EP3056725B1 - Control valve assembly - Google Patents

Control valve assembly Download PDF

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Publication number
EP3056725B1
EP3056725B1 EP15202937.7A EP15202937A EP3056725B1 EP 3056725 B1 EP3056725 B1 EP 3056725B1 EP 15202937 A EP15202937 A EP 15202937A EP 3056725 B1 EP3056725 B1 EP 3056725B1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve arrangement
arrangement according
injector
fluid
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
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EP15202937.7A
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German (de)
French (fr)
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EP3056725A1 (en
Inventor
Lars Olems
Huesamettin Yueksel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP3056725A1 publication Critical patent/EP3056725A1/en
Application granted granted Critical
Publication of EP3056725B1 publication Critical patent/EP3056725B1/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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M63/0043—Two-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
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear

Definitions

  • the invention relates to a control valve assembly of an injector, comprising a sleeve-shaped armature closing body, which is arranged axially displaceably on an anchor bolt, whose first end face is supported on a stationary support plate, and the second front end is acted upon during operation of the injector in phases with high pressure.
  • Such a control valve arrangement is known from DE 10 2010 001486 A1 known.
  • This control valve assembly has a sleeve-shaped armature closing body, which is arranged axially displaceable on an anchor bolt, whose first end face is supported on a stationary support plate. The opposite second front end is acted upon in phases of high pressure during operation of the injector.
  • This high pressure is utilized in a test phase in order to achieve a plastic deformation on the opposite stationary part, by means of which, in particular, a hinged-shell-type bearing bed for the first front end of the anchor bolt on the retaining plate is created. In this case, a deliberate deformation of the interacting components is accepted.
  • control valves for fuel injection injectors are known in which the anchor bolt is supported with a spherical end face on the housing or on a plate which is arranged between the anchor bolt and the housing.
  • the invention has for its object to provide a control valve assembly, which is improved in terms of their durability.
  • This object is achieved in that a fluid space is formed on the control valve arrangement in the region between the first end face of the anchor bolt and the retaining plate.
  • This filled with a basically arbitrary fluid fluid space dampens the impact movement of the anchor bolt on the stationary support plate. Thereby, a possible wear on the corresponding contact surface is reduced and thus improves or increases the durability of the control valve assembly and the entire injector.
  • the anchor bolt has a first end with the second end and connecting liquid-conducting passageway. This passageway is fed from the second face end with high pressure fluid.
  • a hydrostatic bearing is formed at the contact point between the anchor bolt and the retaining plate on the opposite side in the fluid space formed by the through-passage in this area. The hydrostatic power transmission thus formed is quasi wear-free.
  • the anchor bolt on the first end face on a fluid-carrying lubricating pocket is cooperatively formed with the passage channel creating the fluid space and in a further further embodiment cup-shaped.
  • the lubricating pocket in turn surrounds the passageway in a further embodiment.
  • This hydrostatic bearing uses the pressure of the fluid provided by the high pressure source.
  • pressurized fluid enters the lubrication pocket between the retaining plate and the anchor bolt.
  • the pressurized fluid is sealed against a low pressure space surrounding the anchor bolt.
  • a leakage gap through which a leakage amount of fluid can flow into the low-pressure chamber.
  • D of the lubricating pocket the mechanical contact pressure in the contact surface can be adjusted.
  • a large diameter means a low mechanical contact pressure and thus a larger leakage of the fluid.
  • the mechanical contact pressure can be increased and thus the leakage can be reduced.
  • a larger angle error between the holding plate and the anchor bolt is permitted.
  • an optimum can be determined between a leakage quantity of fluid and a possible wear.
  • eliminates the leakage at omission of the passage channel since then the fluid space or the lubricating pocket is filled only with the up and down movements of the anchor bolt from the low pressure chamber or via another connection supplied fluid.
  • the passage has a throttle point.
  • the throttle restriction limits the flow through the passage.
  • the throttle point is preferably arranged near the lubricating pocket. It should be noted that there may be a breathing of the anchor bolt against the holding plate with rapid changes in pressure. This breathing causes small changes in the length of the anchor bolt, which lead to the formation of the leakage gap, the throttle point limited in this case, the leakage and favors the reassignment of the anchor bolt to the holding plate.
  • a further advantage is that the pressure in the lubrication pocket can be influenced by the combination of the throttling effect of the throttle point and the leakage gap between the anchor bolt and the retaining plate.
  • the second front end of the anchor bolt adjoins a space in the valve body, which is connected via an output bore with a control chamber.
  • the first end face of the anchor bolt has a hemispherical basic shape.
  • This hemispherical basic shape is also realized in conventional anchor bolts, so that only the fluid space or the lubrication pocket must be incorporated to implement the inventive design in this hemispherical basic shape.
  • a flat retaining plate an enlargement of the mechanical contact surface between the anchor bolt and the retaining plate is thereby automatically created in addition to the creation of the fluid space.
  • the anchor bolt but also have a flat basic shape.
  • a flat basic shape again increases the contact area between the interacting components. In such an embodiment, an exact alignment of the anchor bolt should be ensured to the support plate to minimize possible angle error between the support plate and the anchor bolt.
  • a fluid-carrying Low pressure space formed between the holding plate and an electromagnet arrangement of the switching valve arrangement a fluid-carrying Low pressure space formed.
  • This fluid-conducting low-pressure chamber communicates with the fluid space or the lubricating pocket via the previously mentioned leakage gap and thus ensures reliable filling of the lubricating space with fluid or unimpeded discharge of the leak escaped through the passageway and further through the leakage gap.
  • the low-pressure chamber is connected to a low-pressure system of the control valve arrangement of the injector.
  • the injector is a fuel injector. While the subject invention may be applied to any injector, the preferred application is with a fuel injector as part of a fuel injection system.
  • This fuel injection system is preferably a common-rail injection system in which fuel stored in a high-pressure accumulator is injected in a controlled manner from the fuel injector into an associated combustion chamber of an internal combustion engine.
  • FIG. 1 partially formed as a fuel injector injector has a multi-part injector 1 with a valve body 2, which form a control valve assembly.
  • a control chamber 3 connects, in which a plunger 4, which with an injector needle cooperates or the Injektornadel is, protruding.
  • the injector needle controls the fuel to be injected by the fuel injector into the associated combustion chamber of an internal combustion engine.
  • the injector needle closes injection ports of the fuel injector while the injection ports are opened when the plunger 4 is displaced upward into the control chamber 3.
  • the control chamber 3 communicates constantly via a throttle line 5 shown only schematically, which can enforce deviating from the graphic representation of the valve body 2, with a high pressure source, usually a high pressure accumulator 6 of the common rail injection system.
  • a high pressure source usually a high pressure accumulator 6 of the common rail injection system.
  • fuel is stored under a pressure of up to 3,000 bar.
  • the common rail injection system furthermore has a low-pressure system designed as a low-pressure fuel system with a tank 11, from which a high-pressure pump 12 delivers fuel into the high-pressure accumulator 6.
  • the fuel low-pressure system may also have a low-pressure pump, at least one filter, an overflow valve, a metering unit and pressure sensors and temperature sensors.
  • a throttled outlet bore 7 for the control chamber 3 is arranged within the valve body 2.
  • This output bore 7 is controlled by a sleeve-shaped armature closing body 8, which cooperates with a concentric to the output hole 7, annular seat 9 on the upper end face of the valve body 2.
  • the outlet bore 7 is connected to a low-pressure space 10 provided in the injector body 1, which is connected to the fuel low-pressure system, for example the tank 11, via line connections (not shown) preferably in the injector body 1.
  • an anchor bolt 13 is arranged, on which the armature closing body 8 is arranged displaceably.
  • the annular gap between the outer circumference of the anchor bolt 13 and the inner circumference of the armature closing body 8 is formed as a sealing gap.
  • an armature 14 is arranged, which cooperates with an annular electromagnet arrangement 15.
  • the armature 14 is tensioned with the armature closing body 8 against the seat 9.
  • the armature 14 and the armature closing body 8 are lifted against the force of the compression spring 16 from the illustrated closed position of the armature closing body 8 and placed in an upper end position in which the armature 14 is seated on annular pole pieces 17 of the solenoid assembly 15.
  • the pressure spring 16 again displaces the armature closing body 8 into the illustrated closed position.
  • the supplied via the output bore 7 of the control chamber 3 in a space 25 below the anchor bolt 13 fuel acts on a lower second end face 18 of the anchor bolt 13, so that the anchor bolt 13 with an upper, first end face 19 against a retaining plate 20 of the injector body. 1 is pushed. Due to the pressure fluctuations occurring during operation of the control valve arrangement, the anchor bolt 13 is moved in phase with the first end face 19 against the holding plate 20 and thus it can in the contact area between the first end face 19 and the holding plate 20, a mechanical wear occur that impair the durability of the control valve assembly can.
  • a through-channel 21 for example, in the form of a bore, which opens into a fluid space 22 in the first end face 19 of the anchor bolt 13.
  • the fluid space 22 is formed by a pocket-shaped lubricating pocket 23 which surrounds the passage 21 in the area of the first end face 19.
  • the fluid space 22 can also be formed only from the upper region of the through-channel 21-that is to say without the lubricating pocket 23.
  • Yet another embodiment provides only the lubricating pocket 23, which is then suitably charged with fluid. In this embodiment, no through-passage 21 is present.
  • FIG. 2 shows a detailed view X of the contact region of the first end face 19 of the anchor bolt 13 and with the holding plate 20.
  • fuel passes into the fluid chamber 22 formed by the lubricating pocket 23 and causes a hydrostatic bearing of the anchor bolt 13 relative to the holding plate 20.
  • a leakage gap 24 is formed in phases between the first front end 19 of the anchor bolt 13 and the holding plate 20, through which a leakage amount of fuel in the also in this region of the fuel injector existing low-pressure space 10 flows.
  • the basic shape of the first front end 19 of the anchor bolt 13 may be hemispherical or planar. In the illustrated embodiment according to FIG. 2 has been planned starting from a hemispherical basic shape, the front end and additionally the lubricating pocket 23 has been incorporated into the planned area.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft eine Steuerventilanordnung eines Injektors, aufweisend einen hülsenförmigen Ankerschließkörper, der axial verschiebbar auf einem Ankerbolzen angeordnet ist, dessen erstes Stirnende auf einer stationären Halteplatte abgestützt ist, und dessen zweites Stirnende beim Betrieb des Injektors phasenweise mit Hochdruck beaufschlagt ist.The invention relates to a control valve assembly of an injector, comprising a sleeve-shaped armature closing body, which is arranged axially displaceably on an anchor bolt, whose first end face is supported on a stationary support plate, and the second front end is acted upon during operation of the injector in phases with high pressure.

Stand der TechnikState of the art

Eine derartige Steuerventilanordnung ist aus der DE 10 2010 001486 A1 bekannt. Diese Steuerventilanordnung weist einen hülsenförmigen Ankerschließkörper auf, welcher axial verschiebbar auf einem Ankerbolzen angeordnet ist, dessen erstes Stirnende auf einer stationären Halteplatte abgestützt ist. Das gegenüberliegende zweite Stirnende ist beim Betrieb des Injektors phasenweise mit Hochdruck beaufschlagt. Dieser Hochdruck wird in einer Prüfphase dazu ausgenutzt, um am gegenüberliegenden stationären Teil eine plastische Verformung zu erzielen, durch die insbesondere ein gelenkschalenartiges Lagerbett für das erste Stirnende des Ankerbolzens an der Halteplatte geschaffen wird. Dabei wird eine bewusste Verformung der zusammenwirkenden Bauteile in Kauf genommen.Such a control valve arrangement is known from DE 10 2010 001486 A1 known. This control valve assembly has a sleeve-shaped armature closing body, which is arranged axially displaceable on an anchor bolt, whose first end face is supported on a stationary support plate. The opposite second front end is acted upon in phases of high pressure during operation of the injector. This high pressure is utilized in a test phase in order to achieve a plastic deformation on the opposite stationary part, by means of which, in particular, a hinged-shell-type bearing bed for the first front end of the anchor bolt on the retaining plate is created. In this case, a deliberate deformation of the interacting components is accepted.

Aus DE 10 2006 021 741 A1 und DE 10 2007 047 151 A1 sind darüber hinaus Steuerventile für Kraftstoffeinspritzinjektoren bekannt, bei denen sich der Ankerbolzen mit einer balligen Stirnfläche am Gehäuse abstützt bzw. an einer Platte, die zwischen dem Ankerbolzen und dem Gehäuse angeordnet ist.Out DE 10 2006 021 741 A1 and DE 10 2007 047 151 A1 In addition, control valves for fuel injection injectors are known in which the anchor bolt is supported with a spherical end face on the housing or on a plate which is arranged between the anchor bolt and the housing.

Der Erfindung liegt die Aufgabe zugrunde, eine Steuerventilanordnung anzugeben, die bezüglich ihrer Dauerhaltbarkeit verbessert ist.The invention has for its object to provide a control valve assembly, which is improved in terms of their durability.

Offenbarung der ErfindungDisclosure of the invention

Diese Aufgabe wird dadurch gelöst, dass an der Steuerventilanordnung im Bereich zwischen dem ersten Stirnende des Ankerbolzens und der Halteplatte ein Fluidraum ausgebildet ist. Dieser mit einem grundsätzlich beliebigen Fluid gefüllte Fluidraum dämpft die Aufschlagbewegung des Ankerbolzens auf der stationären Halteplatte. Dadurch wird ein möglicher Verschleiß an der entsprechenden Kontaktfläche verringert und damit die Dauerhaltbarkeit der Steuerventilanordnung und des gesamten Injektors verbessert beziehungsweise erhöht.This object is achieved in that a fluid space is formed on the control valve arrangement in the region between the first end face of the anchor bolt and the retaining plate. This filled with a basically arbitrary fluid fluid space dampens the impact movement of the anchor bolt on the stationary support plate. Thereby, a possible wear on the corresponding contact surface is reduced and thus improves or increases the durability of the control valve assembly and the entire injector.

Hierbei ist zu berücksichtigen, dass bei bekannten Steuerventilanordnungen ein sogenanntes druckausgeglichenes Schaltventil verwendet wird. Hierbei ist das zentrale Element der Ankerbolzen. Er ermöglicht, dass nahezu keine hydrostatischen Kräfte aus einer Hochdruckquelle, die die Steuerventilanordnung mit Fluid beaufschlagt, auf den Ankerschließkörper wirken. Die Ankerschließkörperdynamik und Dichtheit sind damit unabhängig vom Druck des Fluids in der Hochdruckquelle. Wenn das von der Steuerventilanordnung gebildete Schaltventil geschlossen ist, wirken auf den Ankerbolzen allerdings hohe hydrostatische Kräfte, die von der Halteplatte aufgenommen werden müssen. An der Kontaktstelle zwischen dem Ankerbolzen und der Halteplatte entsteht eine hohe Kontaktkraft. Durch wechselnde Kräfte und Mikrobewegungen kann es an dieser Kontaktstelle zu einem Verschleiß kommen, der durch die erfindungsgemäße Anordnung des Fluidraums an dieser Kontaktstelle zumindest deutlich vermindert wird. Hierbei ist folglich in der allgemeinsten Ausgestaltung durch den fluidgefüllten Fluidraum ein Fluidpolster geschaffen.It should be noted that in known control valve arrangements, a so-called pressure-balanced switching valve is used. Here is the central element of the anchor bolts. It allows almost no hydrostatic forces from a high pressure source, which applies fluid to the control valve assembly, to act on the armature closing body. The armature closing body dynamics and tightness are thus independent of the pressure of the fluid in the high pressure source. When the switching valve formed by the control valve assembly is closed, however, act on the anchor bolt high hydrostatic forces that must be absorbed by the support plate. At the contact point between the anchor bolt and the retaining plate creates a high contact force. By changing forces and micro-movements, wear can occur at this contact point, which is at least significantly reduced by the arrangement of the fluid space according to the invention at this contact point. In this case, therefore, in the most general embodiment, a fluid cushion is created by the fluid-filled fluid space.

In Weiterbildung der Erfindung weist der Ankerbolzen einen das erste Stirnende mit dem zweiten Stirnende verbindenden und flüssigkeitsführenden Durchgangskanal auf. Dieser Durchgangskanal wird von dem zweiten Stirnende aus, mit unter Hochdruck stehendem Fluid beschickt. Dadurch wird auf der gegenüberliegenden Seite in dem von dem Durchgangskanal in diesem Bereich gebildeten Fluidraum eine hydrostatische Lagerung an der Kontaktstelle zwischen dem Ankerbolzen und der Halteplatte gebildet. Die so gebildete hydrostatische Kraftübertragung ist quasi verschleißfrei.In a development of the invention, the anchor bolt has a first end with the second end and connecting liquid-conducting passageway. This passageway is fed from the second face end with high pressure fluid. As a result, a hydrostatic bearing is formed at the contact point between the anchor bolt and the retaining plate on the opposite side in the fluid space formed by the through-passage in this area. The hydrostatic power transmission thus formed is quasi wear-free.

In weiterer Ausgestaltung der Erfindung weist der Ankerbolzen an dem ersten Stirnende eine fluidführende Schmiertasche auf. Diese Schmiertasche ist zusammenwirkend mit dem Durchgangskanal den Fluidraum schaffend gebildet und in wiederum weiterer Ausgestaltung topfförmig ausgebildet. Dabei umgibt die Schmiertasche wiederum in weiterer Ausgestaltung den Durchgangskanal. Dies ist eine bevorzugte Ausgestaltung, die eine besonders effektive hydrostatische Lagerung gewährleistet. Bei dieser hydrostatischen Lagerung wird der Druck des von der Hochdruckquelle bereitgestellten Fluids genutzt. Durch den Durchgangskanal in dem Ankerbolzen gelangt unter Druck stehendes Fluid in die Schmiertasche zwischen der Halteplatte und dem Ankerbolzen. Durch eine Kontaktfläche zwischen dem ersten Stirnende des Ankerbolzens und der Halteplatte wird das unter Druck stehende Fluid gegenüber einem den Ankerbolzen umgebenden Niederdruckraum abgedichtet.In a further embodiment of the invention, the anchor bolt on the first end face on a fluid-carrying lubricating pocket. This lubrication pocket is cooperatively formed with the passage channel creating the fluid space and in a further further embodiment cup-shaped. In this case, the lubricating pocket in turn surrounds the passageway in a further embodiment. This is a preferred embodiment, which ensures a particularly effective hydrostatic bearing. This hydrostatic bearing uses the pressure of the fluid provided by the high pressure source. Through the passageway in the anchor bolt pressurized fluid enters the lubrication pocket between the retaining plate and the anchor bolt. Through a contact surface between the first end face of the anchor bolt and the retaining plate, the pressurized fluid is sealed against a low pressure space surrounding the anchor bolt.

Hierbei ist zu berücksichtigen, dass durch die von den Druckschwankungen in dem System bewirkten geringen Auf- und Abbewegungen des Ankerbolzens phasenweise zwischen dem ersten Stirnende des Ankerbolzens und der Halteplatte ein Leckagespalt gebildet wird, durch den eine Leckagemenge von Fluid in den Niederdruckraum abströmen kann. Beispielsweise durch die Variation des Durchmessers D der Schmiertasche kann die mechanische Anpresskraft in der Kontaktfläche eingestellt werden. Ein großer Durchmesser bedeutet eine geringe mechanische Anpresskraft und damit eine größere Leckage des Fluids. Durch eine Reduzierung des Durchmessers kann die mechanische Anpresskraft erhöht werden und damit die Leckage verringert werden. Weiterhin ist bei einem kleinen Durchmesser ein größerer Winkelfehler zwischen der Halteplatte und dem Ankerbolzen zulässig. Entsprechend den jeweiligen Anforderungen und Gegebenheiten kann ein Optimum zwischen einer Leckagemenge von Fluid und einem möglichen Verschleiß ermittelt werden. Wie zuvor bei der allgemeinsten Darstellung der Erfindung beschrieben ist, entfällt die Leckage bei Entfall des Durchgangskanals, da dann der Fluidraum beziehungsweise die Schmiertasche nur mit bei den Auf- und Abbewegungen des Ankerbolzens aus dem Niederdruckraum oder über eine sonstige Verbindung zugeführten Fluid gefüllt ist.It should be noted that caused by the pressure variations in the system caused small up and down movements of the anchor bolt in phases between the first end face of the anchor bolt and the retaining plate, a leakage gap through which a leakage amount of fluid can flow into the low-pressure chamber. For example, by varying the diameter D of the lubricating pocket, the mechanical contact pressure in the contact surface can be adjusted. A large diameter means a low mechanical contact pressure and thus a larger leakage of the fluid. By reducing the diameter, the mechanical contact pressure can be increased and thus the leakage can be reduced. Furthermore, with a small diameter, a larger angle error between the holding plate and the anchor bolt is permitted. Depending on the respective requirements and circumstances, an optimum can be determined between a leakage quantity of fluid and a possible wear. As described above in the most general representation of the invention, eliminates the leakage at omission of the passage channel, since then the fluid space or the lubricating pocket is filled only with the up and down movements of the anchor bolt from the low pressure chamber or via another connection supplied fluid.

In Weiterbildung der Erfindung weist der Durchgangskanal eine Drosselstelle auf. Die Drosselstelle begrenzt den Durchfluss durch den Durchgangskanal. Die Drosselstelle ist vorzugsweise nahe der Schmiertasche angeordnet. Hierbei ist zu berücksichtigen, dass es bei schnellen Änderungen des Drucks einem Atmen des Ankerbolzens gegenüber der Halteplatte kommen kann. Dieses Atmen verursacht geringe Längenänderungen des Ankerbolzens, die zur Bildung des Leckagespalts führen, Die Drosselstelle begrenzt in diesem Fall die Leckage und begünstigt das Wiederanlegen des Ankerbolzens an die Halteplatte. Ein weiterer Vorteil ist, dass der Druck in der Schmiertasche durch die Kombination der Drosselwirkung der Drosselstelle und der des Leckagespalts zwischen dem Ankerbolzen und der Halteplatte beeinflusst werden kann.In a further development of the invention, the passage has a throttle point. The throttle restriction limits the flow through the passage. The throttle point is preferably arranged near the lubricating pocket. It should be noted that there may be a breathing of the anchor bolt against the holding plate with rapid changes in pressure. This breathing causes small changes in the length of the anchor bolt, which lead to the formation of the leakage gap, the throttle point limited in this case, the leakage and favors the reassignment of the anchor bolt to the holding plate. A further advantage is that the pressure in the lubrication pocket can be influenced by the combination of the throttling effect of the throttle point and the leakage gap between the anchor bolt and the retaining plate.

In weiterer Ausgestaltung der Erfindung grenzt das zweite Stirnende des Ankerbolzens an einen Raum in dem Ventilkörper an, der über eine Ausgangsbohrung mit einer Steuerkammer verbunden ist. Durch diese Ausgestaltung ist das erste Stirnende des Ankerbolzens phasenweise mit Hochdruck beaufschlagt.In a further embodiment of the invention, the second front end of the anchor bolt adjoins a space in the valve body, which is connected via an output bore with a control chamber. By this configuration, the first front end of the anchor bolt is subjected in phases with high pressure.

In Weiterbildung der Erfindung weist das erste Stirnende des Ankerbolzens eine halbkugelförmige Grundform auf. Diese halbkugelförmige Grundform ist auch bei konventionellen Ankerbolzen verwirklicht, so dass zur Umsetzung der erfindungsgemäßen Ausgestaltung in diese halbkugelförmige Grundform nur der Fluidraum beziehungsweise die Schmiertasche eingearbeitet werden muss. Bei einer planen Halteplatte ist dadurch automatisch eine Vergrößerung der mechanischen Kontaktfläche zwischen dem Ankerbolzen und der Halteplatte zusätzlich zu der Schaffung des Fluidraums geschaffen. Alternativ kann der Ankerbolzen aber auch eine plane Grundform aufweisen. Eine plane Grundform vergrößert nochmals die Kontaktfläche zwischen den zusammenwirkenden Komponenten. Bei einer solchen Ausgestaltung sollte eine exakte Ausrichtung des Ankerbolzens zu der Halteplatte gewährleistet sein, um einen möglichen Winkelfehler zwischen der Halteplatte und dem Ankerbolzen möglichst gering zu halten.In a development of the invention, the first end face of the anchor bolt has a hemispherical basic shape. This hemispherical basic shape is also realized in conventional anchor bolts, so that only the fluid space or the lubrication pocket must be incorporated to implement the inventive design in this hemispherical basic shape. In the case of a flat retaining plate, an enlargement of the mechanical contact surface between the anchor bolt and the retaining plate is thereby automatically created in addition to the creation of the fluid space. Alternatively, the anchor bolt but also have a flat basic shape. A flat basic shape again increases the contact area between the interacting components. In such an embodiment, an exact alignment of the anchor bolt should be ensured to the support plate to minimize possible angle error between the support plate and the anchor bolt.

In Weiterbildung der Erfindung ist zwischen der Halteplatte und einer Elektromagnetanordnung der Schaltventilordnung ein fluidführender Niederdruckraum gebildet. Dieser fluidführende Niederdruckraum steht über dem zuvor erwähnten Leckagespalt mit dem Fluidraum beziehungsweise der Schmiertasche in Verbindung und sorgt somit für eine zuverlässige Befüllung des Schmierraums mit Fluid beziehungsweise eine ungehinderte Abführung der durch den Durchgangskanal und weiter durch den Leckagespalt entwichenen Leckage.In a further development of the invention is between the holding plate and an electromagnet arrangement of the switching valve arrangement a fluid-carrying Low pressure space formed. This fluid-conducting low-pressure chamber communicates with the fluid space or the lubricating pocket via the previously mentioned leakage gap and thus ensures reliable filling of the lubricating space with fluid or unimpeded discharge of the leak escaped through the passageway and further through the leakage gap.

In Weiterbildung der Erfindung ist der Niederdruckraum mit einem Niederdrucksystem der Steuerventilanordnung des Injektors verbunden. Dadurch ist eine zuverlässige Abführung insbesondere der Leckage sichergestellt.In a further development of the invention, the low-pressure chamber is connected to a low-pressure system of the control valve arrangement of the injector. As a result, a reliable discharge, in particular the leakage is ensured.

In Weiterbildung der Erfindung ist der Injektor ein Kraftstoffinjektor. Wenn auch der Gegenstand der Erfindung bei einem beliebigen Injektor angewendet sein kann, ist die bevorzugte Anwendung bei einem Kraftstoffinjektor als Teil eines Kraftstoffeinspritzsystems gegeben. Dieses Kraftstoffeinspritzsystem ist bevorzugt ein Common-Rail-Einspritzsystem, bei dem in einem Hochdruckspeicher gespeicherter Kraftstoff von dem Kraftstoffinjektor in einen zugeordneten Brennraum einer Brennkraftmaschine gesteuert eingespritzt wird.In a further development of the invention, the injector is a fuel injector. While the subject invention may be applied to any injector, the preferred application is with a fuel injector as part of a fuel injection system. This fuel injection system is preferably a common-rail injection system in which fuel stored in a high-pressure accumulator is injected in a controlled manner from the fuel injector into an associated combustion chamber of an internal combustion engine.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der ein in der Figur dargestelltes Ausführungsbeispiel näher beschrieben ist.Further advantageous embodiments of the invention are described in the drawings, in which an embodiment shown in the figure is described in more detail.

Es zeigen:

Figur 1
einen teilweisen Längsschnitt durch eine Steuerventilanordnung eines als Kraftstoffinjektor ausgebildeten Injektors, und
Figur 2
eine Detailansicht eines ersten Stirnendes eines mit einer Halteplatte zusammenwirkenden Ankerbolzens eines Injektors.
Show it:
FIG. 1
a partial longitudinal section through a control valve assembly of a fuel injector designed as an injector, and
FIG. 2
a detailed view of a first end face of a cooperating with a holding plate anchor bolt of an injector.

Der in Figur 1 ausschnittsweise dargestellte als Kraftstoffinjektor ausgebildete Injektor besitzt einen mehrteiligen Injektorkörper 1 mit einem Ventilkörper 2, die eine Steuerventilanordnung bilden. An diesen Ventilkörper 2 schließt sich eine Steuerkammer 3 an, in die ein Plunger 4, der mit einer Injektornadel zusammenwirkt oder aber die Injektornadel ist, hineinragt. Die Injektornadel steuert je nach Stellung den von dem Kraftstoffinjektor in den zugeordneten Brennraum einer Brennkraftmaschine einzuspritzenden Kraftstoff. Wenn der Plunger 4 nach Abwärts verschoben ist, schließt die Injektornadel Einspritzöffnungen des Kraftstoffinjektors, während die Einspritzöffnungen geöffnet sind, wenn der Plunger 4 nach Aufwärts in die Steuerkammer 3 hineinragend verschoben ist. Die Steuerkammer 3 kommuniziert ständig über eine nur schematisch dargestellte Drosselleitung 5, die abweichend von der zeichnerischen Darstellung den Ventilkörper 2 durchsetzen kann, mit einer Hochdruckquelle, in der Regel einem Hochdruckspeicher 6 des Common-Rail-Einspritzsystems. In dem Hochdruckspeicher 6 ist Kraftstoff unter einem Druck von bis zu 3.000 bar gespeichert. Das Common-Rail-Einspritzsystem weist weiterhin ein als Kraftstoffniederdrucksystem ausgebildetes Niederdrucksystem mit einem Tank 11 auf, aus dem eine Hochdruckpumpe 12 Kraftstoff in den Hochdruckspeicher 6 fördert. Neben den dargestellten Komponenten kann insbesondere das Kraftstoffniederdrucksystem noch eine Niederdruckpumpe, zumindest einen Filter, ein Überströmventil, eine Zumesseinheit sowie Drucksensoren und Temperatursensoren aufweisen.The in FIG. 1 partially formed as a fuel injector injector has a multi-part injector 1 with a valve body 2, which form a control valve assembly. At this valve body 2, a control chamber 3 connects, in which a plunger 4, which with an injector needle cooperates or the Injektornadel is, protruding. Depending on its position, the injector needle controls the fuel to be injected by the fuel injector into the associated combustion chamber of an internal combustion engine. When the plunger 4 is displaced downward, the injector needle closes injection ports of the fuel injector while the injection ports are opened when the plunger 4 is displaced upward into the control chamber 3. The control chamber 3 communicates constantly via a throttle line 5 shown only schematically, which can enforce deviating from the graphic representation of the valve body 2, with a high pressure source, usually a high pressure accumulator 6 of the common rail injection system. In the high-pressure accumulator 6 fuel is stored under a pressure of up to 3,000 bar. The common rail injection system furthermore has a low-pressure system designed as a low-pressure fuel system with a tank 11, from which a high-pressure pump 12 delivers fuel into the high-pressure accumulator 6. In addition to the illustrated components, in particular the fuel low-pressure system may also have a low-pressure pump, at least one filter, an overflow valve, a metering unit and pressure sensors and temperature sensors.

Innerhalb des Ventilkörpers 2 ist eine gedrosselte Ausgangsbohrung 7 für die Steuerkammer 3 angeordnet. Diese Ausgangsbohrung 7 wird von einem hülsenförmigen Ankerschließkörper 8 gesteuert, der mit einem zur Ausgangsbohrung 7 konzentrischen, ringförmigen Sitz 9 auf der oberen Stirnseite des Ventilkörpers 2 zusammenwirkt.Within the valve body 2, a throttled outlet bore 7 for the control chamber 3 is arranged. This output bore 7 is controlled by a sleeve-shaped armature closing body 8, which cooperates with a concentric to the output hole 7, annular seat 9 on the upper end face of the valve body 2.

Wenn der Ankerschließkörper 8 von dem Sitz 9 abhebt, wird die Ausgangsbohrung 7 mit einem in dem Injektorkörper 1 vorgesehenen Niederdruckraum 10 verbunden, der über (nicht dargestellte) vorzugsweise in dem Injektorkörper 1 angeordnete Leitungsverbindungen mit dem Kraftstoffniederdrucksystem, beispielsweise dem Tank 11, verbunden ist.When the armature closing body 8 lifts off from the seat 9, the outlet bore 7 is connected to a low-pressure space 10 provided in the injector body 1, which is connected to the fuel low-pressure system, for example the tank 11, via line connections (not shown) preferably in the injector body 1.

Wenn der Ankerschließkörper 8 die dargestellte Schließlage einnimmt, wird die Steuerkammer 3 mit unter Hochdruck stehendem Kraftstoff befüllt, und der Plunger 4 wird nach abwärts in die Schließlage der Injektornadel geschoben. Sobald der Ankerschließkörper 8 von dem Sitz 9 abhebt, sinkt der Druck in der Steuerkammer 3 durch Entlastung in den Niederdruckraum 10 ab, und der Plunger 4 wird zusammen mit der Injektornadel nach Aufwärts geschoben, so dass die Injektornadel die Einspritzöffnungen freigibt. Dieser Aufwärtsschub wird durch die auf die Injektornadel einwirkenden hydraulischen Kräfte beziehungsweis eine Öffnungsfeder ermöglicht.When the armature closing body 8 assumes the illustrated closed position, the control chamber 3 is filled with fuel under high pressure, and the plunger 4 is pushed downwards into the closed position of the Injektornadel. As soon as the armature closing body 8 lifts off from the seat 9, the pressure in the sinks Control chamber 3 by discharge in the low-pressure chamber 10, and the plunger 4 is pushed together with the Injektornadel upwards, so that the Injektornadel the injection ports releases. This upward thrust is made possible by the hydraulic forces or an opening spring acting on the injector needle.

Innerhalb des hülsenförmigen Ankerschließkörpers 8 ist ein Ankerbolzen 13 angeordnet, auf dem der Ankerschließkörper 8 verschiebbar angeordnet ist. Dabei ist der Ringspalt zwischen dem Außenumfang des Ankerbolzens 13 und dem Innenumfang des Ankerschließkörpers 8 als Dichtspalt ausgebildet.Within the sleeve-shaped armature closing body 8, an anchor bolt 13 is arranged, on which the armature closing body 8 is arranged displaceably. In this case, the annular gap between the outer circumference of the anchor bolt 13 and the inner circumference of the armature closing body 8 is formed as a sealing gap.

An dem oberen Ende des Ankerschließkörpers 8 ist ein Anker 14 angeordnet, der mit einer ringförmigen Elektromagnetanordnung 15 zusammenwirkt. Mittels einer zu dem Ankerbolzen 13 konzentrischen Druckfeder 16 wird der Anker 14 mit dem Ankerschließkörper 8 gegen den Sitz 9 gespannt. Bei elektrischer Bestromung der Elektromagnetanordnung 15 werden der Anker 14 und der Ankerschließkörper 8 gegen die Kraft der Druckfeder 16 aus der dargestellten Schließlage des Ankerschließkörpers 8 ausgehoben und in eine obere Endlage gebracht, in der der Anker 14 auf ringförmigen Polschuhen 17 der Elektromagnetanordnung 15 aufsitzt. Sobald die elektrische Bestromung der Elektromagnetanordnung 15 abgeschaltet wird, verstellt die Druckfeder 16 den Ankerschließkörper 8 wieder in die dargestellte Schließlage.At the upper end of the armature closing body 8, an armature 14 is arranged, which cooperates with an annular electromagnet arrangement 15. By means of a concentric to the anchor bolt 13 compression spring 16, the armature 14 is tensioned with the armature closing body 8 against the seat 9. When electrical energization of the solenoid assembly 15, the armature 14 and the armature closing body 8 are lifted against the force of the compression spring 16 from the illustrated closed position of the armature closing body 8 and placed in an upper end position in which the armature 14 is seated on annular pole pieces 17 of the solenoid assembly 15. As soon as the electric energization of the electromagnet arrangement 15 is switched off, the pressure spring 16 again displaces the armature closing body 8 into the illustrated closed position.

Der über die Ausgangsbohrung 7 von der Steuerkammer 3 in einen Raum 25 unterhalb des Ankerbolzens 13 zugeführte Kraftstoff wirkt auf ein unteres zweite Stirnende 18 des Ankerbolzens 13 ein, so dass der Ankerbolzen 13 mit einem oberen, ersten Stirnende 19 gegen eine Halteplatte 20 des Injektorkörpers 1 angeschoben wird. Durch die beim Betrieb der Steuerventilanordnung auftretenden Druckschwankungen wird der Ankerbolzen 13 mit dem ersten Stirnende 19 phasenweise gegen die Halteplatte 20 bewegt und es kann somit in dem Kontaktbereich zwischen dem ersten Stirnende 19 und der Halteplatte 20 ein mechanischer Verschleiß auftreten, der die Dauerhaltbarkeit der Steuerventilanordnung beinträchtigen kann. Um einen möglichen Verschleiß zu verhindern oder zumindest deutlich zu verringern, ist in dem dargestellten Ausführungsbeispiel in den Ankerbolzen 13 ein Durchgangskanal 21, beispielsweise in Form einer Bohrung eingelassen, der in einen Fluidraum 22 in dem ersten Stirnende 19 des Ankerbolzens 13 mündet. In dem Ausführungsbeispiel ist der Fluidraum 22 von einer taschenförmig ausgebildeten Schmiertasche 23 gebildet, die den Durchgangskanal 21 im Bereich des ersten Stirnendes 19 umgibt.The supplied via the output bore 7 of the control chamber 3 in a space 25 below the anchor bolt 13 fuel acts on a lower second end face 18 of the anchor bolt 13, so that the anchor bolt 13 with an upper, first end face 19 against a retaining plate 20 of the injector body. 1 is pushed. Due to the pressure fluctuations occurring during operation of the control valve arrangement, the anchor bolt 13 is moved in phase with the first end face 19 against the holding plate 20 and thus it can in the contact area between the first end face 19 and the holding plate 20, a mechanical wear occur that impair the durability of the control valve assembly can. In order to prevent possible wear or at least to significantly reduce it, in the illustrated embodiment in the anchor bolt 13, a through-channel 21, for example, in the form of a bore, which opens into a fluid space 22 in the first end face 19 of the anchor bolt 13. In the exemplary embodiment, the fluid space 22 is formed by a pocket-shaped lubricating pocket 23 which surrounds the passage 21 in the area of the first end face 19.

In einer weiteren Ausführungsform der Erfindung kann der Fluidraum 22 aber auch nur von dem oberen Bereich des Durchgangskanals 21 - also ohne Schmiertasche 23 - gebildet sein. Eine wiederum andere Ausführungsform sieht nur die Schmiertasche 23 vor, die dann in geeigneter Form mit Fluid beschickt wird. Bei dieser Ausführungsform ist kein Durchgangskanal 21 vorhanden.In a further embodiment of the invention, however, the fluid space 22 can also be formed only from the upper region of the through-channel 21-that is to say without the lubricating pocket 23. Yet another embodiment provides only the lubricating pocket 23, which is then suitably charged with fluid. In this embodiment, no through-passage 21 is present.

Figur 2 zeigt eine Detailansicht X des Kontaktbereichs des ersten Stirnendes 19 des Ankerbolzens 13 und beziehungsweise mit der Halteplatte 20. Durch den beschriebenen Durchgangskanal 21 gelangt Kraftstoff in den von der Schmiertasche 23 gebildeten Fluidraum 22 und bewirkt eine hydrostatische Lagerung des Ankerbolzens 13 gegenüber der Halteplatte 20. Durch ein von den Druckschwankungen in dem System bewirktes Atmen (in Form von dadurch verursachten geringen Längenänderungen) des Ankerbolzens 13 wird phasenweise zwischen dem ersten Stirnende 19 des Ankerbolzens 13 und der Halteplatte 20 ein Leckagespalt 24 gebildet, durch den eine Leckagemenge von Kraftstoff in den auch in diesem Bereich des Kraftstoffinjektors vorhandenen Niederdruckraum 10 abströmt. Durch die Variation des Durchmessers D der Schmiertasche 23 beziehungsweise des Fluidraums 22 kann die mechanische Anpresskraft des ersten Stirnendes 19 des Ankerbolzens 13 gegenüber der Halteplatte 20 in dem Leckagespalt 24 eingestellt werden. Ein großer Durchmesser D bedeutet eine geringe mechanische Anpresskraft und damit eine größere Leckage. Durch Reduzierung des Durchmessers D kann die mechanische Anpresskraft erhöht werden und die Leckage verringert werden. Die Grundform des ersten Stirnendes 19 des Ankerbolzens 13 kann halbkugelförmig oder plan sein. In dem dargestellten Ausführungsbeispiel gemäß Figur 2 ist ausgehend von einer halbkugelförmigen Grundform das Stirnende geplant worden und zusätzlich die Schmiertasche 23 in die geplante Fläche eingearbeitet worden. FIG. 2 shows a detailed view X of the contact region of the first end face 19 of the anchor bolt 13 and with the holding plate 20. Through the described passage 21 fuel passes into the fluid chamber 22 formed by the lubricating pocket 23 and causes a hydrostatic bearing of the anchor bolt 13 relative to the holding plate 20. Durch a breathing caused by the pressure fluctuations in the system (in the form of small changes in length caused thereby) of the anchor bolt 13, a leakage gap 24 is formed in phases between the first front end 19 of the anchor bolt 13 and the holding plate 20, through which a leakage amount of fuel in the also in this region of the fuel injector existing low-pressure space 10 flows. By varying the diameter D of the lubricating pocket 23 and the fluid space 22, the mechanical contact pressure of the first end face 19 of the anchor bolt 13 relative to the holding plate 20 in the leakage gap 24 can be adjusted. A large diameter D means a low mechanical contact pressure and thus a larger leakage. By reducing the diameter D, the mechanical contact pressure can be increased and the leakage can be reduced. The basic shape of the first front end 19 of the anchor bolt 13 may be hemispherical or planar. In the illustrated embodiment according to FIG. 2 has been planned starting from a hemispherical basic shape, the front end and additionally the lubricating pocket 23 has been incorporated into the planned area.

Claims (11)

  1. Control valve arrangement for an injector, having a sleeve-shaped armature closing body (8) which is arranged in axially displaceable fashion on an armature pin (13) and the first face end (19) of which is supported on a static holding plate (20) and the second face end (18) of which is, during the operation of the injector, acted on with high pressure in phases,
    characterized in that a fluid space (22) is formed in the region between the first face end (19) of the armature pin (13) and the holding plate (20), wherein the armature pin (13) has a fluid-conducting passage duct (21) which connects the first face end (19) to the second face end (18).
  2. Control valve arrangement according to Claim 1,
    characterized in that the armature pin (13) has a fluid-conducting lubricating pocket (23) on the first face end (19).
  3. Control valve arrangement according to Claim 2,
    characterized in that the lubricating pocket (23) is of pot-shaped form.
  4. Control valve arrangement according to Claim 2 or 3,
    characterized in that the lubricating pocket (23) surrounds the passage duct (21).
  5. Control valve arrangement according to either of Claims 2 and 3,
    characterized in that the passage duct (21) has a throttle point.
  6. Control valve arrangement according to one of the preceding claims,
    characterized in that the second face end (18) adjoins a space (25) which is connected via an outlet bore (7) to a control chamber (3).
  7. Control valve arrangement according to one of the preceding claims,
    characterized in that the first face end (19) has a hemispherical basic shape.
  8. Control valve arrangement according to one of Claims 1 to 6,
    characterized in that the first face end (19) has a planar basic shape.
  9. Control valve arrangement according to one of the preceding claims,
    characterized in that a fluid-conducting low-pressure space (10) is formed between the holding plate (20) and an electromagnet arrangement (15) of the control valve arrangement.
  10. Control valve arrangement according to Claim 9,
    characterized in that the low-pressure space (10) is connected to a low-pressure system.
  11. Injector having a control valve arrangement according to one of the preceding claims,
    characterized in that the injector is a fuel injector.
EP15202937.7A 2015-02-16 2015-12-29 Control valve assembly Not-in-force EP3056725B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015202726.0A DE102015202726A1 (en) 2015-02-16 2015-02-16 Control valve assembly

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Publication Number Publication Date
EP3056725A1 EP3056725A1 (en) 2016-08-17
EP3056725B1 true EP3056725B1 (en) 2017-07-12

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ID=55066436

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15202937.7A Not-in-force EP3056725B1 (en) 2015-02-16 2015-12-29 Control valve assembly

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EP (1) EP3056725B1 (en)
DE (1) DE102015202726A1 (en)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021741A1 (en) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102006021736A1 (en) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102007047151A1 (en) * 2007-10-02 2009-04-09 Robert Bosch Gmbh Injector with control valve sleeve
DE102007047129A1 (en) * 2007-10-02 2009-04-09 Robert Bosch Gmbh Injector with sleeve-shaped control valve element
DE102009029563A1 (en) * 2009-09-18 2011-03-24 Robert Bosch Gmbh injector
DE102010001486A1 (en) 2010-02-02 2011-08-04 Robert Bosch GmbH, 70469 Control valve arrangement of a fuel injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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EP3056725A1 (en) 2016-08-17
DE102015202726A1 (en) 2016-08-18

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