dem Kraftstoffrücklauf 17 geöffnet. Solange diese hydraulische Verbindung besteht, hebt die Düsennadel 21 des Injektors von ihrem Düsennadelsitz ab, so dass Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird.When the valve body 45 is held in this second switch position (not shown), the hydraulic connection is between the drain throttle 13 and the fuel return 17 is opened. As long as this hydraulic connection exists, the nozzle needle 21 of the injector lifts from its nozzle needle seat, so that fuel is injected into the combustion chamber of the internal combustion engine.

Wird der erste Ventilsitz 43 wieder geschlossen, besteht eine hydraulische Verbindung zwischen dem Abschnitt 41a der Stufenbohrung, bzw. dem Bypass 14, und dem Abflusskanal 12 und der Steuerraum 11 wird sowohl von der Zulaufdrossel 9 als auch dem Bypass14 mit Kraftstoff gefüllt. Dadurch wird ein schnelles Schließen der Düsennadel 21 erreicht.When the first valve seat 43 is closed again, there is a hydraulic connection between the portion 41 a of the stepped bore, or the bypass 14, and the discharge channel 12 and the control chamber 11 is filled with fuel both from the inlet throttle 9 and the bypass 14. As a result, a rapid closing of the nozzle needle 21 is achieved.

Bei dem erfindungsgemäßen Steuerventil 15 ist nun vorgesehen, dass beispielsweise der Federteller 53 in seinem Durchmesser so auf den Durchmesser des zweiten Abschnitts 41b der Stufenbohrung 41 abgestimmt ist, dass ein sehr kleiner Spalt "s" zwischen dem Federteller 53 und dem zweiten Abschnitt 41b der Stufenbohrung verbleibt. Dieser Spalt s ist so bemessen, dass der Ventilkörper 45 seitlich geführt wird, so dass der Ventilkegel 47 immer an genau derselben Stelle des Ventilsitzes 43 auftrifft, wenn das Steuerventil 15 geschlossen wird. Dadurch wird der Schlupf und damit der Verschleiß an Ventilkegel 47 und erstem Ventilsitz 43 deutlich verringert.In the control valve 15 according to the invention is now provided that, for example, the spring plate 53 is tuned in its diameter to the diameter of the second portion 41b of the stepped bore 41 that a very small gap "s" between the spring plate 53 and the second portion 41b of the stepped bore remains. This gap s is dimensioned so that the valve body 45 is guided laterally, so that the valve cone 47 always impinges at exactly the same location of the valve seat 43 when the control valve 15 is closed. As a result, the slip and thus the wear on the valve cone 47 and the first valve seat 43 is significantly reduced.

Andererseits muss der Spalt "s" so groß bemessen sein, dass der Ventilkegel 47 sich in dem ersten Ventilsitz 43 selbst zentriert. Die Führung des Ventilkörpers 45 am Außendurchmesser des Federtellers 53 soll lediglich verhindern, dass der Ventilkörper 45 nennenswert seitlich ausgelenkt wird. Wenn dies während des Betriebs der Brennkraftmaschine passieren sollte, würde der Ventilkegel 47 außermittig auf den Ventilsitz 43 auftreffen, was lokale Überbeanspruchungen zur Folge haben kann. Durch die Kraft der Schließfeder 45 würde der Ventilkörper 45 anschließend im ersten Ventilsitz 43 zentriert werden. Die dabei entstehende Relativbewegung zwischen erstem Ventilsitz 43 und Ventilkegel 47 (Schlupf) führt zu einem Verschleiß der beteiligten Bauteile, so dass sich der Hub des Ventilkörpers 45 zwischen der ersten Schaltstellung und der zweiten Schaltstellung während der Lebensdauer der Brennkraftmaschine signifikant ändert. Dies führt zu einem verschlechterten Betriebsverhalten und möglicherweise sogar zu Funktionsstörungen, da bekanntermaßen der Stellweg von Piezoaktoren verhältnismäßig klein ist. In konkreten Ausführungen hat sich eine Dicke des Spaltes "s" von kleiner als 0,1 mm als vorteilhaft erwiesen.On the other hand, the gap "s" must be sized so large that the valve cone 47 is centered in the first valve seat 43 itself. The guide of the valve body 45 on the outer diameter of the spring plate 53 is only intended to prevent the valve body 45 is deflected appreciably laterally. If this should happen during operation of the internal combustion engine, would the poppet 47 eccentrically impinge on the valve seat 43, which may result in local overstress. By the force of the closing spring 45, the valve body 45 would then be centered in the first valve seat 43. The resulting relative movement between the first valve seat 43 and valve cone 47 (slip) leads to wear of the components involved, so that the stroke of the valve body 45 significantly changes between the first switching position and the second switching position during the life of the internal combustion engine. This leads to a deteriorated performance and possibly even malfunctions, since, as is known, the travel of piezo actuators is relatively small. In concrete embodiments, a thickness of the gap "s" of less than 0.1 mm has proven to be advantageous.

In der Figur 2a ist eine Draufsicht auf den Federteller 53 entlang der Linie A-A dargestellt. Aus dieser Darstellung wird deutlich, dass der Spalt s nicht über den gesamten Umfang des Federtellers vorhanden ist, sondern dass der Federteller 53 drei Abflachungen 61 aufweist. Diese Abflachungen 61 ermöglichen das Abströmen der Steuermenge am Federteller 53 vorbei. In den Figuren 2b und 2c sind weitere Ausführungsformen erfindungsgemäßer Durchlässe dargestellt. Bei dem Ausführungsbeispiel gemäß Figur 2b sind vier radial angeordnete Nuten 63 im Federteller 53 vorgesehen, während bei dem Ausführungsbeispiel gemäß Figur 2c vier Bohrungen 65 im Federteller 53 vorhanden sind.In the FIG. 2a is a plan view of the spring plate 53 along the line AA shown. From this representation, it is clear that the gap s is not present over the entire circumference of the spring plate, but that the spring plate 53 has three flats 61. These flats 61 allow the outflow of the control amount past the spring plate 53. In the FIGS. 2b and 2c Further embodiments of passages according to the invention are shown. In the embodiment according to FIG. 2b are four radially arranged grooves 63 provided in the spring plate 53, while in the embodiment according to Figure 2c four holes 65 in the spring plate 53 are present.

Bei dem nicht erfindungsgemäßen Beispiel gemäß Figur 3 wird der Ventilkörper 45 in dem dritten Abschnitt 41c der Stufenbohrung 41 geführt. Dies bedeutet, dass der Durchmesser des Stummels 49 so gewählt wird, dass sich wieder ein Spalt "s" zwischen dem Stummel 49 und dem dritten Abschnitt 41c der Stufenbohrung 41 einstellt. Auch hier hat es sich als vorteilhaft erwiesen, wenn der Spalt s kleiner 0,05 mm beträgt.In the example not according to the invention FIG. 3 For example, the valve body 45 is guided in the third portion 41 c of the stepped bore 41. This means that the Diameter of the stub 49 is chosen so that again a gap "s" between the stub 49 and the third portion 41 c of the stepped bore 41 sets. Again, it has proved to be advantageous if the gap s is less than 0.05 mm.

Auch bei diesem Beispiel müssen Durchlässe am Ventilkörper 45 vorgesehen werden, dort wo der Ventilkörper 45 in der Stufenbohrung 41 geführt wird. In den Figuren 3a und 3b sind Schnittdarstellungen entlang der Linie B-B von zwei verschiedenen Ausführungen erfindungsgemäßer Stummel 49 dargestellt. Bei dem Ausführungsbeispiel gemäß Figur 3a sind Abflachungen 61 vorgesehen, während bei dem Ausführungsbeispiel gemäß Figur 3b Nuten 63 vorgesehen sind, die sich über die gesamte Länge des Führungsabschnittes zwischen dem Stummel 49 und dem dritten Abschnitt 41c der Stufenbohrung 41 erstrecken. Selbstverständlich ist die Erfindung nicht auf die explizit dargestellten Formen der Abflachungen 61, der Nuten 63 und der Bohrungen 65 beschränkt.In this example, passages must be provided on the valve body 45, where the valve body 45 is guided in the stepped bore 41. In the FIGS. 3a and 3b are sectional views along the line BB of two different versions of inventive stub 49 shown. In the embodiment according to FIG. 3a Flats 61 are provided, while in the embodiment according to FIG. 3b Grooves 63 are provided which extend over the entire length of the guide portion between the stub 49 and the third portion 41 c of the stepped bore 41. Of course, the invention is not limited to the explicitly illustrated forms of the flats 61, the grooves 63 and the holes 65.

In Figur 4 ist ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Steuerventils 15 dargestellt. Bei diesem Ausführungsbeispiel wird der Ventilkörper 45 im Bereich des Abschnitts 41b der Stufenbohrung durch eine Hülse 67 geführt.In FIG. 4 another embodiment of a control valve 15 according to the invention is shown. In this embodiment, the valve body 45 is guided in the region of the portion 41 b of the stepped bore through a sleeve 67.

Auf der rechten Seite von Figur 4 ist die Hülse 67 als Ring mit annähernd quadratischem Querschnitt ausgeführt, während er auf der linken Seite die Hülse 67 einen L-förmigen Querschnitt aufweist. Der wesentliche Unterschied zwischen diesen beiden Ausführungsformen besteht in der Überdeckung H1 und H2 zwischen dem Ventilkörper 45 und der Hülse 67.On the right side of FIG. 4 the sleeve 67 is designed as a ring with approximately square cross section, while on the left side, the sleeve 67 has an L-shaped cross-section. The main difference between these two embodiments is in the overlap H 1 and H 2 between the valve body 45 and the sleeve 67th

Um die Steuermenge bei geöffnetem Steuerventil 15 trotz des schmalen Spaltes s zwischen dem Innendurchmesser der Hülse 67 und dem Außendurchmesser des Ventilkörpers 45 abführen zu können, sind in der Hülse 67 und/oder dem Ventilkörper 45 Längsnuten 63 vorgesehen. In den Detailansichten 4a und 4b sind zwei verschiedene Formen von Querschnitten der Nuten 63 dargestellt. Welcher dieser Formen der Vorzug gegeben wird, hängt von den Platzverhältnissen und der abzuführenden Steuermenge ab.In order to discharge the control amount with open control valve 15 despite the narrow gap s between the inner diameter of the sleeve 67 and the outer diameter of the valve body 45, 45 longitudinal grooves 63 are provided in the sleeve 67 and / or the valve body. In the detail views 4a and 4b, two different shapes of cross sections of the grooves 63 are shown. Which of these forms is given preference depends on the space available and the amount of tax to be deducted.

In Figur 5 ist ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Steuerventils 15 dargestellt. Bei diesem Ausführungsbeispiel ist die Hülse 67 zwischen dem Federteller 53 und der Schließfeder 55 angeordnet. Auch bei der Figur 5 sind auf der rechten und auf der linken Seite zwei verschiedene Formen von Hülsen 67 dargestellt. Beiden Ausführungsformen ist gemeinsam, dass die Durchlässe in Form von Nuten 63 ausgeführt sind. Bei der in Figur 5 auf der rechten Seite dargestellten Ausführungsform sind zusätzlich im Ventilkörper 45 Nuten 63 vorgesehen. Außerdem weist der Federteller 53 Bohrungen 65 auf, die ebenfalls dazu dienen, die Steuer- und Leckagemenge aus dem Injektor (nicht dargestellt) durch das Steuerventil 15 hindurch in den Kraftstoffrücklauf 17 abzuführen.In FIG. 5 another embodiment of a control valve 15 according to the invention is shown. In this embodiment, the sleeve 67 is disposed between the spring plate 53 and the closing spring 55. Also at the FIG. 5 On the right and on the left side two different shapes of sleeves 67 are shown. Both embodiments have in common that the passages are designed in the form of grooves 63. At the in FIG. 5 On the right side illustrated embodiment 45 grooves 63 are additionally provided in the valve body. In addition, the spring plate 53 bores 65, which also serve to discharge the control and leakage amount from the injector (not shown) through the control valve 15 into the fuel return 17.

Claims (13)

  1. Injector for an internal combustion engine, having a control valve (15) for opening and closing a nozzle needle (21), with the control valve (15) comprising a housing (29) and an actuator, with a stepped bore (41) having a second section (41b) for holding a valve body (45) being formed in the housing (29), with a first section (41a) of the stepped bore (41) being formed as a bypass (14), and with a third section (41c) of the stepped bore (41) being formed as an outlet, with an outflow duct (12) opening out into the second section (41b) of the stepped bore (41), having a first valve seat (43) which interacts with the valve body (45), with the valve body (45) being pressed by a closing spring (55) against a plunger (51) of an actuator,
    characterized
    in that the valve body (45) has a valve cone (47) which interacts with the first valve seat (43), in that the closing spring (55) is arranged in the second section (41b) of the stepped bore (41), and in that the valve body (45) is guided in the second section (41b) of the stepped bore (41), with one or more passages for the control quantity of the injector being provided in said section (41b).
  2. Injector according to Claim 1, characterized in that the first section (41a) of the stepped bore (41) is connected to a supply duct (5) of the injector.
  3. Injector according to Claim 1 or 2, characterized in that the third section (41c) of the stepped bore (41) is connected to a fuel return line (17).
  4. Injector according to one of the preceding claims, characterized in that the closing spring (55) acts on the valve body (45) counter to the actuation direction of the actuator.
  5. Injector according to Claim 4, characterized in that the closing spring (55) is supported at least indirectly against the housing (29) and against a plate spring (53) of the valve body (45).
  6. Injector according to Claim 5, characterized in that the valve body (45) is guided on the plate spring (53).
  7. Injector according to one of the preceding claims, characterized in that a sleeve (67) is provided in the second section (41b) of the stepped bore (41), and in that the valve body (45) is guided by the sleeve (67).
  8. Injector according to one of the preceding claims, characterized in that the passage(s) is/are formed as grooves (63), flattened portions (61) and/or longitudinal bores (65) which run in the longitudinal direction of the valve body (45).
  9. Injector according to one of the preceding claims, characterized in that a second valve seat (57) is formed at the transition between the first and second sections (41a, 41b) of the stepped bore (41), and in that an end surface (33) of the valve body (45) interacts with the second valve seat (57).
  10. Injector according to one of the preceding claims, characterized in that the housing (29) is of two-part design.
  11. Injector according to one of the preceding claims, characterized in that the control valve (15) is a 3/2 control valve.
  12. Injector according to one of the preceding claims, characterized in that the valve body (45) is actuated by a piezoelectric actuator.
  13. Injector according to one of the preceding claims, characterized in that the injector is used in a common rail fuel injection system.
EP05808118A 2004-12-22 2005-11-22 Injector for a fuel-injection system in an internal combustion engine Not-in-force EP1831537B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004061800A DE102004061800A1 (en) 2004-12-22 2004-12-22 Injector of a fuel injection system of an internal combustion engine
PCT/EP2005/056138 WO2006067015A1 (en) 2004-12-22 2005-11-22 Injector for a fuel-injection system in an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1831537A1 EP1831537A1 (en) 2007-09-12
EP1831537B1 true EP1831537B1 (en) 2009-03-04

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US (1) US7621258B2 (en)
EP (1) EP1831537B1 (en)
CN (1) CN101061308B (en)
AT (1) ATE424506T1 (en)
DE (2) DE102004061800A1 (en)
WO (1) WO2006067015A1 (en)

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ATE424506T1 (en) 2009-03-15
DE502005006773D1 (en) 2009-04-16
US7621258B2 (en) 2009-11-24
DE102004061800A1 (en) 2006-07-06
CN101061308B (en) 2010-08-18
CN101061308A (en) 2007-10-24
EP1831537A1 (en) 2007-09-12
US20090145404A1 (en) 2009-06-11
WO2006067015A1 (en) 2006-06-29

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