EP2354526B1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
EP2354526B1
EP2354526B1 EP20110150091 EP11150091A EP2354526B1 EP 2354526 B1 EP2354526 B1 EP 2354526B1 EP 20110150091 EP20110150091 EP 20110150091 EP 11150091 A EP11150091 A EP 11150091A EP 2354526 B1 EP2354526 B1 EP 2354526B1
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EP
European Patent Office
Prior art keywords
valve
bore
fuel injector
chamber
injector according
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
EP20110150091
Other languages
German (de)
French (fr)
Other versions
EP2354526A2 (en
EP2354526A3 (en
Inventor
Hans Brekle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2354526A2 publication Critical patent/EP2354526A2/en
Publication of EP2354526A3 publication Critical patent/EP2354526A3/en
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Publication of EP2354526B1 publication Critical patent/EP2354526B1/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
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member

Definitions

  • the invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
  • a fuel injector comprises a control valve for controlling a hubbeweglichen nozzle needle, on the lifting movement at least one injection port is releasable or closable.
  • the control valve comprises a valve chamber for receiving a liftable valve member having a valve seat cooperating with a valve cone, wherein the valve space is bounded by a throttle plate, in the at least one first bore for connecting the valve chamber with a control chamber and a second bore for connecting the Valve space are formed with a high pressure passage.
  • a fuel injector of the type mentioned above for example, from the published patent application DE 10 2004 061 800 A1 . EP 0781913 and WO 2004005702 out.
  • the fuel injector described herein has a double-switching control valve with a valve body guided in a housing of the control valve so that wear on a poppet of the valve body and on a first valve seat in the housing of the control valve is reduced.
  • the valve body receiving the valve chamber is further connected via a first bore serving as a drain with a control chamber and via a serving as a bypass second bore with an inlet channel.
  • fuel in a first closed position of the valve body, fuel can flow into the control chamber via the bypass and the drainage channel in order to bring about rapid closing of the nozzle needle.
  • the object of the present invention is to effect, while maintaining the overall height, a further relief of the control valve in the region of its valve seat.
  • the fuel injector should be simple, preferably using the most known components, and thus inexpensive to produce.
  • a bypass function should be retained.
  • the proposed to solve the problem fuel injector has a control valve with a valve member, which is inventively traversed by an axially extending bore in which a bolt is accommodated with play.
  • the hydraulic force in the region of the valve seat can be significantly reduced, since the rail pressure no longer acts on the entire valve seat surface, but only on the reduced around the bore or bolt cross-sectional area.
  • the load on the valve seat can be reduced in this way to 65% and below. This in turn means that the rail pressure can be further increased.
  • the fuel injector can therefore be used at system pressures well above 2,000 bar. To implement the measure, it only requires less constructive changes, which essentially affect the valve member itself.
  • the bolt is formed integrally with the throttle plate, i. that the bolt and the throttle plate may be formed as a part or the bolt may be integrally connected to the throttle plate.
  • the bolt may be embedded in the throttle plate.
  • a frictional connection can be made for example via a press connection.
  • the bolt is thus part of the throttle plate and thus fixed in position. The relative to the bolt slidably mounted valve member is guided by the pin or centered with respect to the valve seat.
  • the bolt has the same length in the axial direction as the valve member.
  • the valve member passing through the axially extending bore is thus completely closed by the bolt.
  • the bolt has a smaller length in the axial direction than the valve member.
  • control valve is double-switching and formed on a valve seat facing away from the end of the valve member of the valve member of the control valve, a further sealing surface over which the second bore formed in the throttle plate is releasable or closable. Since the second bore formed in the throttle plate connects the valve chamber to the high-pressure passage, a bypass function is ensured via this second bore.
  • the further formed on the valve member sealing surface allows the release or closing of the bypass bore, wherein in a first closed position of the control valve, in which the valve cone of the valve member abuts the first valve seat, the bypass bore is released, and in a second closed position of the control valve, in which abuts the valve member with its further sealing surface on the throttle plate, the bypass hole is closed.
  • the control valve In the first closed position of the control valve can thus be supplied via the bypass bore under high pressure fuel from the high-pressure passage to the valve chamber, which then formed over a likewise formed in the throttle plate, as Drain serving bore is supplied to the control room. In this way, a faster filling of the control chamber with fuel under high pressure and thus a fast nozzle needle closing can be effected.
  • the second closed position of the control valve in which the valve chamber is connected to a low pressure chamber, the return flow can be reduced by closing the bypass bore.
  • the further sealing surface formed on the valve seat is preferably planar and / or annular and / or cooperates with a flat seat formed on the throttle plate.
  • a sealing surface for closing or releasing the bypass bore can also be formed thereon.
  • the bolt is formed integrally with the throttle plate, only a ring formed on the valve member sealing surface is used to close or the release of the bypass. Accordingly, the bore serving as a bypass is to be guided within the throttle plate. This means that in one piece design of the bolt with the throttle plate, the bypass hole radially offset from the bolt opens into the valve chamber.
  • the mouth region of the bypass bore can also be arranged coaxially to the bolt.
  • At least one throttle point is formed, which is further preferably designed as a coaxial or branching bore with a smaller flow cross-section than the second bore.
  • the formation and position of the throttle point depends in turn on whether the bolt is freely movable or designed as a position-fixed component of the throttle plate. If at least two throttle points are provided, at least one throttle point is formed as a branching bore, which opens radially offset from the bolt in the valve chamber. The formation of at least one throttle point improves the hydraulic design, since this acts to dampen.
  • the throttle point formed in the second bore is preferably arranged on the valve chamber side, ie in the mouth region of the second bore with the valve chamber. This simplifies the formation of the throttle point, as it is the top of the throttle plate is easily accessible.
  • the throttle point may also have been produced by means of laser drilling.
  • a compression spring for biasing the valve member relative to the valve seat is received in the valve chamber.
  • the compression spring is supported on the one hand on the valve cone of the valve member and on the other hand on the throttle plate. On the valve cone this is preferably a radially extending shoulder formed as a spring plate. The valve cone thus has a radial excess over a cylindrical portion of the valve member.
  • the compression spring ensures the installation of the valve member on the valve seat in the closed position of the control valve.
  • a piezoelectric actuator for actuating the control valve. High switching forces can be achieved by means of a piezo actuator or a plurality of piezo actuators combined to form a stack.
  • the Indian FIG. 1 shown known Kraftstoffinjektor has a control valve 1 for actuating a nozzle needle 2, which is axially displaceable in a nozzle body 23 is included.
  • the nozzle body 23 has a bore formed as a high-pressure channel 11, which connects a feed line 19 with at least one injection opening 23 (not shown) formed in the nozzle body 23.
  • the high-pressure fuel is thus supplied via the supply line 19 and the high-pressure passage 11 of the at least one injection nozzle.
  • the high-pressure channel 11 is delimited by means of a throttle plate 7, which is attached axially to the nozzle body 23. Between the throttle plate 7 and the nozzle needle 2, a control chamber 9 is further separated from the high-pressure passage 11 via a control sleeve 22.
  • the movement of the nozzle needle 2 is controllable. If the hydraulic pressure in the control chamber 9 increases, a closing force is exerted on the nozzle needle 2, so that the nozzle needle is transferred into its closed position. The closing process is supported by the pressure force of a closing spring 24. In contrast, falls off the hydraulic pressure in the control chamber 9, the nozzle needle 2 opens by lifting from their sealing seat. In order to cause the pressure increase or pressure drop in the control chamber 9, this is on the one hand via a formed in the throttle plate 7 and an inlet throttle 20 having inlet bore 21 with the supply line 19 and on the other hand via a in the throttle plate. 7 trained and a drain throttle 25 having drain hole connected to a valve chamber 3 of the control valve.
  • the valve chamber 3 is in turn connectable to a low pressure chamber 18, via which the Abêtmenge can be fed to a return.
  • the connection of the valve chamber 3 with the low pressure chamber 18 is made via a corresponding switching position of the control valve 1.
  • a hydraulic connection is provided when a cooperating with a valve seat 5 valve cone 6 of a valve member 4 occupies a position lifted from the valve seat 5 position.
  • the poppet 6 of the valve member 4 seals against the valve seat 5 of the control valve 1
  • a hydraulic connection of the valve chamber 3 to the low-pressure chamber 18 is prevented.
  • a pressure increase in the control chamber 9 can be effected via the inlet bore 21 contained in the inlet throttle 20, which finally leads to the closing of the nozzle needle 2.
  • a bore 10 is provided in the throttle plate 7 further, which connects the valve chamber 3 with the high pressure passage 11 and thus serves as a bypass.
  • the valve member 4 is located with a further sealing surface 14 on a trained flat seat valve seat of the throttle plate 7, thereby closing the serving as a bypass bore 10.
  • fuel from the valve chamber 3 via the valve seat 5 in the low-pressure chamber 18 outflow.
  • the bypass bore 10 is closed, the amount of fuel supplied via the low-pressure chamber 18 to a return line remains low.
  • the control valve 1 by operation of an actuator, such as a piezoelectric actuator (not shown) transferred.
  • a compression spring 17 ensures that the valve member 4 of the control valve 1 returns to its initial position, ie its first closed position.
  • FIG. 2 is an enlarged view of the valve member 4 of the fuel injector according to the Fig. 1 to be taken, which comprises a valve cone 6 cooperating with the valve seat 5. Furthermore, a further sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4, which is engageable with the throttle plate 7 for closing the bore 10 serving as a bypass.
  • valve member 4 of a fuel injector according to the invention.
  • this valve member 4 has a cooperating with the valve seat 5 valve cone 6 and a further sealing surface 14 on the valve cone 6 opposite end face.
  • the valve member 4 has an axially extending bore 12 which completely penetrates the valve member 4.
  • the valve member 4 is thus designed as a hollow body.
  • a bolt 13 is received, which according to the embodiment of the FIG. 3 has the same length as the valve member 4.
  • the bolt 13 may also have a smaller length than the valve member 4.
  • a corresponding embodiment is in the FIG. 4 shown.
  • the bolt 13 is also integrally connected to the throttle plate 7 and thus fixed in position. Consequently, an axial guidance of the lifting valve member 4 is effected via the bolt 13.
  • throttle bodies 15, 16 are formed in the bore serving as a bore, which connect the bore 10 with the valve chamber 3.
  • Both throttle plates 15, 16 are formed as holes with a reduced flow cross-section relative to the bore 10, wherein the bores are guided such that they open radially offset from the bolt 13 in the valve chamber 3.
  • the release and closing of the throttle points 15, 16 and the bypass bore 10 is effected in the present case solely by the sleeve-like executed valve member 4.
  • an annular sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4.
  • the relief caused by the fuel injector according to the invention of the control valve in the region of its valve seat is in the diagram of FIG. 5 shown graphically.
  • different diameters of the bolt 13 are plotted in millimeters, which in the present range from 0 to 1.2 mm.
  • the remaining load is plotted on the y-axis in percent.
  • the graph shows several graphs, each representing a specific seat diameter.
  • the seat diameter varies here between 1.33 mm (bottom graph) and 1.43 mm (top graph). Decisive for the degree of relief is therefore the area ratio between seat diameter and bolt diameter.

Description

Die Erfindung betrifft einen Kraftstoffinjektor für ein Kraftstoffeinspritzsystem, insbesondere ein Common-Rail-Einspritzsystem, mit den Merkmalen des Oberbegriffs des Anspruchs 1. Ein solcher Kraftstoffinjektor umfasst ein Steuerventil zur Ansteuerung einer hubbeweglichen Düsennadel, über deren Hubbewegung wenigstens eine Einspritzöffnung freigebbar oder verschließbar ist. Dabei umfasst das Steuerventil einen Ventilraum zur Aufnahme eines hubbeweglichen Ventilgliedes, das einen mit einem Ventilsitz zusammenwirkenden Ventilkegel besitzt, wobei der Ventilraum von einer Drosselplatte begrenzt wird, in der wenigstens eine erste Bohrung zur Verbindung des Ventilraums mit einem Steuerraum und eine zweite Bohrung zur Verbindung des Ventilraums mit einem Hochdruckkanal ausgebildet sind.The invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1. Such a fuel injector comprises a control valve for controlling a hubbeweglichen nozzle needle, on the lifting movement at least one injection port is releasable or closable. In this case, the control valve comprises a valve chamber for receiving a liftable valve member having a valve seat cooperating with a valve cone, wherein the valve space is bounded by a throttle plate, in the at least one first bore for connecting the valve chamber with a control chamber and a second bore for connecting the Valve space are formed with a high pressure passage.

Stand der TechnikState of the art

Ein Kraftstoffinjektor der vorstehend genannten Art geht beispielsweise aus der Offenlegungsschrift DE 10 2004 061 800 A1 , EP 0781913 und WO 2004005702 hervor. Der hierin beschriebene Kraftstoffinjektor weist ein doppelt schaltendes Steuerventil mit einem Ventilkörper auf, das in einem Gehäuse des Steuerventils geführt ist, so dass der Verschleiß an einem Ventilkegel des Ventilkörpers und an einem ersten Ventilsitz im Gehäuse des Steuerventils verringert wird. Der den Ventilkörper aufnehmende Ventilraum ist ferner über eine als Ablauf dienende erste Bohrung mit einem Steuerraum und über eine als Bypass dienende zweite Bohrung mit einem Zulaufkanal verbunden. Über den Bypass und den Ablaufkanal kann in einer ersten Schließstellung des Ventilkörpers zusätzlich Kraftstoff in den Steuerraum strömen, um ein schnelles Schließen der Düsennadel zu bewirken.A fuel injector of the type mentioned above, for example, from the published patent application DE 10 2004 061 800 A1 . EP 0781913 and WO 2004005702 out. The fuel injector described herein has a double-switching control valve with a valve body guided in a housing of the control valve so that wear on a poppet of the valve body and on a first valve seat in the housing of the control valve is reduced. The valve body receiving the valve chamber is further connected via a first bore serving as a drain with a control chamber and via a serving as a bypass second bore with an inlet channel. In addition, in a first closed position of the valve body, fuel can flow into the control chamber via the bypass and the drainage channel in order to bring about rapid closing of the nozzle needle.

Ausgehend von einem solchen Kraftstoffinjektor besteht die Aufgabe der vorliegenden Erfindung darin, unter Beibehaltung der Bauhöhe eine weitere Entlastung des Steuerventils im Bereich seines Ventilsitzes zu bewirken. Zudem soll der Kraftstoffinjektor einfach, vorzugsweise unter Verwendung der meisten bereits bekannten Bauteile, und damit kostengünstig herstellbar sein. Ferner soll eine Bypassfunktion erhalten bleiben.Based on such a fuel injector, the object of the present invention is to effect, while maintaining the overall height, a further relief of the control valve in the region of its valve seat. In addition, the fuel injector should be simple, preferably using the most known components, and thus inexpensive to produce. Furthermore, a bypass function should be retained.

Zur Lösung der Aufgabe wird der Kraftstoffinjektor mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Erfindung werden in den Unteransprüchen angegeben.To solve the problem, the fuel injector with the features of claim 1 is proposed. Advantageous developments of the invention are specified in the subclaims.

Offenbarung der ErfindungDisclosure of the invention

Der zur Lösung der Aufgabe vorgeschlagene Kraftstoffinjektor weist ein Steuerventil mit einem Ventiglied auf, das erfindungsgemäß von einer axial verlaufenden Bohrung durchsetzt ist, in der ein Bolzen spielbehaftet aufgenommen ist. Durch diese Maßnahme kann die hydraulische Kraft im Bereich des Ventilsitzes deutlich reduziert werden, da der Raildruck nicht mehr auf die gesamte Ventilsitzfläche, sondern nur noch auf die um den Bohrungs- bzw. Bolzenquerschnitt reduzierte Sitzfläche wirkt. Die Belastung des Ventilsitzes kann auf diese Weise auf 65 % und darunter reduziert werden. Dies hat wiederum zur Folge, dass der Raildruck weiter gesteigert werden kann. Der Kraftstoffinjektor ist damit auch bei Systemdrücken deutlich über 2.000 bar einsetzbar. Zur Umsetzung der Maßnahme bedarf es lediglich weniger konstruktiver Änderungen, die im Wesentlichen das Ventilglied selbst betreffen. Sämtliche bekannten Gehäuseteile, insbesondere die bereits bekannte Ventilplatte, können weiter verwendet werden, so dass im Ergebnis auch die Bauhöhe des Kraftstoffinjektors beibehalten werden kann. Der vorgeschlagene Kraftstoffinjektor ist somit in vorhandene Bauräume einsetzbar und erfordert zudem keine Neuauslegung der Steckeranschlüsse. Ferner bleibt bei Verwendung der bekannten Drosselplatte die volle Bypassfunktion erhalten. Der Bolzen ist einstückig mit der Drosselplatte ausgebildet, d.h. dass der Bolzen und die Drosselplatte als ein Teil ausgebildet sein können oder der Bolzen mit der Drosselplatte einstückig verbunden sein kann. Beispielsweise kann der Bolzen in die Drosselplatte eingelassen sein. Eine kraftschlüssige Verbindung kann beispielsweise über eine Pressverbindung hergestellt werden. Der Bolzen ist somit Bestandteil der Drosselplatte und demzufolge lagefixiert. Das gegenüber dem Bolzen verschiebbar gelagerte Ventilglied wird durch den Bolzen geführt bzw. in Bezug auf den Ventilsitz zentriert. Auch dadurch kann die Belastung im Bereich des Ventilsitzes reduziert werden. Die eigentliche Entlastung erfolgt jedoch dadurch, dass der Raildruck nicht mehr auf die gesamte Ventilsitzfläche wirkt, sondern nur noch auf die um den Bohrungs- bzw. Bolzenquerschnitt reduzierte Sitzfläche. Zusätzlich wird eine Entlastung des Aktors zur Betägtigung des Steuerventils erreicht, da zum Öffnen des Steuerventils eine geringere Aktorkraft erforderlich ist. Mit einer Entlastung des Aktors geht ferner ein geringerer Spannungsbedarf einher.The proposed to solve the problem fuel injector has a control valve with a valve member, which is inventively traversed by an axially extending bore in which a bolt is accommodated with play. By this measure, the hydraulic force in the region of the valve seat can be significantly reduced, since the rail pressure no longer acts on the entire valve seat surface, but only on the reduced around the bore or bolt cross-sectional area. The load on the valve seat can be reduced in this way to 65% and below. This in turn means that the rail pressure can be further increased. The fuel injector can therefore be used at system pressures well above 2,000 bar. To implement the measure, it only requires less constructive changes, which essentially affect the valve member itself. All known housing parts, in particular the already known valve plate, can be used further, so that as a result the overall height of the fuel injector can be maintained. The proposed fuel injector can thus be used in existing installation spaces and also requires no redesign of the connector terminals. Furthermore, when using the known throttle plate, the full bypass function is maintained. The bolt is formed integrally with the throttle plate, i. that the bolt and the throttle plate may be formed as a part or the bolt may be integrally connected to the throttle plate. For example, the bolt may be embedded in the throttle plate. A frictional connection can be made for example via a press connection. The bolt is thus part of the throttle plate and thus fixed in position. The relative to the bolt slidably mounted valve member is guided by the pin or centered with respect to the valve seat. This also allows the load in the region of the valve seat can be reduced. However, the actual relief takes place in that the rail pressure no longer acts on the entire valve seat surface, but only on the reduced around the bore or bolt cross-section seat surface. In addition, a relief of the actuator is achieved to Betägtigung the control valve, since a smaller actuator force is required to open the control valve. With a discharge of the actuator is also associated with a lower voltage requirement.

Gemäß einer ersten bevorzugten Ausführungsform besitzt der Bolzen in axialer Richtung die gleiche Länge wie das Ventilglied. Die das Ventilglied durchsetzende axial verlaufende Bohrung wird somit durch den Bolzen vollständig verschlossen. Indem der Bolzen spielbehaftet eingesetzt ist, ist dennoch eine Verschiebung des Bolzens gegenüber dem Ventilglied möglich.According to a first preferred embodiment, the bolt has the same length in the axial direction as the valve member. The valve member passing through the axially extending bore is thus completely closed by the bolt. By the bolt is inserted play, yet a displacement of the bolt relative to the valve member is possible.

Gemäß einer zweiten bevorzugten Ausführungsform besitzt der Bolzen in axialer Richtung eine geringere Länge als das Ventilglied.According to a second preferred embodiment, the bolt has a smaller length in the axial direction than the valve member.

Vorteilhafterweise ist das Steuerventil doppelt schaltend und an einem den Ventilsitz abgewandten Ende des Ventilgliedes des Ventigliedes des Steuerventils eine weitere Dichtfläche ausgebildet, über welche die in der Drosselplatte ausgebildete zweite Bohrung freigebbar oder verschließbar ist. Da die in der Drosselplatte ausgebildete zweite Bohrung den Ventilraum mit dem Hochdruckkanal verbindet, wird über diese zweite Bohrung eine Bypassfunktion gewährleistet. Die weitere am Ventilglied ausgebildete Dichtfläche ermöglicht die Freigabe oder das Verschließen der Bypass-Bohrung, wobei in einer ersten Schließstellung des Steuerventils, in welcher der Ventilkegel des Ventilglieds am ersten Ventilsitz anliegt, die Bypassbohrung freigegeben ist, und in einer zweiten Schließstellung des Steuerventils, in welcher das Ventilglied mit seiner weiteren Dichtfläche an der Drosselplatte anliegt, die Bypass-Bohrung verschlossen ist. In der ersten Schließstellung des Steuerventils kann somit über die Bypassbohrung unter hohem Druck stehender Kraftstoff aus dem Hochdruckkanal dem Ventilraum zugeführt werden, der dann über eine ebenfalls in der Drosselplatte ausgebildete, als Ablauf dienende Bohrung dem Steuerraum zugeführt wird. Auf diese Weise kann ein schnelleres Befüllen des Steuerraums mit unter hohem Druck stehenden Kraftstoff und damit ein schnellers Düsennadelschließen bewirkt werden. In der zweiten Schließstellung des Steuerventils, in welcher der Ventilraum mit einem Niederdruckraum verbunden ist, kann durch Verschließen der Bypass-Bohrung die Rücklaufmenge reduziert werden.Advantageously, the control valve is double-switching and formed on a valve seat facing away from the end of the valve member of the valve member of the control valve, a further sealing surface over which the second bore formed in the throttle plate is releasable or closable. Since the second bore formed in the throttle plate connects the valve chamber to the high-pressure passage, a bypass function is ensured via this second bore. The further formed on the valve member sealing surface allows the release or closing of the bypass bore, wherein in a first closed position of the control valve, in which the valve cone of the valve member abuts the first valve seat, the bypass bore is released, and in a second closed position of the control valve, in which abuts the valve member with its further sealing surface on the throttle plate, the bypass hole is closed. In the first closed position of the control valve can thus be supplied via the bypass bore under high pressure fuel from the high-pressure passage to the valve chamber, which then formed over a likewise formed in the throttle plate, as Drain serving bore is supplied to the control room. In this way, a faster filling of the control chamber with fuel under high pressure and thus a fast nozzle needle closing can be effected. In the second closed position of the control valve, in which the valve chamber is connected to a low pressure chamber, the return flow can be reduced by closing the bypass bore.

Die weitere am Ventilsitz ausgebildete Dichtfläche ist vorzugsweise eben und/oder ringförmig ausgebildet und/oder wirkt mit einem an der Drosselplatte ausgebildeten Flachsitz zusammen. Sofern in der axial verlaufenden Bohrung des Ventilgliedes ein bekannten separater Bolzen aufgenommen ist, kann auch an diesem eine Dichtfläche zum Verschließen oder Freigeben der Bypass-Bohrung ausgebildet sein. Sofern der Bolzen jedoch einstückig mit der Drosselplatte ausgebildet ist, dient lediglich eine ringförmig am Ventilglied ausgebildete Dichtfläche dem Verschließen oder dem Freigeben des Bypasses. Entsprechend ist die als Bypass dienende Bohrung innerhalb der Drosselplatte zu führen. Das heißt, dass bei einstückiger Ausbildung des Bolzens mit der Drosselplatte die Bypass-Bohrung radial versetzt zum Bolzen in den Ventilraum mündet. Bei einem bekannten separat ausgebildeten Bolzen kann der Mündungsbereich der Bypass-Bohrung auch koaxial zum Bolzen angeordnet sein.The further sealing surface formed on the valve seat is preferably planar and / or annular and / or cooperates with a flat seat formed on the throttle plate. If a known separate bolt is accommodated in the axially extending bore of the valve member, a sealing surface for closing or releasing the bypass bore can also be formed thereon. However, if the bolt is formed integrally with the throttle plate, only a ring formed on the valve member sealing surface is used to close or the release of the bypass. Accordingly, the bore serving as a bypass is to be guided within the throttle plate. This means that in one piece design of the bolt with the throttle plate, the bypass hole radially offset from the bolt opens into the valve chamber. In a known separately formed bolt, the mouth region of the bypass bore can also be arranged coaxially to the bolt.

Vorzugsweise ist in der zweiten als Bypass dienenden Bohrung der Drosselplatte wenigstens eine Drosselstelle ausgebildet, welche weiterhin vorzugsweise als koaxiale oder abzweigende Bohrung mit einem geringeren Durchströmungsquerschnitt als die zweite Bohrung ausgebildet ist. Die Ausbildung und Lage der Drosselstelle hängt vorranging wiederum davon ab, ob der Bolzen frei beweglich oder als lagefixierter Bestandteil der Drosselplatte ausgebildet ist. Sind wenigstens zwei Drosselstellen vorgesehen, ist wenigstens eine Drosselstelle als abzweigende Bohrung ausgebildet, die radial versetzt zum Bolzen in den Ventilraum mündet. Die Ausbildung wenigstens einer Drosselstelle verbessert die hydraulische Auslegung, da diese dämpfend wirkt.Preferably, in the second serving as a bypass bore of the throttle plate at least one throttle point is formed, which is further preferably designed as a coaxial or branching bore with a smaller flow cross-section than the second bore. The formation and position of the throttle point depends in turn on whether the bolt is freely movable or designed as a position-fixed component of the throttle plate. If at least two throttle points are provided, at least one throttle point is formed as a branching bore, which opens radially offset from the bolt in the valve chamber. The formation of at least one throttle point improves the hydraulic design, since this acts to dampen.

Des Weiteren ist die in der zweiten Bohrung ausgebildete Drosselstelle bevorzugt ventilraumseitig angeordnet, d.h. im Mündungsbereich der zweiten Bohrung mit dem Ventilraum. Dies vereinfacht die Ausbildung der Drosselstelle, da sie an der Oberseite der Drosselplatte leicht zugänglich ist. Die Drosselstelle kann zudem mittels Laserbohren hergestellt worden sein.Furthermore, the throttle point formed in the second bore is preferably arranged on the valve chamber side, ie in the mouth region of the second bore with the valve chamber. This simplifies the formation of the throttle point, as it is the top of the throttle plate is easily accessible. The throttle point may also have been produced by means of laser drilling.

Gemäß einer weiteren bevorzugten Ausführungsform ist im Ventilraum eine Druckfeder zur Vorspannung des Ventilgliedes gegenüber dem Ventilsitz aufgenommen. Die Druckfeder ist dabei einerseits am Ventilkegel des Ventilgliedes und andererseits an der Drosselplatte abgestützt. Am Ventilkegel ist hierzu bevorzugt eine radial verlaufende Schulter als Federteller ausgebildet. Der Ventilkegel besitzt somit ein radiales Übermaß gegenüber einem zylinderförmigen Abschnitt des Ventilgliedes. Die Druckfeder stellt die Anlage des Ventilgliedes am Ventilsitz in Schließstellung des Steuerventils sicher.According to a further preferred embodiment, a compression spring for biasing the valve member relative to the valve seat is received in the valve chamber. The compression spring is supported on the one hand on the valve cone of the valve member and on the other hand on the throttle plate. On the valve cone this is preferably a radially extending shoulder formed as a spring plate. The valve cone thus has a radial excess over a cylindrical portion of the valve member. The compression spring ensures the installation of the valve member on the valve seat in the closed position of the control valve.

Weiterhin bevorzugt ist ein Piezoaktor zur Betätigung des Steuerventils vorgesehen. Über einen Piezoaktor bzw. mehrere zu einem Stack zusammengesetzte Piezoaktoren können hohe Schaltkräfte realisiert werden.Further preferably, a piezoelectric actuator for actuating the control valve is provided. High switching forces can be achieved by means of a piezo actuator or a plurality of piezo actuators combined to form a stack.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der Zeichnungen näher beschrieben. Diese zeigen:

  • Figur 1 einen Längsschnitt durch einen aus dem Stand der Technik bekannten Kraftstoffinjektor im Bereich des Steuerventils,
  • Figur 2 eine Ansicht des Ventilgliedes des Steuerventils des Kraftstoffinjektors der Figur 1,
  • Figur 3 eine Ansicht eines Ventilgliedes eines Steuerventils eines erfindungsgemäßen Kraftstoffinjektors,
  • Figur 4 einen Längsschnitt durch einen weiteren erfindungsgemäßen Kraftstoffinjektor im Bereich des Steuerventils und
  • Figur 5 ein Diagramm zur Darstellung der bewirkbaren Entlastung des Steuerventils im Bereich des Ventilsitzes.
Preferred embodiments of the invention are described below with reference to the drawings. These show:
  • FIG. 1 a longitudinal section through a known from the prior art fuel injector in the region of the control valve,
  • FIG. 2 a view of the valve member of the control valve of the fuel injector of FIG. 1 .
  • FIG. 3 a view of a valve member of a control valve of a fuel injector according to the invention,
  • FIG. 4 a longitudinal section through another fuel injector according to the invention in the region of the control valve and
  • FIG. 5 a diagram showing the effecting relief of the control valve in the region of the valve seat.

Der in der Figur 1 dargestellte bekannte Kraftstoffinjektor weist ein Steuerventil 1 zur Betätigung einer Düsennadel 2 auf, die in einem Düsenkörper 23 axial verschieblich aufgenommen ist. Hierzu weist der Düsenkörper 23 eine als Hochdruckkanal 11 ausgebildete Bohrung auf, welche eine Zulaufleitung 19 mit wenigstens einer im Düsenkörper 23 ausgebildeten Einspritzöffnung (nicht dargestellt) verbindet. Der unter hohem Druck stehende Kraftstoff wird somit über die Zulaufleitung 19 und den Hochdruckkanal 11 der wenigstens einen Einspritzdüse zugeführt. Der Hochdruckkanal 11 wird über eine axial an den Düsenkörper 23 angesetzte Drosselplatte 7 begrenzt. Zwischen der Drosselplatte 7 und der Düsennadel 2 ist ferner über eine Steuerhülse 22 ein Steuerraum 9 vom Hochdruckkanal 11 abgetrennt. Über den hydraulischen Druck im Steuerraum 9 ist die Bewegung der Düsennadel 2 steuerbar. Steigt der hydraulische Druck im Steuerraum 9 an, wird auf die Düsennadel 2 eine Schließkraft ausgeübt, so dass die Düsennadel in ihre Schließstellung überführt wird. Der Schließvorgang wird unterstützt von der Druckkraft einer Schließfeder 24. Fällt dagegen der hydraulische Druck im Steuerraum 9 ab, öffnet die Düsennadel 2, indem sie von ihrem Dichtsitz abhebt. Dabei verkleinert sich das Volumen im Steuerraum 9. Um den Druckanstieg bzw. Druckabfall im Steuerraum 9 zu bewirken, ist dieser einerseits über eine in der Drosselplatte 7 ausgebildete und eine Zulaufdrossel 20 aufweisende Zulaufbohrung 21 mit der Zulaufleitung 19 und andererseits über eine in der Drosselplatte 7 ausgebildete und eine Ablaufdrossel 25 aufweisende Ablaufbohrung mit einem Ventilraum 3 des Steuerventils verbunden. Der Ventilraum 3 ist wiederum mit einem Niederdruckraum 18 verbindbar, über welchen die Absteuermenge einem Rücklauf zugeführt werden kann. Die Verbindung des Ventilraums 3 mit dem Niederdruckraum 18 wird über eine entsprechende Schaltstellung des Steuerventils 1 hergestellt. Eine hydraulische Verbindung ist gegeben, wenn ein mit einem Ventilsitz 5 zusammenwirkender Ventilkegel 6 eines Ventilgliedes 4 eine vom Ventilsitz 5 abgehobene Stellung einnimmt. Liegt der Ventilkegel 6 des Ventilgliedes 4 dagegen dichtend am Ventilsitz 5 des Steuerventils 1 an, ist eine hydraulische Verbindung des Ventilraums 3 mit dem Niederdruckraum 18 unterbunden. In dieser ersten Schließstellung des Steuerventils 1 kann über die die Zulaufdrossel 20 enthaltene Zulaufbohrung 21 ein Druckanstieg im Steuerraum 9 bewirkt werden, welche schließlich zum Schließen der Düsennadel 2 führt. Um das Schließen der Düsennadel 2 bzw. den Druckanstieg im Steuerraum 9 zu beschleunigen, ist in der Drosselplatte 7 des Weiteren eine Bohrung 10 vorgesehen, die den Ventilraum 3 mit dem Hochdruckkanal 11 verbindet und somit als Bypass dient. Über die Bohrung 10 in den Ventilraum gelangender Kraftstoff wird über die die Ablaufdrossel 25 aufweisende Ablaufbohrung 8 dem Steuerraum 9 zugeführt. In einer zweiten Schließstellung des Steuerventils 1 liegt das Ventilglied 4 mit einer weiteren Dichtfläche 14 an einem als Flachsitz ausgebildeten Ventilsitz der Drosselplatte 7 an und verschließt dabei die als Bypass dienende Bohrung 10. Zugleich kann Kraftstoff aus dem Ventilraum 3 über den Ventilsitz 5 in den Niederdruckraum 18 abströmen. Dadurch, dass die BypassBohrung 10 jedoch verschlossen ist, bleibt die über den Niederdruckraum 18 einem Rücklauf zugeführte Kraftstoffmenge gering. In die zweite Schließstellung wird das Steuerventil 1 durch Betätigung eines Aktors, beispielsweise eines Piezoaktors (nicht dargestellt) überführt. Eine Druckfeder 17 gewährleistet, dass das Ventilglied 4 des Steuerventils 1 in seine Ausgangsstellung, d. h. seine erste Schließstellung zurückkehrt.The Indian FIG. 1 shown known Kraftstoffinjektor has a control valve 1 for actuating a nozzle needle 2, which is axially displaceable in a nozzle body 23 is included. For this purpose, the nozzle body 23 has a bore formed as a high-pressure channel 11, which connects a feed line 19 with at least one injection opening 23 (not shown) formed in the nozzle body 23. The high-pressure fuel is thus supplied via the supply line 19 and the high-pressure passage 11 of the at least one injection nozzle. The high-pressure channel 11 is delimited by means of a throttle plate 7, which is attached axially to the nozzle body 23. Between the throttle plate 7 and the nozzle needle 2, a control chamber 9 is further separated from the high-pressure passage 11 via a control sleeve 22. About the hydraulic pressure in the control chamber 9, the movement of the nozzle needle 2 is controllable. If the hydraulic pressure in the control chamber 9 increases, a closing force is exerted on the nozzle needle 2, so that the nozzle needle is transferred into its closed position. The closing process is supported by the pressure force of a closing spring 24. In contrast, falls off the hydraulic pressure in the control chamber 9, the nozzle needle 2 opens by lifting from their sealing seat. In order to cause the pressure increase or pressure drop in the control chamber 9, this is on the one hand via a formed in the throttle plate 7 and an inlet throttle 20 having inlet bore 21 with the supply line 19 and on the other hand via a in the throttle plate. 7 trained and a drain throttle 25 having drain hole connected to a valve chamber 3 of the control valve. The valve chamber 3 is in turn connectable to a low pressure chamber 18, via which the Absteuermenge can be fed to a return. The connection of the valve chamber 3 with the low pressure chamber 18 is made via a corresponding switching position of the control valve 1. A hydraulic connection is provided when a cooperating with a valve seat 5 valve cone 6 of a valve member 4 occupies a position lifted from the valve seat 5 position. On the other hand, when the poppet 6 of the valve member 4 seals against the valve seat 5 of the control valve 1, a hydraulic connection of the valve chamber 3 to the low-pressure chamber 18 is prevented. In this first closed position of the control valve 1, a pressure increase in the control chamber 9 can be effected via the inlet bore 21 contained in the inlet throttle 20, which finally leads to the closing of the nozzle needle 2. In order to accelerate the closing of the nozzle needle 2 or the increase in pressure in the control chamber 9, a bore 10 is provided in the throttle plate 7 further, which connects the valve chamber 3 with the high pressure passage 11 and thus serves as a bypass. About the bore 10 into the valve space reaching fuel is on the flow restrictor 25 having drain hole 8 the Control chamber 9 supplied. In a second closed position of the control valve 1, the valve member 4 is located with a further sealing surface 14 on a trained flat seat valve seat of the throttle plate 7, thereby closing the serving as a bypass bore 10. At the same time fuel from the valve chamber 3 via the valve seat 5 in the low-pressure chamber 18 outflow. However, because the bypass bore 10 is closed, the amount of fuel supplied via the low-pressure chamber 18 to a return line remains low. In the second closed position, the control valve 1 by operation of an actuator, such as a piezoelectric actuator (not shown) transferred. A compression spring 17 ensures that the valve member 4 of the control valve 1 returns to its initial position, ie its first closed position.

Der Figur 2 ist in einer vergrößerten Darstellung das Ventilglied 4 des Kraftstoffinjektors gemäß der Fig. 1 zu entnehmen, das einen mit dem Ventilsitz 5 zusammenwirkenden Ventilkegel 6 umfasst. Des Weiteren ist an der dem Ventilkegel 6 gegenüberliegenden Stirnfläche des Ventilgliedes 4 eine weitere Dichtfläche 14 ausgebildet, die in Anlage mit der Drosselplatte 7 zum Verschließen der als Bypass dienenden Bohrung 10 bringbar ist.Of the FIG. 2 is an enlarged view of the valve member 4 of the fuel injector according to the Fig. 1 to be taken, which comprises a valve cone 6 cooperating with the valve seat 5. Furthermore, a further sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4, which is engageable with the throttle plate 7 for closing the bore 10 serving as a bypass.

Der Figur 3 ist in einer vergleichbaren Darstellung das Ventilglied 4 eines erfindungsgemäßen Kraftstoffinjektors zu entnehmen. Auch dieses Ventilglied 4 besitzt einen mit dem Ventilsitz 5 zusammenwirkenden Ventilkegel 6 sowie eine weitere Dichtfläche 14 an der dem Ventilkegel 6 gegenüberliegenden Stirnfläche. Darüber hinaus weist jedoch das Ventilglied 4 eine axial verlaufende Bohrung 12 auf, die das Ventilglied 4 vollständig durchsetzt. Das Ventilglied 4 ist somit als Hohlkörper ausgeführt. In der axial verlaufenden Bohrung 12 ist ein Bolzen 13 aufgenommen, der gemäß der Ausführungsform der Figur 3 die gleiche Länge wie das Ventilglied 4 besitzt. Alternativ kann der Bolzen 13 auch eine geringere Länge als das Ventilglied 4 aufweisen. Eine entsprechende Ausführungsform ist in der Figur 4 dargestellt. Bei dem in der Figur 4 dargestellten Ausführungsbeispiel ist der Bolzen 13 zudem einstückig mit der Drosselplatte 7 verbunden und somit lagefixiert. Über den Bolzen 13 wird demzufolge eine axiale Führung des hubbeweglichen Ventilgliedes 4 bewirkt.Of the FIG. 3 can be seen in a comparable illustration, the valve member 4 of a fuel injector according to the invention. Also, this valve member 4 has a cooperating with the valve seat 5 valve cone 6 and a further sealing surface 14 on the valve cone 6 opposite end face. In addition, however, the valve member 4 has an axially extending bore 12 which completely penetrates the valve member 4. The valve member 4 is thus designed as a hollow body. In the axially extending bore 12, a bolt 13 is received, which according to the embodiment of the FIG. 3 has the same length as the valve member 4. Alternatively, the bolt 13 may also have a smaller length than the valve member 4. A corresponding embodiment is in the FIG. 4 shown. In the in the FIG. 4 illustrated embodiment, the bolt 13 is also integrally connected to the throttle plate 7 and thus fixed in position. Consequently, an axial guidance of the lifting valve member 4 is effected via the bolt 13.

Durch die den Bolzen 13 aufnehmende axial verlaufende Bohrung 12 wird - unabhängig davon, ob der Bolzen 13 als separates Bauteil oder einstückig mit der Drosselplatte 7 ausgebildet ist - eine Verringerung der Querschnittsfläche des Ventilgliedes 4 bewirkt, so dass das Steuerventil 1 in geschlossenem Zustand, d.h. in Anlage am Ventilsitz 5, entlastet wird. Denn der Raildruck wirkt nicht mehr auf die gesamte Steuerventilsitzfläche, sondern nur noch auf die um den Querschnitt der Bohrung 12 bzw. des Bolzens 13 reduzierte Sitzfläche. Ist der Bolzen 13 ferner einstückig mit der Drosselplatte 7 verbunden bzw. ausgebildet, verringert sich darüber hinaus die zum Öffnen des Steuerventils 1 erforderliche Aktorkraft. Denn lediglich das Ventilglied 4 muss weiters gegen den im Ventilraum 3 anstehenden Raildruck aus seinem Sitz gehoben werden.By the bolt 13 receiving axially extending bore 12 is - regardless of whether the bolt 13 as a separate component or integrally with the Throttle plate 7 is formed - causes a reduction in the cross-sectional area of the valve member 4, so that the control valve 1 in the closed state, ie in contact with the valve seat 5, is relieved. Because the rail pressure no longer acts on the entire control valve seat surface, but only on the reduced around the cross section of the bore 12 and the pin 13 seat surface. Further, when the bolt 13 is integrally connected to the throttle plate 7, the actuator force required for opening the control valve 1 is reduced. Because only the valve member 4 must be further raised against the pending in the valve chamber 3 rail pressure from its seat.

Wie ferner der Figur 4 zu entnehmen ist, sind in der als Bypass dienenden Bohrung 10 Drosselstellen 15, 16 ausgebildet, die die Bohrung 10 mit dem Ventilraum 3 verbinden. Beide Drosseltellen 15, 16 sind als Bohrungen mit verringertem Durchströmungsquerschnitt gegenüber der Bohrung 10 ausgebildet, wobei die Bohrungen derart geführt sind, dass sie radial versetzt zum Bolzen 13 in den Ventilraum 3 münden. Das Freigeben und das Verschließen der Drosselstellen 15, 16 bzw. der Bypass-Bohrung 10 wird vorliegend allein durch das hülsenartig ausgeführte Ventilglied 4 bewirkt. Hierzu ist an der dem Ventilkegel 6 gegenüberliegenden Stirnfläche des Ventilgliedes 4 eine ringförmige Dichtfläche 14 ausgebildet.How further the FIG. 4 can be seen, 10 throttle bodies 15, 16 are formed in the bore serving as a bore, which connect the bore 10 with the valve chamber 3. Both throttle plates 15, 16 are formed as holes with a reduced flow cross-section relative to the bore 10, wherein the bores are guided such that they open radially offset from the bolt 13 in the valve chamber 3. The release and closing of the throttle points 15, 16 and the bypass bore 10 is effected in the present case solely by the sleeve-like executed valve member 4. For this purpose, an annular sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4.

Die durch den erfindungsgemäßen Kraftstoffinjektor bewirkte Entlastung des Steuerventils im Bereich seines Ventilsitzes ist in dem Diagramm der Figur 5 grafisch dargestellt. Auf der X-Achse sind verschiedene Durchmesser des Bolzens 13 in Millimetern aufgetragen, die vorliegend von 0 bis 1,2mm reichen. Auf der Y-Achse ist die Restlast in Prozent aufgetragen. Bei einem Bolzendruchmesser von 0 mm ist kein Bolzen 13 vorhanden, d.h. die Restlast beträgt 100 %. Mit zunehmendem Durchmesser des Bolzens 13 fällt die Restlast jedoch stark ab. Dem Diagramm sind mehrere Graphen zu entnehmen, die jeweils für einen bestimmten Sitzdurchmesser stehen. Der Sitzdurchmesser variiert vorliegend zwischen 1,33 mm (unterster Graph) und 1,43 mm (oberster Graph). Entscheidend für das Maß der Entlastung ist demnach das Flächenverhältnis zwischen Sitzdurchmesser und Bolzendurchmesser.The relief caused by the fuel injector according to the invention of the control valve in the region of its valve seat is in the diagram of FIG. 5 shown graphically. On the X-axis different diameters of the bolt 13 are plotted in millimeters, which in the present range from 0 to 1.2 mm. The remaining load is plotted on the y-axis in percent. With a bolt diameter of 0 mm, no bolt 13 is present, ie the residual load is 100%. However, as the diameter of the bolt 13 increases, the residual load drops sharply. The graph shows several graphs, each representing a specific seat diameter. The seat diameter varies here between 1.33 mm (bottom graph) and 1.43 mm (top graph). Decisive for the degree of relief is therefore the area ratio between seat diameter and bolt diameter.

Claims (9)

  1. Fuel injector for a fuel injection system, in particular a common rail injection system, having a control valve (1) for the actuation of a nozzle needle (2) which can perform a stroke movement and by means of the stroke movement of which at least one injection opening can be opened up or closed off, wherein the control valve (1) comprises a valve chamber (3) for accommodating a valve element (4) which can perform a stroke movement and which has a valve cone (6) that interacts with a valve seat (5), and wherein the valve chamber (3) is delimited by a throttle plate (7) in which there are formed at least a first bore (8) for connecting the valve chamber (3) to a control chamber (9) and a second bore (10) for connecting the valve chamber (3) to a high-pressure duct (11),
    characterized in that an axially running bore (12) in which a pin (13) is accommodated with play extends through the valve element (4), wherein the pin (13) is integrally connected to the throttle plate (7) and is thus fixed in position.
  2. Fuel injector according to Claim 1,
    characterized in that the pin (13) has the same length in the axial direction as the valve element (4).
  3. Fuel injector according to Claim 1,
    characterized in that the pin (13) has a shorter length in the axial direction than the valve element (4).
  4. Fuel injector according to one of the preceding claims,
    characterized in that the control valve (1) is of double-acting configuration, and a further sealing surface (14) is formed on an end, which faces away from the valve seat (5), of the valve element (4) of the control valve (1), by means of which further sealing surface the second bore (10) can be opened up or closed off.
  5. Fuel injector according to Claim 4,
    characterized in that the further sealing surface (14) is of flat and/or annular form and/or interacts with a flat seat formed on the throttle plate (7).
  6. Fuel injector according to one of the preceding claims,
    characterized in that, in the second bore (10) of the throttle plate (7), there is formed at least one throttle point (15, 16) which is preferably formed as a coaxial or branching bore with a smaller throughflow cross section than the second bore (10).
  7. Fuel injector according to Claim 6,
    characterized in that the throttle point (15, 16) formed in the second bore (10) is arranged at the valve chamber side.
  8. Fuel injector according to one of the preceding claims,
    characterized in that a compression spring (17) for preloading the valve element (4) against the valve seat (5) is accommodated in the valve chamber (3), wherein the compression spring (17) is supported at one side on the valve cone (6) of the valve element (4) and at the other side on the throttle plate (7).
  9. Fuel injector according to one of the preceding claims,
    characterized in that a piezo actuator is provided for actuating the control valve (1).
EP20110150091 2010-01-28 2011-01-04 Fuel injector Not-in-force EP2354526B1 (en)

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EP2354526A3 EP2354526A3 (en) 2013-07-24
EP2354526B1 true EP2354526B1 (en) 2014-07-23

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Publication number Priority date Publication date Assignee Title
DE102013222650A1 (en) * 2013-06-10 2014-12-11 Robert Bosch Gmbh Fuel injector
DE102014220841A1 (en) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injection valve for injecting fluid into a combustion chamber of an internal combustion engine
DE102016216885A1 (en) * 2016-09-06 2018-03-08 Continental Automotive Gmbh Fluid injector for a motor vehicle
CN106593725A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Resonance type electronic fuel injector

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GB9526522D0 (en) * 1995-12-23 1996-02-28 Lucas Ind Plc Valve arrangement
GB0215490D0 (en) * 2002-07-04 2002-08-14 Delphi Tech Inc Control valve arrangement
DE102004061800A1 (en) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injector of a fuel injection system of an internal combustion engine
DE102008040637A1 (en) * 2008-07-23 2010-01-28 Robert Bosch Gmbh Fuel injection valve device

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DE102010001315A1 (en) 2011-08-18
EP2354526A2 (en) 2011-08-10
EP2354526A3 (en) 2013-07-24

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