EP2138709A1 - Directly actuated fuel injector - Google Patents

Directly actuated fuel injector Download PDF

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Publication number
EP2138709A1
EP2138709A1 EP09100250A EP09100250A EP2138709A1 EP 2138709 A1 EP2138709 A1 EP 2138709A1 EP 09100250 A EP09100250 A EP 09100250A EP 09100250 A EP09100250 A EP 09100250A EP 2138709 A1 EP2138709 A1 EP 2138709A1
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EP
European Patent Office
Prior art keywords
valve
pressure
fuel injector
fuel
sleeve
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.)
Granted
Application number
EP09100250A
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German (de)
French (fr)
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EP2138709B1 (en
Inventor
Olaf Ohlhafer
Robert Giezendanner-Thoben
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2138709A1 publication Critical patent/EP2138709A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • DE 10 2006 050 810 refers to a fuel injector for internal combustion engines with a control room connected to a high-pressure side. About the pressure and the change in pressure, the movement of a nozzle needle is controlled.
  • a control valve locks or opens the connection of the control chamber to a low pressure side.
  • the control valve comprises a fixed valve pin which has an inner relief channel coming from the control chamber and opening into an annular groove of the valve pin. Further, a displaceably guided on the free end of the valve pin, force balanced control sleeve is provided which closes the annular groove in its closed valve position to the outside and opens in their direction towards the free end of the valve pin open valve position, the compound of the annular groove to the low pressure side.
  • Fuel injectors of this type therefore inherently have a necessary for the realization of the needle stroke control flow and, where appropriate, a leakage volume flow, which leads to an increased required delivery capacity of the high-pressure pump.
  • a delayed response of the injection valve member which can also be influenced by unintentionally occurring pressure fluctuations.
  • a direct actuation of the usually needle-shaped injection valve member with an electromagnetic actuator has not been possible because the required force due to the non-pressure balanced formed injection valve member at system pressures of over 2000 bar resulted in too large a magnetic actuator.
  • a concept of a fuel injector is proposed, with which the force required to open a needle-shaped injection valve member is lowered so far that the injection valve member can be lifted directly and directly via a magnetic actuator.
  • the proposed injector concept is characterized by low applied forces for opening the injection valve member, so that a direct actuation of the same by means of an electromagnet is possible.
  • the proposed solution according to the invention realizes a tax-free principle. There is no return of a controlled from a control room volume of fuel required, which on the one hand represents a reduced system overhead and on the other hand leads to smaller pump delivery in terms of high-pressure pumping unit through which the high-pressure accumulator chamber (common rail) is acted upon.
  • the proposed solution according to the invention represents a very cost-effective solution, since a simple construction can be achieved.
  • a control valve with associated inlet and outlet throttles can be omitted, as well as a push rod with respect to the injection valve member and any required leakage lines.
  • the proposed solution according to the invention realizes a concept which requires little installation space.
  • the magnetic armature cooperating with a magnetic actuator is designed as a valve sleeve.
  • a spring presses the valve sleeve into the sealing seat, which is formed, for example, on a valve piece embedded in the injector body.
  • the spring force is preset when mounting a shim, for example.
  • the valve piece is pressed via the shim into the sealing seat, so that no leakage can occur on the sealing seat. Any leakage that may occur is led out through the guide of the valve sleeve via a return line. It is important to avoid leaking into the high pressure area.
  • the leakage described here occurs between the guide the valve body and the valve sleeve in the return.
  • the return flow flows due to the pressure conditions through a laterally mounted hole upwards in the direction of a return.
  • the valve sleeve at the top of which the anchor plate is formed, is external, top and bottom of the system pressure, i. surrounded by the pressure prevailing in the high-pressure accumulator body. It is therefore pressure-balanced with respect to its axial movement and thus balanced with respect to the pressure prevailing in the high pressure reservoir body (common rail) system pressure.
  • To open the valve sleeve only the spring force must be overcome by means of a magnetic actuator.
  • the force required for opening is independent of the pressure prevailing in the high-pressure accumulator body system pressure (which is also referred to as rail pressure) and thus over the entire pressure range that occurs in the high-pressure accumulator body, constant.
  • valve sleeve which also represents the armature, pulled by the magnetic actuator upwards.
  • fuel now flows from the outside to the at least one injection port at the combustion chamber end of the fuel injector.
  • the injection openings may be embodied, for example, at the combustion chamber end in the wall of the fuel injector.
  • the energization of the magnetic actuator is interrupted.
  • the valve sleeve is urged back down into its sealing seat on the valve member by the spring force acting on it so that supply of system pressurized fuel to the at least one injection port formed at the combustion chamber end of the fuel injector is discontinued.
  • FIG. 1 is a longitudinal section through the inventively proposed fuel injector with directly actuated valve sleeve refer.
  • a fuel injector 10 as shown in FIG. 1 comprises an injector body 12, which in the illustration according to FIG. 1 is guided symmetrically to a Injektorachse 14.
  • a high pressure supply line 16 is under system pressure pending fuel.
  • the pressure level is designated, which within a in the illustration according to FIG. 1 unplayed high-pressure accumulator body (common rail) prevails. This pressure level is in the illustration according to FIG. 1 indicated by p Rail .
  • the fuel which is present at the high-pressure port 16 of the injector body 12, flows into the interior of the injector body 12 and supplies it with fuel.
  • valve piece 20 Inside the injector body 12 is a valve piece 20 which is fixed to the combustion chamber end of the injector body 12 of the fuel injector 10.
  • the valve piece 20 comprises a leakage bore 22 extending coaxially with the injector axis 14.
  • the leakage bore 22 has no direct connection to the supply line 26 or 28.
  • the fuel flows during the injection through the inlet bore 28 or the transverse bore 26.
  • the leakage bore 22 is intended to remove leakage from the blind hole, which flows through the lower guide of the valve piece with the sleeve, and the leakage from the high-pressure region passes through the guide above the transverse bore 26 into the return line (FIG.
  • valve piece 20 is installed with the aid of a dial 40 in the injector 12 and forms at the combustion chamber end a seal 32, below which extends a blind hole configured cavity. From this extend, as shown in the illustration FIG. 1 reproduced, at least two injection openings 30, via which fuel in the in FIG. 1 not shown combustion chamber of an internal combustion engine can be injected.
  • a further dial 46 is added below the dial 40.
  • This further shim 46 serves to adjust the spring force of a closing spring 44.
  • This closing spring 44 surrounds a magnetic actuator 38.
  • the magnetic actuator 38 is received in the interior of the injector body 12 and surrounded by the fuel under system pressure p rail .
  • the solenoid actuator 38 further encloses the valve member 20 which extends coaxially with the injector axis 14 through the injector body 12 of the fuel injector 10.
  • the magnetic actuator 38 acts on an armature plate 36, which is formed on the upper plan side of the axially movable in the injector body 12 valve sleeve 42.
  • the valve sleeve 42 is also enclosed on the inside of the injector body 12 by the system pressure fuel on all sides, i. pressure-balanced.
  • the adjusting washer 40, the further adjusting washer 46 for adjusting the force acting on the closing spring 44 are supported by an adjusting sleeve 48 which is arranged in the interior of the injector body 12, the valve sleeve 42 enclosing.
  • valve sleeve 42 which surrounds the valve member 20 forms at the lower end a sealing seat 24, which is formed for example as a conical seat. From the illustration according to FIG. 1 shows that even at the sealing seat 24, the in FIG. 1 is shown closed, standing under high pressure fuel from the outside.
  • the blind hole 34 is acted upon only via the concentric, ie coaxially to the injector 14 extending inlet bore 28 under system pressure p rail standing fuel.
  • the solenoid actuator 38 applies only the force required to actuate the pressure balanced valve sleeve 42.
  • the magnet armature 38 When the magnet armature 38 is energized, it pulls the armature plate 36 of the valve sleeve 42 against the force of the closing spring 44. Accordingly, the magnetic actuator 38 has only the closing force, ie the spring force which applies the closing spring 44, to overcome and can be designed accordingly.
  • the inventively proposed, directly operated fuel injector 10 is also constructed much simpler compared to previously known from the prior art fuel injectors whose operation is done indirectly via the pressure relief or pressurization of a control room.
  • the inventively proposed fuel injector 10 realizes a tax-free fuel injector, in which no return of a controlled from a control room volume in the direction of the low pressure region is required. This requires a reduced compared to previous solutions system overhead and a smaller dimensioning capacity of a delivery unit.
  • drain and inlet throttle can be omitted, as well as the control chamber and the push rod, which was previously used in generally needle-shaped injection valve members.
  • the inventively proposed fuel injector 10 is characterized by a shorter overall length compared to known from the prior art fuel injectors.
  • the representation according to FIG. 2 is to refer to the connection of the leakage hole 22 in an enlarged scale.
  • FIG. 2 puts the in FIG. 1 Circled area on an enlarged scale.
  • the return flow flows due to suitable pressure conditions and possibly to generate a negative pressure in the leakage bore 22 by the in FIG. 2 illustrated transverse holes upwards in the direction of the return.
  • the return flow occurs as soon as a leakage pressure p leakage as a function of the system pressure p rail plus a combustion chamber pressure p cylinder is greater than the pressure prevailing in the return pressure level p RL .
  • valve sleeve 42 is surrounded outside on its lateral surface at the top and at the bottom of system pressure p rail . This means that the valve sleeve 42 is pressure-balanced with respect to its axial movement and is force-balanced with respect to the system pressure p Rail .
  • the spring force which is applied by the closing spring 44, must be overcome by means of the magnet armature 38.
  • the required magnetic force is independent of the system pressure p rail and thus constant over the entire pressure range of the system pressure p rail .
  • this or its armature plate 36 is attracted by the magnetic actuator 38 upwards.
  • the fuel which is present at the valve seat 42 under system pressure p rail flows via the open valve seat 24 in the direction of the blind hole 34 and from there to the injection openings 30.
  • the energization of the magnetic actuator 38 is interrupted and the force-balanced valve sleeve 42 is pressed by the action of the spring force of the closing spring 44 back down into the valve seat 24.
  • the pressurization of the blind hole-like cavity 34 is interrupted at the combustion chamber end of the injector body 12 of the fuel injector 10 and the injection is completed.

Abstract

The injector (10) has a valve piece (20) fastened to an injector body (12), and a valve sleeve (42) guided in the valve piece. A magnetic actuator (38) is attached at an end (36) of the sleeve, and a valve seat (24) is limited at another end of the sleeve, where the sleeve is directly actuated by the magnetic actuator. The end (36) of the sleeve is formed as an armature plate. The valve piece is engaged at the injector body by an adjusting disk (40) and has a transverse borehole (26), which is connected with a supply borehole (28) in the valve piece above the valve seat.

Description

Stand der TechnikState of the art

DE 10 2006 050 810 bezieht sich auf einen Kraftstoffinjektor für Brennkraftmaschinen mit einem an einer Hochdruckseite angeschlossenen Steuerraum. Über dessen Druck bzw. dessen Druckänderung wird die Bewegung einer Düsennadel gesteuert. Ein Steuerventil sperrt oder öffnet die Verbindung des Steuerraums zu einer Niederdruckseite. Das Steuerventil umfasst einen feststehenden Ventilbolzen, welcher einen vom Steuerraum kommenden und in eine Ringnut des Ventilbolzens mündenden inneren Entlastungskanal aufweist. Ferner ist eine auf dem freien Ende des Ventilbolzens verschiebbar geführte, kraftausgeglichene Steuerhülse vorgesehen, die in ihrer geschlossenen Ventilstellung die Ringnut nach außen verschließt und in ihrer in Richtung auf das freie Ende des Ventilbolzens verschobenen geöffneten Ventilstellung die Verbindung der Ringnut zu der Niederdruckseite öffnet. DE 10 2006 050 810 refers to a fuel injector for internal combustion engines with a control room connected to a high-pressure side. About the pressure and the change in pressure, the movement of a nozzle needle is controlled. A control valve locks or opens the connection of the control chamber to a low pressure side. The control valve comprises a fixed valve pin which has an inner relief channel coming from the control chamber and opening into an annular groove of the valve pin. Further, a displaceably guided on the free end of the valve pin, force balanced control sleeve is provided which closes the annular groove in its closed valve position to the outside and opens in their direction towards the free end of the valve pin open valve position, the compound of the annular groove to the low pressure side.

Bei heute verfügbaren, magnetisch betätigten Kraftstoffinjektoren, insbesondere für selbstzündende Verbrennungskraftmaschinen, die über Hochdruckspeichersysteme (Common-Rail) mit Kraftstoff versorgt werden, erfolgt die Betätigung eines nadelförmig ausgebildeten Einspritzventilgliedes indirekt, indem eine Druckabsenkung in einem Steuerraum erfolgt. Die Differenz zwischen dem Systemdruck, d.h. dem Druckniveau, welches im Hochdruckspeicherkörper herrscht, und dem im Steuerraum jeweils herrschenden Druck bewirkt in Verbindung mit dem Größenverhältnis der druckbeaufschlagten Flächen die Bewegung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes. Dieses Prinzip kommt zum Beispiel bei heute eingesetzten Kraftstoffinjektoren zum Einsatz. Von Nachteil bei diesen Injektorkonzepten ist die Notwendigkeit, die aus dem Steuerraum jeweils abgesteuerte Steuermenge in einen Niederdruckkraftstoffrücklauf abführen zu müssen. Kraftstoffinjektoren dieser Bauart besitzen daher prinzipbedingt einen zur Realisierung des Nadelhubs erforderlichen Steuervolumenstrom sowie gegebenenfalls einen Leckagevolumenstrom, was zu einer erhöhten erforderlichen Förderleistung der Hochdruckpumpe führt. Außerdem erfolgt aus der indirekten Steuerung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes ein verspätetes Ansprechverhalten des Einspritzventilgliedes, welches auch zusätzlich durch ungewollt auftretende Druckschwankungen beeinflusst werden kann.In today available, magnetically actuated fuel injectors, especially for self-igniting internal combustion engines, which are supplied via high-pressure storage systems (common rail) with fuel, the actuation of a needle-shaped injection valve member takes place indirectly by a pressure reduction takes place in a control room. The difference between the system pressure, ie the pressure level which prevails in the high-pressure accumulator body, and the prevailing pressure in the control chamber in conjunction with the size ratio of the pressurized surfaces causes the movement of the usually needle-shaped injection valve member. This principle is used, for example, in fuel injectors used today. A disadvantage of these Injektorkonzepten is the need to dissipate each of the control room diverted control amount in a low-pressure fuel return. Fuel injectors of this type therefore inherently have a necessary for the realization of the needle stroke control flow and, where appropriate, a leakage volume flow, which leads to an increased required delivery capacity of the high-pressure pump. In addition, from the indirect control of the usually needle-shaped injection valve member a delayed response of the injection valve member, which can also be influenced by unintentionally occurring pressure fluctuations.

Eine direkte Betätigung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes mit einem elektromagnetischen Aktor ist bisher nicht möglich, da die hierzu erforderliche Kraft aufgrund des nicht druckausgeglichenen ausgebildeten Einspritzventilgliedes bei Systemdrücken von über 2000 bar zu einem zu großen Magnetaktor führte.A direct actuation of the usually needle-shaped injection valve member with an electromagnetic actuator has not been possible because the required force due to the non-pressure balanced formed injection valve member at system pressures of over 2000 bar resulted in too large a magnetic actuator.

Offenbarung der ErfindungDisclosure of the invention

Erfindungsgemäß wird eine Konzeption eines Kraftstoffinjektors vorgeschlagen, mit der die zum Öffnen eines nadelförmig ausgebildeten Einspritzventilgliedes erforderliche Kraft so weit herabgesenkt ist, dass das Einspritzventilglied direkt und unmittelbar über einen Magnetaktor angehoben werden kann. Das vorgeschlagene Injektorkonzept zeichnet sich durch geringe aufzubringende Kräfte zum Öffnen des Einspritzventilgliedes aus, so dass eine direkte Betätigung desselben mittels eines Elektromagneten möglich ist. Die erfindungsgemäß vorgeschlagene Lösung verwirklicht ein steuermengenfreies Prinzip. Es ist keine Rückführung eines aus einem Steuerraum abgesteuerten Kraftstoffvolumens erforderlich, was einerseits einen verringerten Systemaufwand darstellt und andererseits zu kleineren Pumpenförderleistungen im Hinblick auf das Hochdruckförderaggregat führt, durch welches der Hochdruckspeicherraum (Common-Rail) beaufschlagt ist.According to the invention, a concept of a fuel injector is proposed, with which the force required to open a needle-shaped injection valve member is lowered so far that the injection valve member can be lifted directly and directly via a magnetic actuator. The proposed injector concept is characterized by low applied forces for opening the injection valve member, so that a direct actuation of the same by means of an electromagnet is possible. The proposed solution according to the invention realizes a tax-free principle. There is no return of a controlled from a control room volume of fuel required, which on the one hand represents a reduced system overhead and on the other hand leads to smaller pump delivery in terms of high-pressure pumping unit through which the high-pressure accumulator chamber (common rail) is acted upon.

Des Weiteren stellt die erfindungsgemäß vorgeschlagene Lösung eine sehr kostengünstige Lösung dar, da ein einfacher Aufbau erreicht werden kann. Ein Steuerventil mit dazugehörigen Zulauf- und Ablaufdrosseln kann entfallen, ebenso wie eine Druckstange in Bezug auf das Einspritzventilglied sowie eventuell erforderliche Leckageleitungen. Schließlich verwirklicht die erfindungsgemäß vorgeschlagene Lösung ein Konzept, welches geringen Bauraum beansprucht.Furthermore, the proposed solution according to the invention represents a very cost-effective solution, since a simple construction can be achieved. A control valve with associated inlet and outlet throttles can be omitted, as well as a push rod with respect to the injection valve member and any required leakage lines. Finally, the proposed solution according to the invention realizes a concept which requires little installation space.

Der erfindungsgemäß vorgeschlagenen Lösung folgend, ist der mit einem Magnetaktor zusammenwirkende Magnetanker als Ventilhülse ausgeführt. Im geschlossenen Zustand drückt eine Feder die Ventilhülse in den Dichtsitz, der zum Beispiel an einem in den Injektorkörper eingelassenen Ventilstück ausgebildet ist. Die Federkraft wird bei der Montage einer Einstellscheibe, um ein Beispiel zu nennen, voreingestellt. Das Ventilstück wird über die Einstellscheibe in den Dichtsitz eingepresst, derart, dass keine Leckage am Dichtsitz auftreten kann. Eine möglicherweise auftretende Leckage wird durch die Führung der Ventilhülse über eine Rücklaufleitung herausgeführt. Es ist unbedingt zu vermeiden, dass Leckage in den Hochdruckbereich gelangt. Die hier beschriebene Leckage tritt durch die Führung zwischen dem Ventilkörper und der Ventilhülse in den Rücklauf. Die Rücklaufmenge fließt aufgrund der Druckverhältnisse durch eine seitlich angebrachte Bohrung nach oben in Richtung eines Rücklaufes.Following the solution proposed by the invention, the magnetic armature cooperating with a magnetic actuator is designed as a valve sleeve. In the closed state, a spring presses the valve sleeve into the sealing seat, which is formed, for example, on a valve piece embedded in the injector body. The spring force is preset when mounting a shim, for example. The valve piece is pressed via the shim into the sealing seat, so that no leakage can occur on the sealing seat. Any leakage that may occur is led out through the guide of the valve sleeve via a return line. It is important to avoid leaking into the high pressure area. The leakage described here occurs between the guide the valve body and the valve sleeve in the return. The return flow flows due to the pressure conditions through a laterally mounted hole upwards in the direction of a return.

Die Ventilhülse, an deren Oberseite die Ankerplatte ausgebildet ist, ist außen, oben und unten vom Systemdruck, d.h. dem im Hochdruckspeicherkörper herrschenden Druck, umgeben. Sie ist daher im Hinblick auf ihre axiale Bewegung druckausgeglichen und damit bezüglich des im Hochdruckspeicherkörper (Common-Rail) herrschenden Systemdrucks kraftausgeglichen. Zum Öffnen der Ventilhülse muss lediglich die Federkraft mittels eines Magnetaktors überwunden werden. Die zum Öffnen benötigte Kraft ist unabhängig vom im Hochdruckspeicherkörper herrschenden Systemdruck (der auch als Raildruck bezeichnet wird) und damit über den gesamten Druckbereich, der im Hochdruckspeicherkörper auftritt, konstant. Zum Öffnen der Einspritzöffnungen am brennraumseitigen Ende des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors wird die Ventilhülse, die gleichzeitig den Magnetanker darstellt, durch den Magnetaktor nach oben gezogen. Unter Systemdruck stehender Kraftstoff fließt nun von außen zu der mindestens einen Einspritzöffnung am brennraumseitigen Ende des Kraftstoffinjektors. Die Einspritzöffnungen können zum Beispiel am brennraumseitigen Ende in der Wand des Kraftstoffinjektors ausgeführt sein.The valve sleeve, at the top of which the anchor plate is formed, is external, top and bottom of the system pressure, i. surrounded by the pressure prevailing in the high-pressure accumulator body. It is therefore pressure-balanced with respect to its axial movement and thus balanced with respect to the pressure prevailing in the high pressure reservoir body (common rail) system pressure. To open the valve sleeve, only the spring force must be overcome by means of a magnetic actuator. The force required for opening is independent of the pressure prevailing in the high-pressure accumulator body system pressure (which is also referred to as rail pressure) and thus over the entire pressure range that occurs in the high-pressure accumulator body, constant. To open the injection openings at the combustion chamber end of the inventively proposed fuel injector, the valve sleeve, which also represents the armature, pulled by the magnetic actuator upwards. Under system pressure fuel now flows from the outside to the at least one injection port at the combustion chamber end of the fuel injector. The injection openings may be embodied, for example, at the combustion chamber end in the wall of the fuel injector.

Zum Schließen des Ventilstückes und zum Beenden der Einspritzung von Kraftstoff in den Brennraum der Verbrennungskraftmaschine wird die Bestromung des Magnetaktors unterbrochen. Die Ventilhülse wird durch die auf sie wirkende Federkraft wieder nach unten in ihren Dichtsitz am Ventilstück gedrückt, so dass die Zufuhr von unter Systemdruck stehendem Kraftstoff zu der mindestens einen am brennraumseitigen Ende des Kraftstoffinjektors ausgeführten Einspritzöffnung unterbrochen wird.To close the valve piece and to terminate the injection of fuel into the combustion chamber of the internal combustion engine, the energization of the magnetic actuator is interrupted. The valve sleeve is urged back down into its sealing seat on the valve member by the spring force acting on it so that supply of system pressurized fuel to the at least one injection port formed at the combustion chamber end of the fuel injector is discontinued.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Anhand der Zeichnungen wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawings, the invention will be described in more detail below.

Es zeigt:

Figur 1
einen Schnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor mit direkt betätigter Ventilhülse und
Figur 2
eine Darstellung der Anbindung einer Leckagebohrung am Ventilstück.
It shows:
FIG. 1
a section through the inventively proposed fuel injector with directly actuated valve sleeve and
FIG. 2
a representation of the connection of a leakage hole on the valve piece.

Ausfiihrungsformenembodiments

Der Darstellung gemäß Figur 1 ist ein Längsschnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor mit direkt betätigter Ventilhülse zu entnehmen.The representation according to FIG. 1 is a longitudinal section through the inventively proposed fuel injector with directly actuated valve sleeve refer.

Ein Kraftstoffinjektor 10 gemäß der Darstellung in Figur 1 umfasst einen Injektorkörper 12, der in der Darstellung gemäß Figur 1 symmetrisch zu einer Injektorachse 14 geführt ist. An einer Hochdruckzuleitung 16 steht unter Systemdruck anstehender Kraftstoff an. Unter Systemdruck ist im vorliegenden Falle das Druckniveau bezeichnet, welches innerhalb eines in der Darstellung gemäß Figur 1 nicht wiedergegebenen Hochdruckspeicherkörpers (Common-Rail) herrscht. Dieses Druckniveau ist in der Darstellung gemäß Figur 1 durch pRail angedeutet. Der Kraftstoff, der am Hochdruckanschluss 16 des Injektorkörpers 12 ansteht, strömt in das Innere des Injektorkörpers 12 ein und beaufschlagt dieses mit Kraftstoff.A fuel injector 10 as shown in FIG FIG. 1 comprises an injector body 12, which in the illustration according to FIG. 1 is guided symmetrically to a Injektorachse 14. At a high pressure supply line 16 is under system pressure pending fuel. Under system pressure in the present case, the pressure level is designated, which within a in the illustration according to FIG. 1 unplayed high-pressure accumulator body (common rail) prevails. This pressure level is in the illustration according to FIG. 1 indicated by p Rail . The fuel, which is present at the high-pressure port 16 of the injector body 12, flows into the interior of the injector body 12 and supplies it with fuel.

Im Inneren des Injektorkörpers 12 befindet sich ein Ventilstück 20, welches am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 fixiert ist. Das Ventilstück 20 umfasst eine sich koaxial zur Injektorachse 14 erstreckende Leckagebohrung 22. Die Leckagebohrung 22 hat keine direkte Verbindung zu der Versorgungsleitung 26 bzw. 28. Durch die Zulaufbohrung 28 bzw. die Querbohrung 26 fließt der Kraftstoff während der Einspritzung. Die Leckagebohrung 22 soll Leckage aus dem Sackloch, die durch die untere Führung des Ventilstücks mit der Hülse strömt, und die Leckage aus dem Hochdruckbereich durch die Führung oberhalb der Querbohrung 26 in den Rücklauf gelangt, abführen (??). Das Ventilstück 20 ist mit Hilfe einer Einstellscheibe 40 im Injektorkörper 12 verbaut und bildet am brennraumseitigen Ende eine Abdichtung 32, unterhalb der sich ein sacklochförmig konfigurierter Hohlraum erstreckt. Von diesem erstrecken sich, wie in der Darstellung gemäß Figur 1 wiedergegeben, zumindest zwei Einspritzöffnungen 30, über welche Kraftstoff in den in Figur 1 nicht dargestellten Brennraum einer Verbrennungskraftmaschine eingespritzt werden kann.Inside the injector body 12 is a valve piece 20 which is fixed to the combustion chamber end of the injector body 12 of the fuel injector 10. The valve piece 20 comprises a leakage bore 22 extending coaxially with the injector axis 14. The leakage bore 22 has no direct connection to the supply line 26 or 28. The fuel flows during the injection through the inlet bore 28 or the transverse bore 26. The leakage bore 22 is intended to remove leakage from the blind hole, which flows through the lower guide of the valve piece with the sleeve, and the leakage from the high-pressure region passes through the guide above the transverse bore 26 into the return line (FIG. The valve piece 20 is installed with the aid of a dial 40 in the injector 12 and forms at the combustion chamber end a seal 32, below which extends a blind hole configured cavity. From this extend, as shown in the illustration FIG. 1 reproduced, at least two injection openings 30, via which fuel in the in FIG. 1 not shown combustion chamber of an internal combustion engine can be injected.

Aus der Schnittdarstellung gemäß Figur 1 geht überdies hervor, dass unterhalb der Einstellscheibe 40 eine weitere Einstellscheibe 46 aufgenommen ist. Diese weitere Einstellscheibe 46 dient zur Einstellung der Federkraft einer Schließfeder 44. Diese Schließfeder 44 umgibt einen Magnetaktor 38. Der Magnetaktor 38 ist im Inneren des Injektorkörpers 12 aufgenommen und von dem unter Systemdruck pRail stehenden Kraftstoff umgeben. Der Magnetaktor 38 umschließt des Weiteren das Ventilstück 20, das sich koaxial zur Injektorachse 14 durch den Injektorkörper 12 des Kraftstoffinjektors 10 erstreckt.From the sectional view according to FIG. 1 also shows that below the dial 40, a further dial 46 is added. This further shim 46 serves to adjust the spring force of a closing spring 44. This closing spring 44 surrounds a magnetic actuator 38. The magnetic actuator 38 is received in the interior of the injector body 12 and surrounded by the fuel under system pressure p rail . The solenoid actuator 38 further encloses the valve member 20 which extends coaxially with the injector axis 14 through the injector body 12 of the fuel injector 10.

Der Magnetaktor 38 wirkt auf eine Ankerplatte 36, die an der oberen Planseite der axial im Injektorkörper 12 beweglichen Ventilhülse 42 ausgebildet ist. Auch die Ventilhülse 42 ist im Inneren des Injektorkörpers 12 von dem unter Systemdruck stehenden Kraftstoff allseits umschlossen, d.h. druckausgeglichen.The magnetic actuator 38 acts on an armature plate 36, which is formed on the upper plan side of the axially movable in the injector body 12 valve sleeve 42. The valve sleeve 42 is also enclosed on the inside of the injector body 12 by the system pressure fuel on all sides, i. pressure-balanced.

Die Einstellscheibe 40, die weitere Einstellscheibe 46 zur Einstellung der auf die Schließfeder 44 wirkenden Kraft sind von einer Einstellhülse 48 abgestützt, die in das Innere des Injektorkörpers 12, die Ventilhülse 42 umschließend, angeordnet ist.The adjusting washer 40, the further adjusting washer 46 for adjusting the force acting on the closing spring 44 are supported by an adjusting sleeve 48 which is arranged in the interior of the injector body 12, the valve sleeve 42 enclosing.

Wie aus der Schnittdarstellung gemäß Figur 1 überdies hervorgeht, bildet die Ventilhülse 42, die das Ventilstück 20 umschließt, am unteren Ende einen Dichtsitz 24, der zum Beispiel als Kegelsitz ausgebildet ist. Aus der Darstellung gemäß Figur 1 geht hervor, dass auch am Dichtsitz 24, der in Figur 1 geschlossen dargestellt ist, unter Hochdruck stehender Kraftstoff von außen ansteht.As from the sectional view according to FIG. 1 In addition, it can be seen that the valve sleeve 42, which surrounds the valve member 20 forms at the lower end a sealing seat 24, which is formed for example as a conical seat. From the illustration according to FIG. 1 shows that even at the sealing seat 24, the in FIG. 1 is shown closed, standing under high pressure fuel from the outside.

Bei einer Bestromung des Magnetaktors 38 bewegt sich die Ankerplatte 36, die an der Ventilhülse 42 aufgenommen ist, entgegen der Wirkung der Schließfeder 44 nach oben. Dadurch wird der Dichtsitz 24 oberhalb des verbreiterten Bereiches des Ventilstücks 20 geöffnet, so dass von der Außenseite in Bezug auf den Dichtsitz 24 gesehen, unter Systemdruck PRail stehender Kraftstoff 18 über die Querbohrung 26 in die Zulaufbohrung 28 innerhalb des Ventilstücks 20 in das Sackloch 34 einströmt. Der im Sackloch 34 unter Systemdruck stehende Kraftstoff wird dann über die in Figur 1 dargestellten zwei Einspritzöffnungen 30 in den hier nicht näher dargestellten Brennraum der Verbrennungskraftmaschine eingespritzt.When the magnetic actuator 38 is energized, the armature plate 36, which is received on the valve sleeve 42, moves upward against the action of the closing spring 44. Characterized the sealing seat 24 is opened above the widened portion of the valve member 20 so that seen from the outside with respect to the sealing seat 24, under system pressure P rail standing fuel 18 via the transverse bore 26 into the inlet bore 28 within the valve member 20 in the blind hole 34th flows. The standing in the blind hole 34 under system pressure fuel is then on the in FIG. 1 shown injected two injection openings 30 in the combustion chamber, not shown here, the internal combustion engine.

Das Sackloch 34 wird nur über die zentrisch, d.h. koaxial zur Injektorachse 14 verlaufende Zulaufbohrung 28 mit unter Systemdruck pRail stehendem Kraftstoff beaufschlagt. Die Außenseite, d.h. die Innenseite des Ventilkörpers 12 und die Außenseite des Ventilstücks 20, bilden die Abdichtung 32, so dass das Sackloch 34 am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 gegen den unter Systemdruck stehenden Kraftstoff abgedichtet ist.The blind hole 34 is acted upon only via the concentric, ie coaxially to the injector 14 extending inlet bore 28 under system pressure p rail standing fuel. The outside, ie the inside of the valve body 12 and the outside of the valve piece 20, form the seal 32, so that the blind hole 34 is sealed at the combustion chamber end of the injector body 12 of the fuel injector 10 against the under system pressure fuel.

Bei dem im Längsschnitt gemäß Figur 1 dargestellten, direkt betätigten Kraftstoffinjektor 10 bringt der Magnetaktor 38 nur die Kraft auf, die zur Betätigung der druckausgeglichenen Ventilhülse 42 erforderlich ist. Beim Bestromen des Magnetankers 38 zieht dieser die Ankerplatte 36 der Ventilhülse 42 gegen die Kraft der Schließfeder 44 an. Der Magnetaktor 38 hat demnach nur die Schließkraft, d.h. die Federkraft, die die Schließfeder 44 aufbringt, zu überwinden und kann dementsprechend ausgelegt werden.In the longitudinal section according to FIG. 1 shown, directly actuated fuel injector 10, the solenoid actuator 38 applies only the force required to actuate the pressure balanced valve sleeve 42. When the magnet armature 38 is energized, it pulls the armature plate 36 of the valve sleeve 42 against the force of the closing spring 44. Accordingly, the magnetic actuator 38 has only the closing force, ie the spring force which applies the closing spring 44, to overcome and can be designed accordingly.

Der erfindungsgemäß vorgeschlagene, direkt betätigte Kraftstoffinjektor 10 ist darüber hinaus wesentlich einfacher aufgebaut im Vergleich zu bisher aus dem Stand der Technik bekannten Kraftstoffinjektoren, deren Betätigung indirekt über die Druckentlastung bzw. Druckbeaufschlagung eines Steuerraums erfolgt. Der erfindungsgemäß vorgeschlagene Kraftstoffinjektor 10 verwirklicht einen steuermengenfreien Kraftstoffinjektor, bei dem keine Rückführung eines aus einem Steuerraum abgesteuerten Volumens in Richtung des Niederdruckbereiches erforderlich ist. Dies bedingt einen im Vergleich zu bisherigen Lösungen verringerten Systemaufwand sowie eine kleiner zu dimensionierende Förderleistung eines Förderaggregates. Des Weiteren können Ablauf- und Zulaufdrossel entfallen, ebenso wie der Steuerraum sowie die Druckstange, die bei im Allgemeinen nadelförmig ausgebildeten Einspritzventilgliedern bisher eingesetzt wurde. Der erfindungsgemäß vorgeschlagene Kraftstoffinjektor 10 zeichnet sich durch eine kürzere Baulänge aus im Vergleich zu aus dem Stand der Technik bekannten Kraftstoffinjektoren.The inventively proposed, directly operated fuel injector 10 is also constructed much simpler compared to previously known from the prior art fuel injectors whose operation is done indirectly via the pressure relief or pressurization of a control room. The inventively proposed fuel injector 10 realizes a tax-free fuel injector, in which no return of a controlled from a control room volume in the direction of the low pressure region is required. This requires a reduced compared to previous solutions system overhead and a smaller dimensioning capacity of a delivery unit. Furthermore, drain and inlet throttle can be omitted, as well as the control chamber and the push rod, which was previously used in generally needle-shaped injection valve members. The inventively proposed fuel injector 10 is characterized by a shorter overall length compared to known from the prior art fuel injectors.

Aus dem Längsschnitt gemäß der Darstellung in Figur 1 geht hervor, dass die Abdichtung 32 des Ventilstücks 20 zur Innenseite des Injektorkörpers 12 über die Einstellscheibe 40 erfolgt. Die untere Planseite der Einstellscheibe 40 wiederum dient als Anlage für eine weitere Einstellscheibe 46. Die Dicke dieser weiteren Einstellscheibe 46 wiederum definiert die Federkraft, die an der Schließfeder 44 eingestellt ist. Beide Einstellscheiben, d.h. die Einstellscheibe 40 zur Fixierung des Ventilstücks 20, als auch die an deren unterer Planseite anliegende weitere Einstellscheibe 46, stützen sich auf einer in den Injektorkörper 12 eingepressten Einstellhülse 48 ab. Das Ventilstück 20 wird unter Ausbildung der Abdichtung 32 derart in den Injektorkörper 12 eingepresst, dass keine Leckage der Abdichtung 32 in das Sackloch 34 und damit von dort über die Einspritzöffnungen 30 in den Brennraum der Verbrennungskraftmaschine gelangen kann.From the longitudinal section as shown in FIG. 1 shows that the seal 32 of the valve member 20 to the inside of the injector body 12 via the shim 40 takes place. The lower plan side of the dial 40 in turn serves as an abutment for a further dial 46. The thickness of this further dial 46 in turn defines the spring force which is set on the closing spring 44. Both shims, ie the shim 40 for fixing the valve member 20, as well as at the lower plan side fitting further shim 46, based on a pressed-in the injector 12 adjusting sleeve 48 from. The valve member 20 is pressed with the formation of the seal 32 in such a way in the injector body 12 that no leakage of the seal 32 in the blind hole 34 and thus can pass from there via the injection ports 30 into the combustion chamber of the internal combustion engine.

Der Darstellung gemäß Figur 2 ist in vergrößertem Maßstab die Anbindung der Leckagebohrung 22 zu entnehmen.The representation according to FIG. 2 is to refer to the connection of the leakage hole 22 in an enlarged scale.

Die Darstellung gemäß Figur 2 stellt den in Figur 1 eingekreisten Bereich in vergrößertem Maßstab dar. Über die das Ventilstück koaxial zur Injektorachse 14 durchziehende Leckagebohrung 22, in der Rücklaufdruck pRL herrscht, strömt Führungsleckage, die sich zwischen einem Innenumfang 58 der Ventilhülse 42 und einer Mantelfläche 56 des Ventilstücks 20 einstellt, über eine Querbohrung in die Leckagebohrung 22 ab. Damit wird verhindert, dass über die Führung Leckagemenge nach unten in Richtung des brennraumseitigen Endes gelangen kann. Die Rücklaufmenge fließt aufgrund geeigneter Druckverhältnisse und eventuell unter Erzeugung eines Unterdruckes in der Leckagebohrung 22 durch die in Figur 2 dargestellten Querbohrungen nach oben in Richtung des Rücklaufes. Die Rücklaufströmung stellt sich ein, sobald ein Leckagedruck pLeckage als Funktion des Systemdruckes pRail zuzüglich eines Brennraumdruckes pZylinder größer ist, als das im Rücklauf herrschende Druckniveau pRL. Sobald diese Bedingung erfüllt ist, wird die Führungsleckage zwischen der Mantelfläche 56 des Ventilstücks 20 und der Innenumfangsfläche 58 der Ventilhülse 42 über die in Figur 2 dargestellte Querbohrung in die Leckagebohrung 22 abgeführt, in der Rücklaufdruckniveau pRL herrscht.The representation according to FIG. 2 puts the in FIG. 1 Circled area on an enlarged scale. About the valve piece coaxial with the injector 14 passing through leakage bore 22, prevails in the return pressure p RL , guide leakage flowing between an inner periphery 58 of the valve sleeve 42 and a lateral surface 56 of the valve member 20 flows through a transverse bore in the leakage hole 22 from. This prevents leakage via the guide downwards in the direction of the combustion chamber end can reach. The return flow flows due to suitable pressure conditions and possibly to generate a negative pressure in the leakage bore 22 by the in FIG. 2 illustrated transverse holes upwards in the direction of the return. The return flow occurs as soon as a leakage pressure p leakage as a function of the system pressure p rail plus a combustion chamber pressure p cylinder is greater than the pressure prevailing in the return pressure level p RL . Once this condition is met, the guide leakage between the lateral surface 56 of the valve member 20 and the inner peripheral surface 58 of the valve sleeve 42 on the in FIG. 2 shown transverse bore discharged into the leakage bore 22, in the return pressure level p RL prevails.

Wie den Darstellungen gemäß der Figuren 1 und 2 entnommen werden kann, ist die Ventilhülse 42 außen an ihrer Mantelfläche am oberen und am unteren Ende von Systemdruck pRail umgeben. Dies bedeutet, dass die Ventilhülse 42 hinsichtlich ihrer axialen Bewegung druckausgeglichen und in Bezug auf den Systemdruck pRail kraftausgeglichen ist. Zum Öffnen der Ventilhülse 42 muss lediglich die Federkraft, die durch die Schließfeder 44 aufgebracht wird, mittels des Magnetankers 38 überwunden werden. Die dafür benötigte Magnetkraft ist unabhängig vom Systemdruck pRail und damit über den gesamten Druckbereich des Systemdrucks pRail konstant. Zum Öffnen der Ventilhülse 42 wird diese bzw. deren Ankerplatte 36 durch den Magnetaktor 38 nach oben angezogen. Der unter Systemdruck pRail am Ventilsitz 42 anstehende Kraftstoff strömt über den geöffneten Ventilsitz 24 in Richtung des Sacklochs 34 und von dort zu den Einspritzöffnungen 30.As the representations according to Figures 1 and 2 can be removed, the valve sleeve 42 is surrounded outside on its lateral surface at the top and at the bottom of system pressure p rail . This means that the valve sleeve 42 is pressure-balanced with respect to its axial movement and is force-balanced with respect to the system pressure p Rail . To open the valve sleeve 42, only the spring force, which is applied by the closing spring 44, must be overcome by means of the magnet armature 38. The required magnetic force is independent of the system pressure p rail and thus constant over the entire pressure range of the system pressure p rail . To open the valve sleeve 42, this or its armature plate 36 is attracted by the magnetic actuator 38 upwards. The fuel which is present at the valve seat 42 under system pressure p rail flows via the open valve seat 24 in the direction of the blind hole 34 and from there to the injection openings 30.

Zum Schließen der Kraftstoffzufuhr in den Brennraum der Verbrennungskraftmaschine wird die Bestromung des Magnetaktors 38 unterbrochen und die kraftausgeglichene Ventilhülse 42 durch die Wirkung der Federkraft der Schließfeder 44 wieder nach unten in den Ventilsitz 24 gedrückt. Damit ist die Druckbeaufschlagung des sacklochartigen Hohlraums 34 am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 unterbrochen und die Einspritzung beendet.To close the fuel supply in the combustion chamber of the internal combustion engine, the energization of the magnetic actuator 38 is interrupted and the force-balanced valve sleeve 42 is pressed by the action of the spring force of the closing spring 44 back down into the valve seat 24. Thus, the pressurization of the blind hole-like cavity 34 is interrupted at the combustion chamber end of the injector body 12 of the fuel injector 10 and the injection is completed.

Claims (10)

Kraftstoffinjektor (10) mit einem Injektorkörper (12), in dem ein Ventilstück (20) befestigt ist, an dem eine Ventilhülse (42) geführt ist, die an einem Ende (36) einem Magnetaktor (38) zuweist und am anderen Ende einen Ventilsitz (24) begrenzt, dadurch gekennzeichnet, dass die Ventilhülse (42) durch den Magnetaktor (38) direkt betätigt ist.A fuel injector (10) having an injector body (12) in which is mounted a valve member (20) having a valve sleeve (42) attached to a solenoid actuator (38) at one end (36) and a valve seat at the other end (24) limited, characterized in that the valve sleeve (42) is actuated directly by the magnetic actuator (38). Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass das dem Magnetaktor (38) zuweisende Ende (36) der Ventilhülse (42) als Ankerplatte ausgeführt ist.Fuel injector according to claim 1, characterized in that the magnetic actuator (38) facing end (36) of the valve sleeve (42) is designed as an anchor plate. Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass das Ventilstück (20) mittels einer Einstellscheibe (40) an dem Injektorkörper (12) angestellt ist.Fuel injector according to claim 1, characterized in that the valve piece (20) by means of a shim (40) on the injector body (12) is employed. Kraftstoffinjektor gemäß Anspruch 3, dadurch gekennzeichnet, dass das Ventilstück (20) mit dem Injektorkörper (12) eine Abdichtung (32) eines mit unter Systemdruck pRail stehenden Kraftstoff beaufschlagbaren Hohlraumes (34) bildet.Fuel injector according to claim 3, characterized in that the valve piece (20) with the injector body (12) forms a seal (32) of a standing under system pressure p rail fuel cavity (34). Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass das dem Magnetaktor (38) zuweisende Ende (36) der Ventilhülse (42) durch eine Schließfeder (44) beaufschlagt ist, deren Federkraft durch eine weitere Einstellscheibe (46) einstellbar ist.Fuel injector according to claim 1, characterized in that the magnetic actuator (38) assigning end (36) of the valve sleeve (42) is acted upon by a closing spring (44) whose spring force is adjustable by a further adjusting disc (46). Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass die Ventilhülse (42) allseits von unter Systemdruck pRail stehendem Kraftstoff umgeben ist und damit im gesamten Raildruckbereich druckausgeglichen ist und keine durch Druckdifferenzen resultierende Kräfte auftreten.Fuel injector according to claim 1, characterized in that the valve sleeve (42) is surrounded on all sides by standing under system pressure p rail fuel and thus is pressure balanced throughout the rail pressure range and no forces resulting from pressure differences occur. Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass das Ventilstück (20) eine Querbohrung (26) aufweist, die oberhalb des Ventilsitzes (24) mit einer Zulaufbohrung (28) im Ventilstück (20) verbunden ist.Fuel injector according to claim 1, characterized in that the valve piece (20) has a transverse bore (26) which is connected above the valve seat (24) with an inlet bore (28) in the valve piece (20). Kraftstoffinjektor gemäß Anspruch 1, dadurch gekennzeichnet, dass eine Leckagebohrung (22) im Ventilstück (20) Leckage der Führung zwischen Ventilhülse (42) und Ventilstück (20) abführt, wobei ein Leckagedruck pLeckage als Funktion des Systemdrucks pRail und des Brennraumdrucks pZylinder einen Rücklaufdruck pRL übersteigt.Fuel injector according to claim 1, characterized in that a leakage bore (22) in the valve piece (20) leakage of the guide between the valve sleeve (42) and valve piece (20) dissipates, wherein a leakage pressure p leakage as a function of the system pressure p rail and the combustion chamber pressure p cylinder exceeds a return pressure p RL . Kraftstoffinjektor gemäß der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Einstellscheibe (40) und die weitere Einstellscheibe (46) zur Einstellung der Federkraft der Schließfeder (44) durch eine Einstellhülse (48) im Injektorkörper (12) abgestützt sind.Fuel injector according to the preceding claims, characterized in that the adjusting disc (40) and the further adjusting disc (46) for adjusting the spring force the closing spring (44) are supported by an adjusting sleeve (48) in the injector body (12). Kraftstoffinjektor gemäß einem oder mehrerer der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Federkraft der Schließfeder (44) unabhängig vom Systemdruck pRail sowie über den gesamten Systemdruckbereich konstant ist.Fuel injector according to one or more of the preceding claims, characterized in that the spring force of the closing spring (44) is independent of the system pressure p rail and over the entire system pressure range constant.
EP09100250A 2008-06-24 2009-04-24 Directly actuated fuel injector Not-in-force EP2138709B1 (en)

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Publication number Priority date Publication date Assignee Title
EP2395227A3 (en) * 2010-06-14 2015-04-22 Robert Bosch GmbH Injection valve
SE1951116A1 (en) * 2019-10-01 2021-04-02 Scania Cv Ab Fuel injector arrangement, high pressure injection system comprising the injector arrangement, fuel system comprising the high pressure injection system, vehicle comprising the fuel system, and a meth

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US5645226A (en) * 1995-02-13 1997-07-08 Siemens Automotive Corporation Solenoid motion initiator
DE19754112A1 (en) * 1996-12-06 1998-06-10 Hyundai Motor Co Ltd Automotive fuel injection system for diesel engines
DE10111293A1 (en) * 2001-03-09 2002-09-19 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE102006050810A1 (en) 2006-10-27 2008-04-30 Robert Bosch Gmbh Fuel injector for internal combustion engines, comprises control valve with stationary valve pin which has internal relief duct that extends from control chamber to annular groove of valve pin

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Publication number Priority date Publication date Assignee Title
US5645226A (en) * 1995-02-13 1997-07-08 Siemens Automotive Corporation Solenoid motion initiator
DE19754112A1 (en) * 1996-12-06 1998-06-10 Hyundai Motor Co Ltd Automotive fuel injection system for diesel engines
DE10111293A1 (en) * 2001-03-09 2002-09-19 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE102006050810A1 (en) 2006-10-27 2008-04-30 Robert Bosch Gmbh Fuel injector for internal combustion engines, comprises control valve with stationary valve pin which has internal relief duct that extends from control chamber to annular groove of valve pin

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2395227A3 (en) * 2010-06-14 2015-04-22 Robert Bosch GmbH Injection valve
SE1951116A1 (en) * 2019-10-01 2021-04-02 Scania Cv Ab Fuel injector arrangement, high pressure injection system comprising the injector arrangement, fuel system comprising the high pressure injection system, vehicle comprising the fuel system, and a meth
SE545024C2 (en) * 2019-10-01 2023-02-28 Scania Cv Ab Fuel injector arrangement for an internal combustion engine and method for operating said arrangement

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EP2138709B1 (en) 2011-10-26
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