EP2185807B1 - Control valve for a fuel injector - Google Patents

Control valve for a fuel injector Download PDF

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Publication number
EP2185807B1
EP2185807B1 EP08787092A EP08787092A EP2185807B1 EP 2185807 B1 EP2185807 B1 EP 2185807B1 EP 08787092 A EP08787092 A EP 08787092A EP 08787092 A EP08787092 A EP 08787092A EP 2185807 B1 EP2185807 B1 EP 2185807B1
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EP
European Patent Office
Prior art keywords
valve
control
guide
valve sleeve
region
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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EP08787092A
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German (de)
French (fr)
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EP2185807A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2185807A1 publication Critical patent/EP2185807A1/en
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Publication of EP2185807B1 publication Critical patent/EP2185807B1/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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a control valve for a fuel injector with the features of the preamble of claim 1.
  • Out EP 1 612 403 A1 is a force-balanced control valve is known in which a valve sleeve is guided axially movable on a valve body.
  • the valve sleeve defines an annular space to the outside, which is connected to a control chamber of a nozzle needle of the fuel injector via an outlet throttle.
  • a closing spring By a closing spring, the valve sleeve is pressed against a valve seat formed on the valve body and thereby closes the annular space to the outside.
  • the valve sleeve is moved by an electromagnetic actuator and thereby operated force-free, ie, that no force is exerted in the direction of movement of the valve sleeve by the fuel pressure in the annulus.
  • valve sleeve is pulled away via an electromagnet of the electromagnetic actuator from the valve seat, which can be done very quickly by the lack of hydraulic force component and overcoming the relatively small closing force of the closing spring.
  • the control chamber of the nozzle needle is connected to a low-pressure / return system and as a result depressurized.
  • a disadvantage of such a technical solution is that over the system pressure, the dynamics of the fuel injector on the control valve remains constant and the control valve does not open automatically at massive excess of the maximum pressure in order to have a safety function.
  • the control valve according to the invention with the characterizing features of claim 1 has the advantage that the control valve opens faster. This is achieved by the formation of a dynamic pressure stage in the guide gap between the valve sleeve and guide pin.
  • the dynamic pressure level is created by a targeted widening of the guide clearance on the valve sleeve by the valve sleeve in the region of the valve seat portion is stiff and relatively soft in the remaining area of the guide portion.
  • the valve sleeve in the region of the valve seat portion has a higher rigidity than in the region of the guide portion, so that the guide clearance of the guide diameter of the valve sleeve widens relative to the valve seat diameter with increasing pressure in the annular space.
  • the minimum, self-forming dynamic pressure stage generates, for example, at an increase in pressure from 200 to 1800 bar an opening force of, for example, 8 - 10N.
  • this dynamic pressure stage causes the control valve to open automatically when the closing force of the closing spring is exceeded, thereby reducing the pressure in the uncritical low-pressure / return region.
  • the force-balanced function of the control valve is maintained in that the valve seat has the same diameter as the guide portion of the valve sleeve.
  • the dynamic pressure stage which forms relative to the diameter of the valve seat, arises because within the valve sleeve of the annulus is pressurized with system pressure of the common rail and the valve sleeve from the outside surrounded by the leak oil pressure, which corresponds to the pressure of the low pressure / return system, for example, 10 bar.
  • valve sleeve in the form that in the region of the guide portion, the valve sleeve is made relatively soft compared to the region of the valve seat portion is advantageously formed by the outer diameter D1 in the region of the guide portion is smaller than the outer diameter D2 in the region of the valve seat portion.
  • a fuel injector for a common rail system of a diesel injection device is shown in partial section, with an injector housing 10, a base body 11, a nozzle needle 12, a control valve 13 and an actuating element 14.
  • the main body 11, a guide member 15 for the nozzle needle 12 and a valve member 16 for the control valve 13 is inserted hydraulically tight in the injector 10 and separates a high-pressure chamber 17 of a low-pressure chamber 37.
  • annular high-pressure chamber 17 opens a high-pressure bore 18 which is connected to the unillustrated Commom Rail system.
  • a control chamber 20 is formed, to which the nozzle needle 12 is exposed to a control surface 21. From the high-pressure chamber 17, an inlet bore 22 with an inlet throttle 23 leads into the control chamber 20.
  • the valve piece 16 has a guide pin 31, on which a valve sleeve 32 is arranged to be axially displaceable.
  • the valve sleeve 32 is designed with a guide cylinder 34 and a plate-shaped magnet armature 35.
  • the valve sleeve 32 is guided axially displaceably with the guide cylinder 34 with a guide diameter d on the guide pin 31, wherein a guide gap 39 is present in the region of the guide diameter d between the guide pin 31 and the valve sleeve 32.
  • the valve sleeve 32 has a control chamber remote end portion 45 and a control near the end portion 47.
  • a sealing surface 43 is further formed, with which the valve sleeve 32 rests with a valve seat diameter on a valve seat 33 formed on the valve seat 33.
  • the sealing surface 43 and the valve seat 33 can, as the embodiments in FIG. 1 . 3 and 4 or FIG. 2 and 4 show, be formed at different locations on the valve member 16 and on the valve sleeve 32.
  • valve sleeve 32 Between guide pin 31 and valve sleeve 32, an annular space 36 is further formed.
  • the valve sleeve 32 is further surrounded by the low pressure chamber 37, which is connected to a pressurized with leak oil pressure, not shown, low pressure / return system.
  • a closing spring 38 acts on the valve sleeve 32, so that the valve sleeve 32 is held with the sealing surface 43 against the valve seat 33 in the closed position.
  • a riser 25 with an outlet throttle 26 and, for example, two oblique holes 27 are arranged, which lead from the riser hole 25 into the annular space 36.
  • About the riser 25 with the outlet throttle 26 and the oblique holes 27 of the control chamber 20 is hydraulically connected to the annular space 36.
  • the adjusting element 14 which is for example a magnetic actuator, comprises a magnetic coil 41, which is fixed in a magnetic core 42 and acts on the armature 35 of the valve sleeve 32.
  • the electromagnetic actuator 14 forms together with the control valve 13, a servo-valve for controlling the control chamber 20th
  • the valve sleeve 32 has a guide portion 48 and a valve seat portion 49.
  • the guide portion 48 is formed with an outer diameter D1 and the valve seat portion 49 with an outer diameter D2, where D1 ⁇ D2.
  • the annular space 36 is incorporated in the valve sleeve 32.
  • the valve seat 33 is formed there on an actuating element-side section of the guide pin 31.
  • the valve seat portion 49 with the outer diameter D2 and with the sealing surface 43 located at the control room remote end portion 45 of the valve sleeve 32.
  • the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the valve sleeve 32 at the control room remote end portion 45 through the plate-shaped armature 35 is stronger than in the underlying guide section 48.
  • the annular space 36 is incorporated in the guide pin 31.
  • the valve seat portion 33 is located at a control-room-side end portion of the guide pin 31.
  • the valve seat portion 49 with the outer diameter D2 and the sealing surface 43 is located at the control chamber near end portion 47 of the valve sleeve 32.
  • the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the Valve sleeve 32 is thickened at the control chamber near end portion 47.
  • the valve sleeve 32 on the valve seat portion 49 is relatively stiff and the rest of the guide portion 48 relative soft. This measure has the effect that the guide diameter d of the valve sleeve 32 in the region of the guide section 48 can widen relative to the valve seat diameter of the valve seat 33. In the region of the valve seat portion 49, the valve sleeve 32 remains rigid, so that there the guide diameter d does not expand or significantly less expands than in the region of the guide portion 48, so that there the guide diameter d corresponds substantially to the valve seat diameter. As a result arises according to FIGS.
  • valve sleeve 32 The rigidity of the valve sleeve 32 should be designed so that the pressure stage 51 acts in the opening direction of the valve seat 33 of the valve sleeve 32.
  • the widening 50 arises due to the high pressure of, for example, 1800 bar of the common rail pressure, which acts via the riser bore 25, the oblique bore 27 and via the annular space 36 in the guide gap 39 from the inside to the valve sleeve 32. Because only the pressure in the low-pressure chamber 37 leak oil pressure of less than 10 bar acts on the outside of the valve sleeve 32, said expansion 50 is formed with the dynamically acting compression stage 51st
  • the emergence of the expansion 50 is exploited by the present invention to produce relative to the valve seat diameter of the valve seat 33, the dynamic pressure acting stage 51 in the guide gap 39 in the opening direction of the valve sleeve 32. This ensures that the valve sleeve 32 opens quickly when actuated by the actuator 14 and / or that at a rail pressure exceeding the valve sleeve 32 lifts off the valve seat 33 without activation by the actuator 14.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Steuerventil für einen Kraftstoffinjektor mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a control valve for a fuel injector with the features of the preamble of claim 1.

Aus EP 1 612 403 A1 ist ein kraftausgeglichenes Steuerventil bekannt, bei dem an einem Ventilkörper eine Ventilhülse axial bewegbar geführt ist. Die Ventilhülse begrenzt einen Ringraum nach außen, der mit einem Steuerraum einer Düsennadel des Kraftstoffinjektors über eine Ablaufdrossel verbunden ist. Durch eine Schließfeder wird die Ventilhülse gegen einen am Ventilkörper ausgebildeten Ventilsitz gepresst und verschließt dadurch den Ringraum nach außen. Die Ventilhülse wird von einem elektromagnetischen Stellelement bewegt und dabei kraftfrei betrieben, d.h., dass auf die Ventilhülse durch den Kraftstoffdruck im Ringraum keine resultierende Kraft in deren Bewegungsrichtung ausgeübt wird. Soll nun eine Einspritzung mittels des Kraftstoffinjektors erfolgen, so wird die Ventilhülse über einen Elektromagneten des elektromagnetischen Stellelements vom Ventilsitz weggezogen, was durch die fehlende hydraulische Kraftkomponente und der Überwindung der relativ kleinen Schließkraft der Schließfeder sehr schnell geschehen kann. Dadurch wird der Steuerraum der Düsennadel mit einem Niederdruck-/Rücklaufsystem verbunden und infolgedessen druckentlastet. Nachteilig bei einer derartigen technischen Lösung ist, dass über den Systemdruck die Dynamik des Kraftstoffinjektors am Steuerventil konstant bleibt und das Steuerventil bei massiver Überschreitung des maximalen Drucks nicht selbstständig öffnet, um damit eine Sicherheitsfunktion zu haben.Out EP 1 612 403 A1 is a force-balanced control valve is known in which a valve sleeve is guided axially movable on a valve body. The valve sleeve defines an annular space to the outside, which is connected to a control chamber of a nozzle needle of the fuel injector via an outlet throttle. By a closing spring, the valve sleeve is pressed against a valve seat formed on the valve body and thereby closes the annular space to the outside. The valve sleeve is moved by an electromagnetic actuator and thereby operated force-free, ie, that no force is exerted in the direction of movement of the valve sleeve by the fuel pressure in the annulus. Now, if an injection by means of the fuel injector, the valve sleeve is pulled away via an electromagnet of the electromagnetic actuator from the valve seat, which can be done very quickly by the lack of hydraulic force component and overcoming the relatively small closing force of the closing spring. As a result, the control chamber of the nozzle needle is connected to a low-pressure / return system and as a result depressurized. A disadvantage of such a technical solution is that over the system pressure, the dynamics of the fuel injector on the control valve remains constant and the control valve does not open automatically at massive excess of the maximum pressure in order to have a safety function.

Insbesondere bei Common-Rail-Einspritzsystemen kann das Problem auftreten, dass es zu einem Überdruck innerhalb des Kraftstoffeinspritzventils oder des Hochdruckspeichers kommt. Damit derartige Druckspitzen innerhalb des Kraftstoffinjektors rasch abgebaut werden können und somit Schäden an diesen vermieden werden, wird in der DE-Patentanmeldung 102006027485.7 vorgeschlagen, die Ventilhülse mit einer in Öffnungsrichtung des Steuerventils wirkenden Druckstufe auszuführen, die dem Ringraum ausgesetzt ist. Dadurch wird bei einem Überdruck im Steuerraum des Kraftstoffinjektors entgegen der Kraft der Schließfeder das Steuerventil geöffnet und der Druck in das Niederdruck-/Rücklaufsystem entspannt.In particular, in common-rail injection systems, the problem may arise that there is an overpressure within the fuel injection valve or the high-pressure accumulator. So that such pressure peaks within the fuel injector can be rapidly reduced and thus damage to these avoided, is in the DE patent application 102006027485.7 proposed to perform the valve sleeve with an acting in the opening direction of the control valve pressure stage, which is exposed to the annulus. As a result, in the case of an overpressure in the control chamber of the fuel injector, the control valve is opened against the force of the closing spring and the pressure in the low-pressure / return system is released.

Darlegung der ErfindungPresentation of the invention

Das erfindungsgemäße Steuerventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass das Steuerventil schneller öffnet. Erreicht wird dies durch die Ausbildung einer dynamischen Druckstufe im Führungsspalt zwischen Ventilhülse und Führungszapfen. Die dynamische Druckstufe entsteht durch eine gezielte Aufweitung des Führungsspiels an der Ventilhülse, indem die Ventilhülse im Bereich des Ventilsitzabschnitts steif und im übrige Bereich des Führungsabschnitts relativ weich ausgebildet ist. Dadurch weist die Ventilhülse im Bereich des Ventilsitzabschnitts eine höhere Steifigkeit auf als im Bereich des Führungsabschnitts, so dass sich das Führungsspiel des Führungsdurchmessers der Ventilhülse relativ zum Ventilsitzdurchmesser mit zunehmendem Druck im Ringraum aufweitet. Die minimale, selbsttätig sich ausbildende dynamische Druckstufe erzeugt beispielsweise bei einem Druckanstieg von 200 auf 1800 bar eine Öffnungskraft von beispielsweise 8 - 10N. Gleichzeitig bewirkt diese dynamische Druckstufe, dass bei Überschreiten der Schließkraft der Schließfeder das Steuerventil selbsttätig öffnet und dadurch den Druck in den unkritischen Niederdruck-/Rücklaufbereich abbaut. Die kraftausgeglichene Funktion des Steuerventiles wird dadurch beibehalten, in dem der Ventilsitz den gleichen Durchmesser besitzt wie der Führungsabschnitt der Ventilhülse.The control valve according to the invention with the characterizing features of claim 1 has the advantage that the control valve opens faster. This is achieved by the formation of a dynamic pressure stage in the guide gap between the valve sleeve and guide pin. The dynamic pressure level is created by a targeted widening of the guide clearance on the valve sleeve by the valve sleeve in the region of the valve seat portion is stiff and relatively soft in the remaining area of the guide portion. As a result, the valve sleeve in the region of the valve seat portion has a higher rigidity than in the region of the guide portion, so that the guide clearance of the guide diameter of the valve sleeve widens relative to the valve seat diameter with increasing pressure in the annular space. The minimum, self-forming dynamic pressure stage generates, for example, at an increase in pressure from 200 to 1800 bar an opening force of, for example, 8 - 10N. At the same time, this dynamic pressure stage causes the control valve to open automatically when the closing force of the closing spring is exceeded, thereby reducing the pressure in the uncritical low-pressure / return region. The force-balanced function of the control valve is maintained in that the valve seat has the same diameter as the guide portion of the valve sleeve.

Die dynamische Druckstufe, die relativ zum Durchmesser des Ventilsitzes sich ausbildet, entsteht, weil innerhalb der Ventilhülse der Ringraums mit Systemdruck des Common-Rails beaufschlagt ist und die Ventilhülse von außen vom Lecköldruck umgeben ist, der dem Druck des Niederdruck- /Rücklaufsystems von beispielsweise 10 bar entspricht.The dynamic pressure stage, which forms relative to the diameter of the valve seat, arises because within the valve sleeve of the annulus is pressurized with system pressure of the common rail and the valve sleeve from the outside surrounded by the leak oil pressure, which corresponds to the pressure of the low pressure / return system, for example, 10 bar.

Die unterschiedliche Steifigkeit der Ventilhülse in der Gestalt, dass im Bereich des Führungsabschnitts die Ventilhülse relativ weich ausgeführt ist im Vergleich zum Bereich des Ventilsitzabschnitts wird zweckmäßigerweise dadurch ausgebildet, indem der Außendurchmesser D1 im Bereich des Führungsabschnitts kleiner ist als der Außendurchmesser D2 im Bereich des Ventilsitzabschnitts.The different stiffness of the valve sleeve in the form that in the region of the guide portion, the valve sleeve is made relatively soft compared to the region of the valve seat portion is advantageously formed by the outer diameter D1 in the region of the guide portion is smaller than the outer diameter D2 in the region of the valve seat portion.

Ausführungsbeispieleembodiments

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

Es zeigen:

  • Figur 1 einen Teilschnitt eines Kraftstoffinjektors mit einem ersten
  • Ausführungsbeispiel eines Steuerventils,
  • Figur 2 einen Teilschnitt eines Kraftstoffinjektors mit einem zweiten
  • Ausführungsbeispiel eines Steuerventils
  • Figur 3 einen vergrößerten Teilschnitt durch das Steuerventil des ersten Ausführungsbeispiels in Figur 1,
  • Figur 4 einen vergrößerten Teilschnitt durch das Steuerventil gemäß Figur 1 mit einer Darstellung der dynamischen Aufweitung der Ventilhülse und
  • Figur 5 einen vergrößerten Teilschnitt durch das Steuerventil des zweiten Ausführungsbeispiels in Figur 2 mit einer Darstellung der dynamischen Aufweitung der Ventilhülse.
Show it:
  • FIG. 1 a partial section of a fuel injector with a first
  • Embodiment of a control valve,
  • FIG. 2 a partial section of a fuel injector with a second
  • Embodiment of a control valve
  • FIG. 3 an enlarged partial section through the control valve of the first embodiment in FIG. 1 .
  • FIG. 4 an enlarged partial section through the control valve according to FIG. 1 with a representation of the dynamic expansion of the valve sleeve and
  • FIG. 5 an enlarged partial section through the control valve of the second embodiment in FIG. 2 with a representation of the dynamic expansion of the valve sleeve.

In den Figuren 1 und 2 ist ein Kraftstoffinjektor für ein Common-Rail-System einer Dieseleinspritzeinrichtung im Teilschnitt dargestellt, mit einem Injektorgehäuse 10, einem Grundkörper 11, einer Düsennadel 12, einem Steuerventil 13 und einem Stellelement 14. Der Grundkörper 11, der einen Führungsteil 15 für die Düsennadel 12 und ein Ventilstück 16 für das Steuerventil 13 aufweist, ist im Injektorgehäuse 10 hydraulisch dicht eingesetzt und trennt einen Hochdruckraum 17 von einem Niederdruckraum 37. In den zwischen Injektorgehäuse 10 und Grundkörper 11 ausgebildeten ringförmigen Hochdruckraum 17 mündet eine Hochdruckbohrung 18, die an das nicht dargestelltes Commom-Rail-System angeschlossen ist. Im Führungsteil 15 des Grundkörpers 11 ist ein Steuerraum 20 ausgebildet, dem die Düsennadel 12 mit einer Steuerfläche 21 ausgesetzt ist. Vom Hochdruckraum 17 führt eine Zulaufbohrung 22 mit einer Zulaufdrossel 23 in den Steuerraum 20.In the FIGS. 1 and 2 a fuel injector for a common rail system of a diesel injection device is shown in partial section, with an injector housing 10, a base body 11, a nozzle needle 12, a control valve 13 and an actuating element 14. The main body 11, a guide member 15 for the nozzle needle 12 and a valve member 16 for the control valve 13 is inserted hydraulically tight in the injector 10 and separates a high-pressure chamber 17 of a low-pressure chamber 37. In the formed between the injector housing 10 and body 11 annular high-pressure chamber 17 opens a high-pressure bore 18 which is connected to the unillustrated Commom Rail system. In the guide part 15 of the main body 11, a control chamber 20 is formed, to which the nozzle needle 12 is exposed to a control surface 21. From the high-pressure chamber 17, an inlet bore 22 with an inlet throttle 23 leads into the control chamber 20.

Das Ventilstück 16 weist einen Führungszapfen 31 auf, an dem eine Ventilhülse 32 axial verschiebbar angeordnet ist Die Ventilhülse 32 ist mit einem Führungszylinder 34 und einem tellerförmigen Magnetanker 35 ausgeführt. Die Ventilhülse 32 ist dabei mit dem Führungszylinder 34 mit einem Führungsdurchmesser d am Führungszapfen 31 axial verschiebbar geführt, wobei im Bereich des Führungsdurchmessers d zwischen Führungszapfen 31 und Ventilhülse 32 ein Führungsspalt 39 vorliegt. Die Ventilhülse 32 weist einen steuerraumfernen Endabschnitt 45 und einen steuerraumnahen Endabschnitt 47 auf. An der Ventilhülse 32 ist weiterhin eine Dichtfläche 43 ausgebildet, mit der die Ventilhülse 32 mit einem Ventilsitzdurchmesser auf einem am Ventilstück 16 ausgebildeten Ventilsitz 33 aufliegt. Die Dichtfläche 43 und der Ventilsitz 33 können dabei, wie die Ausführungsbeispiele in Figur 1, 3 und 4 oder Figur 2 und 4 zeigen, an unterschiedlichen Stellen am Ventilstück 16 und an der Ventilhülse 32 ausgebildet sein.The valve piece 16 has a guide pin 31, on which a valve sleeve 32 is arranged to be axially displaceable. The valve sleeve 32 is designed with a guide cylinder 34 and a plate-shaped magnet armature 35. The valve sleeve 32 is guided axially displaceably with the guide cylinder 34 with a guide diameter d on the guide pin 31, wherein a guide gap 39 is present in the region of the guide diameter d between the guide pin 31 and the valve sleeve 32. The valve sleeve 32 has a control chamber remote end portion 45 and a control near the end portion 47. On the valve sleeve 32, a sealing surface 43 is further formed, with which the valve sleeve 32 rests with a valve seat diameter on a valve seat 33 formed on the valve seat 33. The sealing surface 43 and the valve seat 33 can, as the embodiments in FIG. 1 . 3 and 4 or FIG. 2 and 4 show, be formed at different locations on the valve member 16 and on the valve sleeve 32.

Zwischen Führungszapfen 31 und Ventilhülse 32 ist weiterhin ein Ringraum 36 ausgebildet. Die Ventilhülse 32 ist weiterhin vom Niederdruckraum 37 umgeben, der mit einem mit Lecköldruck beaufschlagten, nicht dargestellten Niederdruck-/Rücklaufsystem verbunden ist. Eine Schließfeder 38 wirkt auf die Ventilhülse 32, so dass die Ventilhülse 32 mit der Dichtfläche 43 gegen den Ventilsitz 33 in Schließstellung gehalten wird.Between guide pin 31 and valve sleeve 32, an annular space 36 is further formed. The valve sleeve 32 is further surrounded by the low pressure chamber 37, which is connected to a pressurized with leak oil pressure, not shown, low pressure / return system. A closing spring 38 acts on the valve sleeve 32, so that the valve sleeve 32 is held with the sealing surface 43 against the valve seat 33 in the closed position.

Im Führungszapfen 31 ist eine Steigbohrung 25 mit eine Ablaufdrossel 26 und beispielsweise zwei Schrägbohrungen 27 angeordnet, die von den Steigbohrung 25 aus in den Ringraum 36 führen. Über die Steigbohrung 25 mit der Ablaufdrossel 26 und den Schrägbohrungen 27 wird der Steuerraum 20 hydraulisch mit dem Ringraum 36 verbunden.In the guide pin 31, a riser 25 with an outlet throttle 26 and, for example, two oblique holes 27 are arranged, which lead from the riser hole 25 into the annular space 36. About the riser 25 with the outlet throttle 26 and the oblique holes 27 of the control chamber 20 is hydraulically connected to the annular space 36.

Das Stellelement 14, das beispielsweise ein Magnet-Aktor ist, umfasst eine Magnetspule 41, die in einem Magnetkern 42 fixiert ist und auf den Magnetanker 35 der Ventilhülse 32 einwirkt. Das elektromagnetische Stellelement 14 bildet zusammen mit dem Steuerventil 13 ein Servo-Ventil zur Ansteuerung des Steuerraums 20.The adjusting element 14, which is for example a magnetic actuator, comprises a magnetic coil 41, which is fixed in a magnetic core 42 and acts on the armature 35 of the valve sleeve 32. The electromagnetic actuator 14 forms together with the control valve 13, a servo-valve for controlling the control chamber 20th

Wie in Figur 3, 4 und 5 dargestellt ist, weist die Ventilhülse 32 einen Führungsabschnitt 48 und einen Ventilsitzabschnitt 49 auf. Der Führungsabschnitt 48 ist mit einem Außendurchmesser D1 und der Ventilsitzabschnitt 49 mit einem Außendurchmesser D2 ausgeführt, wobei D1 < D2 ist.As in FIGS. 3, 4 and 5 is shown, the valve sleeve 32 has a guide portion 48 and a valve seat portion 49. The guide portion 48 is formed with an outer diameter D1 and the valve seat portion 49 with an outer diameter D2, where D1 <D2.

Beim Ausführungsbeispiel gemäß Figur 1, 3 und 4 ist der Ringraum 36 in die Ventilhülse 32 eingearbeitet. Der Ventilsitz 33 ist dort an einem stellelementseitigen Abschnitt des Führungszapfens 31 ausgebildet. Der Ventilsitzabschnitt 49 mit dem Außendurchmesser D2 und mit der Dichtfläche 43 befindet am steuerraumfernen Endabschnitt 45 der Ventilshülse 32. Der größere Außendurchmesser D2 des Ventilsitzabschnitts 49 ist dadurch realisiert, indem die Wandung der Ventilshülse 32 am steuerraumfernen Endabschnitt 45 durch den tellerförmigen Magnetanker 35 stärker ist als im darunterliegenden Führungsabschnitt 48.According to the embodiment FIG. 1 . 3 and 4 the annular space 36 is incorporated in the valve sleeve 32. The valve seat 33 is formed there on an actuating element-side section of the guide pin 31. The valve seat portion 49 with the outer diameter D2 and with the sealing surface 43 located at the control room remote end portion 45 of the valve sleeve 32. The larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the valve sleeve 32 at the control room remote end portion 45 through the plate-shaped armature 35 is stronger than in the underlying guide section 48.

Bei Ausführungsbeispiel in Figur 2 und 5 ist der Ringraum 36 in den Führungszapfen 31 eingearbeitet. Der Ventilsitz 33 befindet sich hierbei an einem steuerraumseitigen Endabschnitt des Führungszapfens 31. Der Ventilsitzabschnitt 49 mit dem Außendurchmesser D2 und mit der Dichtfläche 43 befindet am steuerraumnahen Endabschnitt 47 der Ventilshülse 32. Der größere Außendurchmesser D2 des Ventilsitzabschnitts 49 ist dadurch realisiert, indem die Wandung der Ventilshülse 32 am steuerraumnahen Endabschnitt 47 verdickt ist.In embodiment in FIG. 2 and 5 the annular space 36 is incorporated in the guide pin 31. The valve seat portion 33 is located at a control-room-side end portion of the guide pin 31. The valve seat portion 49 with the outer diameter D2 and the sealing surface 43 is located at the control chamber near end portion 47 of the valve sleeve 32. The larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the Valve sleeve 32 is thickened at the control chamber near end portion 47.

Dadurch, dass der Außendurchmesser D2 des Ventilssitzabschnitts 49 größer ist als der Außendurchmesser D1 des Führungsabschnitts 48 ist die Ventilhülse 32 am Ventilsitzabschnitt 49 relativ steif und der übrige Führungsabschnitt 48 relativ weich ausgebildet. Diese Maßnahme bewirkt, dass sich der Führungsdurchmesser d der Ventilhülse 32 im Bereich des Führungsabschnitts 48 relativ zum Ventilsitzdurchmesser des Ventilsitzes 33 aufweiten kann. Im Bereich des Ventilsitzabschnitts 49 bleibt die Ventilhülse 32 starr, so dass sich dort der Führungsdurchmesser d nicht aufweitet oder aber wesentlich weniger aufweitet als im Bereich des Führungsabschnitts 48, so dass dort der Führungsdurchmesser d im Wesentlichen dem Ventilsitzdurchmesser entspricht. Infolgedessen entsteht gemäß Figur 4 und 5 im Führungsspalt 39 zwischen Führungszapfen 31 und Ventilhülse 32 im Bereich des Führungsanschnittes 48 vornehmlich angrenzend an den Ringraum 36 eine Aufweitung 50, die eine Druckstufe 51 am Führungsdurchmesser d der Ventilhülse 32 ausbildet. Die Steifigkeit der Ventilhülse 32 sollte dabei so ausgeführt sein, dass die Druckstufe 51 in Öffnungsrichtung des Ventilssitzes 33 der Ventilhülse 32 wirkt.Characterized in that the outer diameter D2 of the valve seat portion 49 is greater than the outer diameter D1 of the guide portion 48, the valve sleeve 32 on the valve seat portion 49 is relatively stiff and the rest of the guide portion 48 relative soft. This measure has the effect that the guide diameter d of the valve sleeve 32 in the region of the guide section 48 can widen relative to the valve seat diameter of the valve seat 33. In the region of the valve seat portion 49, the valve sleeve 32 remains rigid, so that there the guide diameter d does not expand or significantly less expands than in the region of the guide portion 48, so that there the guide diameter d corresponds substantially to the valve seat diameter. As a result arises according to FIGS. 4 and 5 in the guide gap 39 between the guide pin 31 and the valve sleeve 32 in the region of the guide section 48, primarily adjacent to the annular space 36 a widening 50, which forms a pressure step 51 on the guide diameter d of the valve sleeve 32. The rigidity of the valve sleeve 32 should be designed so that the pressure stage 51 acts in the opening direction of the valve seat 33 of the valve sleeve 32.

Die Aufweitung 50 entsteht aufgrund des Hochdrucks von beispielsweise 1800 bar des Common-Rails-Drucks, der über die Steigbohrung 25, die Schrägbohrung 27 und über den Ringraum 36 im Führungsspalt 39 von innen auf die Ventilhülse 32 wirkt. Weil von außen auf die Ventilhülse 32 lediglich der im Niederdruckraum 37 anliegende Lecköldruck von unter 10 bar wirkt, entsteht die genannte Aufweitung 50 mit der dynamisch wirkenden Druckstufe 51.The widening 50 arises due to the high pressure of, for example, 1800 bar of the common rail pressure, which acts via the riser bore 25, the oblique bore 27 and via the annular space 36 in the guide gap 39 from the inside to the valve sleeve 32. Because only the pressure in the low-pressure chamber 37 leak oil pressure of less than 10 bar acts on the outside of the valve sleeve 32, said expansion 50 is formed with the dynamically acting compression stage 51st

Das Entstehen der Aufweitung 50 wird von der vorliegenden Erfindung ausgenutzt, um relativ zum Ventilsitzdurchmesser des Ventilsitzes 33 die dynamische wirkende Druckstufe 51 im Führungsspalt 39 in Öffnungsrichtung der Ventilhülse 32 zu erzeugen. Dadurch wird gewährleistet, dass die Ventilhülse 32 bei Ansteuerung durch des Stellelement 14 schnell öffnet und/oder dass bei einer Rail-Druck-Überschreitung die Ventilhülse 32 vom Ventilsitz 33 auch ohne Ansteuerung durch das Stellelement 14 abhebt.The emergence of the expansion 50 is exploited by the present invention to produce relative to the valve seat diameter of the valve seat 33, the dynamic pressure acting stage 51 in the guide gap 39 in the opening direction of the valve sleeve 32. This ensures that the valve sleeve 32 opens quickly when actuated by the actuator 14 and / or that at a rail pressure exceeding the valve sleeve 32 lifts off the valve seat 33 without activation by the actuator 14.

Claims (7)

  1. Control valve for activating a control space (20) of a fuel injector, with a valve sleeve (32) which is guided moveably with a guide diameter d on a guide pin (31) by means of a guide cylinder (34) and presses with a closing force against a valve seat (33) formed on the guide pin (31), the valve sleeve (32) being actuable by an actuating element (14) and having a guide portion (48) and a valve-seat portion (49), a guide gap (39) being present between the valve sleeve (32) and guide pin (31) and an annular space (36) being formed, the annular space (36) being delimited by the valve sleeve (32) in interaction with the valve seat (33), and the annular space (36) and control space (20) being connected via a hydraulic connection (25, 26, 27), characterized in that the valve sleeve (32) has higher rigidity in the region of the valve-seat portion (49) than in the region of the guide portion (48), in such a way that in the event of high pressure acting in the annular space (36), an expansion (50) of the guide gap (39) at the valve sleeve (32) appears, is restricted essentially to the region of the guide portion (48) and forms there a dynamic pressure step (51) on the guide diameter d of the valve sleeve (32), the dynamic pressure step (51) acting upon the valve sleeve (32) in the opening direction.
  2. Control valve according to Claim 1, characterized in that the valve sleeve (32) has an outside diameter D1 in the region of the guide portion (48) and an outside diameter D2 in the region of the valve-seat portion (49), and in that, to generate the different rigidity of the valve sleeve (32) in the region of the guide portion (48) and in the region of the valve-seat portion (49), the outside diameter D1 in the region of the guide portion (48) is smaller than the outside diameter D2 in the region of the valve-seat portion (49).
  3. Control valve according to Claim 1 or 2, characterized in that the valve sleeve (32) has a control-space-remote end portion (45) and a control-space-near end portion (47), and in that the valve-seat portion (49) is formed on the control-space-remote end portion (45).
  4. Control valve according to Claim 1 or 2, characterized in that the valve sleeve (32) has a control-space-remote end portion (45) and a control-space-near end portion (47), and in that the valve-seat portion (49) is formed on the control-space-near end portion (47).
  5. Control valve according to one of the preceding claims, characterized in that the annular space (36) is formed on the valve sleeve (32).
  6. Control valve according to one of the preceding claims, characterized in that the annular space (36) is formed on the valve piece (31).
  7. Control valve according to one of the preceding claims, characterized in that the high pressure corresponds to the system pressure of a common rail of a diesel injection device.
EP08787092A 2007-08-27 2008-08-11 Control valve for a fuel injector Not-in-force EP2185807B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710040248 DE102007040248A1 (en) 2007-08-27 2007-08-27 Control valve for a fuel injector
PCT/EP2008/060518 WO2009027215A1 (en) 2007-08-27 2008-08-11 Control valve for a fuel injector

Publications (2)

Publication Number Publication Date
EP2185807A1 EP2185807A1 (en) 2010-05-19
EP2185807B1 true EP2185807B1 (en) 2012-10-31

Family

ID=39951479

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Application Number Title Priority Date Filing Date
EP08787092A Not-in-force EP2185807B1 (en) 2007-08-27 2008-08-11 Control valve for a fuel injector

Country Status (3)

Country Link
EP (1) EP2185807B1 (en)
DE (1) DE102007040248A1 (en)
WO (1) WO2009027215A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009046563A1 (en) * 2009-11-10 2011-05-12 Robert Bosch Gmbh fuel injector
DE102013211855A1 (en) * 2013-06-21 2014-12-24 Robert Bosch Gmbh Control valve for a fuel injector

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2277229T3 (en) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE.
EP1707797B1 (en) * 2005-03-14 2007-08-22 C.R.F. Società Consortile per Azioni Adjustable metering servovalve for a fuel injector
DE102006027485A1 (en) * 2006-06-14 2007-12-20 Robert Bosch Gmbh Fuel injector with safety control valve

Also Published As

Publication number Publication date
WO2009027215A1 (en) 2009-03-05
EP2185807A1 (en) 2010-05-19
DE102007040248A1 (en) 2009-03-05

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