EP1373710B1 - Fuel-injection valve for internal combustion engines - Google Patents

Fuel-injection valve for internal combustion engines Download PDF

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Publication number
EP1373710B1
EP1373710B1 EP02727267A EP02727267A EP1373710B1 EP 1373710 B1 EP1373710 B1 EP 1373710B1 EP 02727267 A EP02727267 A EP 02727267A EP 02727267 A EP02727267 A EP 02727267A EP 1373710 B1 EP1373710 B1 EP 1373710B1
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EP
European Patent Office
Prior art keywords
bore
needle
inner needle
nozzle needle
combustion chamber
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.)
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EP02727267A
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German (de)
French (fr)
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EP1373710A1 (en
Inventor
Gerhard Mack
Taner Narin
Holger Rapp
Ulrich Kunzi
Ralf Heinecke
Wilhelm Christ
Friedrich Boecking
Wolfgang Fleiner
Manfred Fink
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • 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
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known for example from the published patent application DE 43 03 813 A1.
  • a fuel injection valve has a valve body in which a bore is formed, at the brennraum workedem end of a valve seat surface and at least one injection port are formed.
  • a piston-shaped nozzle needle is arranged longitudinally displaceably, which is sealingly guided in a bore in the bore facing away from the combustion chamber.
  • the nozzle needle tapers to the combustion chamber to form a pressure shoulder and merges at its combustion chamber end in a valve sealing surface, which cooperates with the valve seat surface and so by longitudinal movement of the nozzle needle, the at least one injection opening up and head.
  • a pressure chamber is formed by a radial extension of the bore, which, surrounding the nozzle needle, continues as an annular channel to the valve seat surface.
  • the nozzle needle is acted upon by a closing force which acts in the direction of the valve seat.
  • a hydraulic force against this closing force acts on the fuel pressure in the pressure chamber and the associated hydraulic force on the pressure shoulder.
  • a plurality of injection openings are generally distributed uniformly over the circumference of the valve body.
  • the nozzle needle and thus the substantially conical valve sealing surface in the opening stroke of the nozzle needle remain exactly centric to the bore and thus the valve sealing surface, so that a uniform fuel flow from the pressure chamber to the injection ports take place can.
  • the nozzle needle is now guided in the bore at the region facing away from the combustion chamber, a very long free length of the nozzle needle results after lifting off the valve sealing surface from the valve seat surface between the guided section and the valve sealing surface, so that it is easy for the nozzle needle to become disaligned in the bore can come and thus corresponding to an uneven flow of fuel to the injection ports.
  • a desalination has great influence on the injection pattern and thus on the quality of the combustion.
  • a fuel injection valve which has a nozzle needle.
  • the nozzle needle is in the form of a sleeve and guided on a stationary insert body, which ensures an optimum position of the nozzle needle with respect to the valve seat.
  • a fuel injection valve which comprises a nozzle needle for controlling at least one injection opening.
  • the nozzle needle has at its end facing the valve seat on a blind bore in which a guide pin is slidably mounted, wherein the guide pin is immersed at its end facing away from the nozzle needle in a recess of the valve body.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that the nozzle needle is guided by a reference to the valve body fixedly fixed inner needle, so that an exact centering is ensured in the bore over the entire stroke range of the nozzle needle.
  • the nozzle needle has a central longitudinal bore, in which the inner needle is arranged, which is fixed relative to the valve body.
  • the nozzle needle is guided in particular in its valve seat facing end portion on the inner needle, so that there can be no dislocation of the nozzle needle in the region of the valve seat.
  • the inner needle has at least two radially outwardly projecting fixing webs, which bear against the inner wall of the bore and thus caulk the inner needle in the bore.
  • the inner needle has an undercut in its central region, so that the nozzle needle is guided only in a combustion chamber facing end portion and a combustion chamber facing away from end portion on the inner needle.
  • FIG. 1 shows a longitudinal section through a fuel injection valve.
  • a valve holding body 1 is braced by means of a clamping nut 4 in the axial direction against a valve body 3.
  • a bore 7 is formed, at the combustion chamber end of which a valve seat surface 10 is formed which is substantially conical and in which at least one injection opening 9 is arranged.
  • a nozzle needle 12 is arranged, which is piston-shaped and at its combustion chamber end has a substantially frusto-conical valve sealing surface 17 which cooperates with the valve seat 10, so that upon contact of the valve sealing surface 17 on the valve seat 10, the injection openings 9 closed become.
  • the nozzle needle 12 is sealingly guided in a bore away from combustion chamber in the bore 7, wherein the sealingly guided portion of the nozzle needle 12 has a larger diameter than the combustion chamber facing portion of the nozzle needle 12, so that at the transition, a pressure shoulder 22 is formed.
  • a pressure chamber 16 is formed at the level of the pressure shoulder 22, which continues to the combustion chamber to as the nozzle needle 12 surrounding annular channel to the valve seat surface 10.
  • the pressure chamber 16 is connected via a valve body 3 and in the valve holding body 1 extending inlet channel 30 with a high-pressure port 49, can be promoted via the fuel from a high-pressure fuel source, not shown in the drawing into the pressure chamber.
  • FIG. 2 an enlarged view of FIG.
  • FIG. 3 shows a cross section of FIG. 2 along the line III-III.
  • the nozzle needle 12 has a central longitudinal bore 19, which serves here as a guide bore and in which an inner needle 14 is arranged.
  • the inner needle 14 has at its combustion chamber end facing a contact surface 11 which is conical and rests against the likewise conical valve seat surface 10. Due to the conical shape of both surfaces, the contact surface 11 is centrally fixed, so that the combustion chamber facing side of the inner needle 14 is aligned exactly in the direction of the longitudinal axis 6 of the bore 7.
  • the inner needle 14 has three fixing webs 20, which extend in the radial direction from the inner needle 14 to the outside, where they are caulked non-positively in the bore 7.
  • the three fixing webs 20 are distributed uniformly over the circumference of the inner needle 14, so that the inner needle 14 is fixed by the Fixierstege 20 exactly in the direction of the longitudinal axis 6 of the bore 7 fixed in the valve body 3. It can also be provided to form more or less than three fixing webs 20 on the nozzle needle 12, which are then preferably also distributed uniformly over the circumference of the inner needle 14.
  • the nozzle needle 12 has corresponding recesses 15, which receive the fixing webs 20 and thus ensure the longitudinal displacement of the nozzle needle 12 on the inner needle 14.
  • the nozzle needle 12 is located at its end facing away from the combustion chamber on a cylindrical pressure piece 37, which is arranged in a formed in the valve holding body 1 spring chamber 32. Between the combustion chamber facing away from the end of the spring chamber 32 and the pressure piece 37, a closing spring 34 is arranged under pressure bias, on the pressure piece 37 on the nozzle needle 12 acts and so the nozzle needle 12 in the closed position - that is, when the valve sealing surface 17 abuts the valve seat surface 10 - presses. Coaxially to the bore 7, a piston bore 38 is formed in the valve holding body 1, which opens into the spring chamber 32.
  • a pressure piston 39 is arranged longitudinally displaceable, which protrudes at its end facing the combustion chamber into the spring chamber 32 and there rests on the pressure piece 37 and limited with its combustion chamber facing away face 41 a control chamber 40.
  • the opening stroke of the nozzle needle 12 is stopped by the abutment of the pressure piston 39 at the combustion chamber end facing away from the piston bore 38.
  • the control chamber 40 is connected via an inlet throttle 42 to the inlet channel 30 and via an outlet throttle 43 with a formed in the valve holding body 1 leakage oil space 48.
  • This leakage oil chamber 48 is connected to a drain oil, not shown in the drawing and thus constantly depressurized.
  • a magnet armature 45 is arranged, on whose the control chamber 40 facing the end of a sealing ball 47 is arranged.
  • the armature 45 is acted upon by a spring 53 in the direction of the control chamber 40, so that the sealing ball 47 is pressed onto the outlet throttle 43 and the outlet throttle 43 closes.
  • a spring 53 surrounding the electromagnet 51 is arranged, which exerts an attractive force to the armature 45 with appropriate energization, so that it is pulled against the force of the spring 53 in the direction of the electromagnet 51, so that the sealing ball 47, the outlet throttle 43 releases. If the electromagnet 51 is not energized, then the spring 53 pushes the magnet armature 45 and thus the sealing ball 47 back onto the outlet throttle 43 and thus closes off the control chamber 40 against the leakage oil chamber 48.
  • the operation of the fuel injection valve is as follows: Via the high pressure port 49 fuel is constantly passed under high pressure into the pressure chamber 16, so that in the pressure chamber 16 a constant predetermined high pressure fuel prevails. This results in a hydraulic force on the pressure shoulder 22 of the nozzle needle 12, which is directed in the opening direction of the nozzle needle 12. If no injection takes place, then the electromagnet 51 is not energized and the outlet throttle 43 is thus closed by the sealing ball 47. As a result, prevails in the control chamber 40 due to the inlet throttle 42, the same pressure as in the inlet channel 30 or in the pressure chamber 16 so that a corresponding hydraulic force on the combustion chamber facing away from face 41 of the pressure piston 39 results.
  • the pressure piston 39 Since the pressure piston 39 has a larger diameter, and thus a larger hydraulically effective area than the nozzle needle 12, the force exerted by the pressure piston 39 via the pressure piece 37 on the nozzle needle 12 force prevails, so that the nozzle needle 12 remains in the closed position and the injection openings 9 closes , If an injection takes place, then the electromagnet 51 is energized and the magnet armature 45 moves in the direction of the electromagnet 51. In this way, the sealing ball 47 releases the outlet throttle 43 and the control chamber 40 is connected to the leakage oil chamber 48. As a result, the pressure in the control chamber 40 decreases, so that now the hydraulic force on the pressure shoulder 22 of the nozzle needle 12 outweighs and lifts the nozzle needle from the valve seat surface 10 and the injection openings 9 releases.
  • the closing spring 34 plays only a minor role and is mainly used to keep the nozzle needle 12 in the closed position when the fuel injection system is switched off. If the injection is terminated, the electromagnet 51 is de-energized, and the high fuel pressure of the inlet channel 30 builds up again in the control chamber 40.
  • the inner needle 14 is inserted into the nozzle needle 12 and then both are introduced together into the hole 7.
  • the annular webs 20 of the inner needle 14 are formed so that they must be pressed into the bore 7, so that a stationary fixation of the inner needle 14 takes place in the bore 7 along its longitudinal axis 6.
  • the nozzle needle 12 does not need to be fixed further, since it is arranged uniquely in the bore 7 by the fixation of the inner needle 14.
  • the valve holding body 1 is braced with the pressure piston 39 already arranged therein, the closing spring 34 and the pressure piece 37 by means of the clamping nut 4 against the valve body 3.
  • FIG. 4 shows a further exemplary embodiment of the fuel injection valve according to the invention.
  • the inner needle 14 in this case has no constant outer diameter, but has between a first combustion chamber facing guide portion 114 and a second combustion chamber away from the guide portion 214 an undercut 25, in the region of the inner needle 14 is reduced in outer diameter.
  • the nozzle needle 12 is guided only on the first guide portion 114 and the second guide portion 214, whereby the risk of seizing the nozzle needle 12 is reduced to the inner needle 14, and both the wear and the friction of the nozzle needle 12 are reduced on the inner needle 14 , It can also be provided that the second guide portion 214 is also omitted and the nozzle needle 12 is guided on the inner needle 14 only on the first guide portion 114.
  • the nozzle needle 12 is already sealingly guided in the combustion chamber facing away from the bore 7 on its outer lateral surface, so that a guide of the nozzle needle 12 in this area on the inner needle 14 for stabilization depending on the requirements of the fuel injection valve is not essential.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es beispielsweise aus der Offenlegungsschrift DE 43 03 813 A1 bekannt ist. Ein solches Kraftstoffeinspritzventil weist einen Ventilkörper auf, in dem eine Bohrung ausgebildet ist, an deren brennraumseitigem Ende eine Ventilsitzfläche und wenigstens eine Einspritzöffnung ausgebildet sind. In der Bohrung ist eine kolbenförmige Düsennadel längsverschiebbar angeordnet, die in einem brennraumabgewandten Abschnitt in der Bohrung dichtend geführt ist. Die Düsennadel verjüngt sich dem Brennraum zu unter Bildung einer Druckschulter und geht an ihrem brennraumseitigen Ende in eine Ventildichtfläche über, die mit der Ventilsitzfläche zusammenwirkt und so durch Längsbewegung der Düsennadel die wenigstens eine Einspritzöffnung auf- und zusteuert. Auf Höhe der Druckschulter ist durch eine radiale Erweiterung der Bohrung ein Druckraum ausgebildet, der sich, die Düsennadel umgebend, als Ringkanal bis zur Ventilsitzfläche fortsetzt. An ihrem brennraumabgewandten Ende wird die Düsennadel von einer Schließkraft beaufschlagt, die in Richtung des Ventilsitzes wirkt. Gleichzeitig wirkt auf die Düsennadel eine hydraulische Kraft entgegen dieser Schließkraft, die durch den Kraftstoffdruck im Druckraum und die damit verbundene hydraulische Kraft auf die Druckschulter ausgeübt wird.The invention is based on a fuel injection valve for internal combustion engines, as is known for example from the published patent application DE 43 03 813 A1. Such a fuel injection valve has a valve body in which a bore is formed, at the brennraumseitigem end of a valve seat surface and at least one injection port are formed. In the bore, a piston-shaped nozzle needle is arranged longitudinally displaceably, which is sealingly guided in a bore in the bore facing away from the combustion chamber. The nozzle needle tapers to the combustion chamber to form a pressure shoulder and merges at its combustion chamber end in a valve sealing surface, which cooperates with the valve seat surface and so by longitudinal movement of the nozzle needle, the at least one injection opening up and head. At the level of the pressure shoulder, a pressure chamber is formed by a radial extension of the bore, which, surrounding the nozzle needle, continues as an annular channel to the valve seat surface. At its end facing away from the combustion chamber, the nozzle needle is acted upon by a closing force which acts in the direction of the valve seat. At the same time acts on the nozzle needle, a hydraulic force against this closing force, which is exerted by the fuel pressure in the pressure chamber and the associated hydraulic force on the pressure shoulder.

In der im wesentlichen konischen Ventilsitzfläche sind im allgemeinen mehrere Einspritzöffnungen gleichmäßig über den Umfang des Ventilkörpers verteilt angeordnet. Für eine gleichmäßige Einspritzung durch alle diese Einspritzöffnungen ist es wichtig, daß die Düsennadel und damit auch die im wesentlichen konische Ventildichtfläche bei der Öffnungshubbewegung der Düsennadel genau zentrisch zur Bohrung und damit zur Ventildichtfläche bleiben, so daß ein gleichmäßiger Kraftstoffzufluß aus dem Druckraum zu den Einspritzöffnungen stattfinden kann. Da die Düsennadel nun an dem brennraumabgewandten Abschnitt in der Bohrung geführt ist, ergibt sich nach Abheben der Ventildichtfläche von der Ventilsitzfläche zwischen dem geführten Abschnitt und der Ventildichtfläche eine sehr lange freie Länge der Düsennadel, so daß es leicht zu einer Desachsierung der Düsennadel in der Bohrung kommen kann und damit entsprechend zu einem ungleichmäßigen Zufluß von Kraftstoff zu den Einspritzöffnungen. Gerade zu Beginn der Öffnungshubbewegung bei einem nur sehr kleinen Spalt zwischen der Ventildichtfläche und der Ventilsitzfläche hat eine solche Desachsierung großen Einfluß auf das Einspritzbild und damit auf die Qualität der Verbrennung.In the substantially conical valve seat surface a plurality of injection openings are generally distributed uniformly over the circumference of the valve body. For a uniform injection through all these injection ports, it is important that the nozzle needle and thus the substantially conical valve sealing surface in the opening stroke of the nozzle needle remain exactly centric to the bore and thus the valve sealing surface, so that a uniform fuel flow from the pressure chamber to the injection ports take place can. Since the nozzle needle is now guided in the bore at the region facing away from the combustion chamber, a very long free length of the nozzle needle results after lifting off the valve sealing surface from the valve seat surface between the guided section and the valve sealing surface, so that it is easy for the nozzle needle to become disaligned in the bore can come and thus corresponding to an uneven flow of fuel to the injection ports. Especially at the beginning of the opening stroke movement with only a very small gap between the valve sealing surface and the valve seat surface, such a desalination has great influence on the injection pattern and thus on the quality of the combustion.

Aus der Offenlegungsschrift WO 99/19619 ist darüber hinaus ein Kraftstoffeinspritzventil bekannt, das eine Düsennadel aufweist. Die Düsennadel ist in Form einer Hülse ausgebildet und auf einem ortsfesten Einsatzkörper geführt, der eine optimale Position der Düsennadel bezüglich des Ventilsitzes gewährleistet.From the published patent application WO 99/19619 a fuel injection valve is also known, which has a nozzle needle. The nozzle needle is in the form of a sleeve and guided on a stationary insert body, which ensures an optimum position of the nozzle needle with respect to the valve seat.

Aus der Schrift JP 11-294301 ist außerdem ein Kraftstoffeinspritzventil bekannt, das eine Düsennadel zur Steuerung wenigstens einer Einspritzöffnung umfasst. Die Düsennadel weist an ihrem dem Ventilsitz zugewandten Ende eine Sackbohrung auf, in der ein Führungsstift gleitverschiebbar gelagert ist, wobei der Führungsstift an seinem der Düsennadel abgewandten Ende in eine Ausnehmung des Ventilkörpers eintaucht. Durch Druckbeaufschlagung der der Ventilnadel zugewandten Stirnseite wird der Führungsstift bezüglich des Ventilkörpers ortsfest in der Ausnehmung gehalten.From document JP 11-294301 a fuel injection valve is also known which comprises a nozzle needle for controlling at least one injection opening. The nozzle needle has at its end facing the valve seat on a blind bore in which a guide pin is slidably mounted, wherein the guide pin is immersed at its end facing away from the nozzle needle in a recess of the valve body. By pressurizing the valve needle facing end face of the guide pin is held stationary in the recess with respect to the valve body.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß die Düsennadel durch eine Bezüglich des Ventilkörpers ortsfest fixierte Innennadel geführt ist, so daß eine exakte Zentrierung in der Bohrung über den gesamten Hubbereich der Düsennadel gewährleistet ist. Die Düsennadel weist eine mittige Längsbohrung auf, in der die Innennadel angeordnet ist, die bezüglich des Ventilkörpers fixiert ist. Die Düsennadel ist insbesondere in ihrem ventilsitzzugewandten Endabschnitt auf der Innennadel geführt, so daß sich keine Desachsierung der Düsennadel im Bereich des Ventilsitzes ergeben kann.The fuel injection valve according to the invention with the features of claim 1 has the advantage that the nozzle needle is guided by a reference to the valve body fixedly fixed inner needle, so that an exact centering is ensured in the bore over the entire stroke range of the nozzle needle. The nozzle needle has a central longitudinal bore, in which the inner needle is arranged, which is fixed relative to the valve body. The nozzle needle is guided in particular in its valve seat facing end portion on the inner needle, so that there can be no dislocation of the nozzle needle in the region of the valve seat.

Gemäß der Erfindung weist die Innennadel wenigstens zwei radial nach außen ragende Fixierstege auf, die an der Innenwand der Bohrung anliegen und so die Innennadel in der Bohrung verstemmen. Hierdurch ist eine einfache Montage der Innennadel gewährleistet, ohne daß am Ventilkörper konstruktive Änderungen oder Vorbereitungen zur Aufnahme der Innennadel durchgeführt werden müssen. Es kann dabei auch vorgesehen sein, mehr als zwei Fixierstege auszubilden, die dann vorzugsweise gleichmäßig über den Umfang der Innennadel verteilt angeordnet sind.According to the invention, the inner needle has at least two radially outwardly projecting fixing webs, which bear against the inner wall of the bore and thus caulk the inner needle in the bore. As a result, a simple assembly of the inner needle is ensured without the valve body design changes or preparations for receiving the inner needle must be performed. It can also be provided to form more than two fixing webs, which are then preferably distributed uniformly over the circumference of the inner needle.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung weist die Innennadel in ihrem Mittelbereich einen Freistich auf, so daß die Düsennadel nur in einem brennraumzugewandten Endabschnitt und einem brennraumabgewandten Endabschnitt auf der Innennadel geführt ist. Hierdurch ergeben sich zwischen der Innennadel und der Außennadel weniger Reibungsverluste und die Gefahr des Fressens der Außennadel auf der Innennadel ist reduziert.In an advantageous embodiment of the object of the invention, the inner needle has an undercut in its central region, so that the nozzle needle is guided only in a combustion chamber facing end portion and a combustion chamber facing away from end portion on the inner needle. As a result, between the inner needle and the outer needle less friction losses and the risk of seizing the outer needle on the inner needle is reduced.

Zeichnungdrawing

In der Zeichnung sind zwei Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils gezeigt. Es zeigt

  • Figur 1 einen Längsschnitt durch ein Kraftstoffeinspritzventil,
  • Figur 2 eine Vergrößerung von Figur 1 im Bereich des Ventilkörpers,
  • Figur 3 einen Querschnitt durch Figur 2 entlang der Linie III-III und
  • Figur 4 eine Vergrößerung von Figur 1 im Bereich des Ventilkörpers eines weiteren Ausführungsbeispiels.
In the drawing, two embodiments of the fuel injection valve according to the invention are shown. It shows
  • 1 shows a longitudinal section through a fuel injection valve,
  • FIG. 2 shows an enlargement of FIG. 1 in the region of the valve body,
  • Figure 3 shows a cross section through Figure 2 along the line III-III and
  • Figure 4 is an enlargement of Figure 1 in the region of the valve body of another embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Längsschnitt durch ein Kraftstoffeinspritzventil gezeigt. Ein Ventilhaltekörper 1 ist mittels einer Spannmutter 4 in axialer Richtung gegen einen Ventilkörper 3 verspannt. Im Ventilkörper 3 ist eine Bohrung 7 ausgebildet, an deren brennraumseitigen Ende eine Ventilsitzfläche 10 ausgebildet ist, der im wesentlichen konisch ausgebildet ist und in dem wenigstens eine Einspritzöffnung 9 angeordnet ist. In der Bohrung 7 ist eine Düsennadel 12 angeordnet, die kolbenförmig ausgebildet ist und die an ihrem brennraumseitigen Ende eine im wesentlichen kegelstumpfförmige Ventildichtfläche 17 aufweist, die mit der Ventilsitzfläche 10 zusammenwirkt, so daß bei Anlage der Ventildichtfläche 17 an der Ventilsitzfläche 10 die Einspritzöffnungen 9 verschlossen werden. Die Düsennadel 12 ist in einem brennraumabgewandten Abschnitt in der Bohrung 7 dichtend geführt, wobei der dichtend geführte Abschnitt der Düsennadel 12 einen größeren Durchmesser aufweist als der brennraumzugewandte Abschnitt der Düsennadel 12, so daß am Übergang eine Druckschulter 22 ausgebildet ist. Durch eine radiale Erweiterung der Bohrung 7 ist auf Höhe der Druckschulter 22 ein Druckraum 16 ausgebildet, der sich dem Brennraum zu als ein die Düsennadel 12 umgebender Ringkanal bis zur Ventilsitzfläche 10 fortsetzt. Der Druckraum 16 ist über einen im Ventilkörper 3 und im Ventilhaltekörper 1 verlaufenden Zulaufkanal 30 mit einem Hochdruckanschluß 49 verbunden, über den Kraftstoff aus einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle in den Druckraum gefördert werden kann. In Figur 2 ist zur Verdeutlichung eine vergrößerte Darstellung von Figur 1 im Bereich des Ventilkörpers 3 gezeigt und Figur 3 zeigt einen Querschnitt von Figur 2 entlang der Linie III-III. Die Düsennadel 12 weist eine mittige Längsbohrung 19 auf, die hier als Führungsbohrung dient und in der eine Innennadel 14 angeordnet ist. Die Innennadel 14 weist an ihrem brennraumzugewandten Ende eine Anlagefläche 11 auf, die konisch ausgebildet ist und an der ebenfalls konisch ausgebildeten Ventilsitzfläche 10 anliegt. Durch die konische Form beider Flächen wird die Anlagefläche 11 zentrisch fixiert, so daß die brennraumzugewandte Seite der Innennadel 14 genau in Richtung der Längsachse 6 der Bohrung 7 ausgerichtet ist. Am brennraumabgewandten Ende weist die Innennadel 14 drei Fixierstege 20 auf, die sich in radialer Richtung von der Innennadel 14 nach außen erstrecken, wo sie kraftschlüssig in der Bohrung 7 verstemmt sind. Die drei Fixierstege 20 sind gleichmäßig über den Umfang der Innennadel 14 verteilt angeordnet, so daß die Innennadel 14 durch die Fixierstege 20 genau in Richtung der Längsachse 6 der Bohrung 7 ortsfest im Ventilkörper 3 fixiert wird. Es kann auch vorgesehen sein, mehr oder weniger als drei Fixierstege 20 an der Düsennadel 12 auszubilden, die dann ebenfalls vorzugsweise gleichmäßig über den Umfang der Innennadel 14 verteilt angeordnet sind. Die Düsennadel 12 weist entsprechende Ausnehmungen 15 auf, die die Fixierstege 20 aufnehmen und so die Längsverschiebbarkeit der Düsennadel 12 auf der Innennadel 14 gewährleisten. Hierbei bleibt zwischen der brennraumzugewandten Seite des Fixierstegs 20 und der Ausnehmung 15 ein Spalt 36 bestehen, der auch in Öffnungsstellung der Düsennadel 12 sicherstellt, daß die Düsennadel 12 nicht an den Fixierstegen 20 der Innennadel 14 zur Anlage kommt, so daß die Innennadel 14 nicht durch das ständige Anschlagen der Düsennadel 12 aus ihrer mittig fixierten Lage dejustiert wird.FIG. 1 shows a longitudinal section through a fuel injection valve. A valve holding body 1 is braced by means of a clamping nut 4 in the axial direction against a valve body 3. In the valve body 3, a bore 7 is formed, at the combustion chamber end of which a valve seat surface 10 is formed which is substantially conical and in which at least one injection opening 9 is arranged. In the bore 7, a nozzle needle 12 is arranged, which is piston-shaped and at its combustion chamber end has a substantially frusto-conical valve sealing surface 17 which cooperates with the valve seat 10, so that upon contact of the valve sealing surface 17 on the valve seat 10, the injection openings 9 closed become. The nozzle needle 12 is sealingly guided in a bore away from combustion chamber in the bore 7, wherein the sealingly guided portion of the nozzle needle 12 has a larger diameter than the combustion chamber facing portion of the nozzle needle 12, so that at the transition, a pressure shoulder 22 is formed. By a radial extension of the bore 7, a pressure chamber 16 is formed at the level of the pressure shoulder 22, which continues to the combustion chamber to as the nozzle needle 12 surrounding annular channel to the valve seat surface 10. The pressure chamber 16 is connected via a valve body 3 and in the valve holding body 1 extending inlet channel 30 with a high-pressure port 49, can be promoted via the fuel from a high-pressure fuel source, not shown in the drawing into the pressure chamber. In FIG. 2, an enlarged view of FIG. 1 in the region of the valve body 3 is shown for clarity and FIG. 3 shows a cross section of FIG. 2 along the line III-III. The nozzle needle 12 has a central longitudinal bore 19, which serves here as a guide bore and in which an inner needle 14 is arranged. The inner needle 14 has at its combustion chamber end facing a contact surface 11 which is conical and rests against the likewise conical valve seat surface 10. Due to the conical shape of both surfaces, the contact surface 11 is centrally fixed, so that the combustion chamber facing side of the inner needle 14 is aligned exactly in the direction of the longitudinal axis 6 of the bore 7. At the end facing away from the combustion chamber, the inner needle 14 has three fixing webs 20, which extend in the radial direction from the inner needle 14 to the outside, where they are caulked non-positively in the bore 7. The three fixing webs 20 are distributed uniformly over the circumference of the inner needle 14, so that the inner needle 14 is fixed by the Fixierstege 20 exactly in the direction of the longitudinal axis 6 of the bore 7 fixed in the valve body 3. It can also be provided to form more or less than three fixing webs 20 on the nozzle needle 12, which are then preferably also distributed uniformly over the circumference of the inner needle 14. The nozzle needle 12 has corresponding recesses 15, which receive the fixing webs 20 and thus ensure the longitudinal displacement of the nozzle needle 12 on the inner needle 14. This remains between the combustion chamber facing side of the Fixierstegs 20 and the recess 15, a gap 36, which ensures even in the open position of the nozzle needle 12 that the nozzle needle 12 does not come to the Fixierstegen 20 of the inner needle 14 to the plant, so that the inner needle 14 is not through the constant impact of the nozzle needle 12 is dejustiert from its centrally fixed position.

Die Düsennadel 12 liegt an ihrem brennraumabgewandten Ende an einem zylinderförmigen Druckstück 37 an, das in einem im Ventilhaltekörper 1 ausgebildeten Federraum 32 angeordnet ist. Zwischen dem brennraumabgewandten Ende des Federraums 32 und dem Druckstück 37 ist eine Schließfeder 34 unter Druckvorspannung angeordnet, die über das Druckstück 37 auf die Düsennadel 12 wirkt und so die Düsennadel 12 in Schließstellung - das ist, wenn die Ventildichtfläche 17 an der Ventilsitzfläche 10 anliegt - drückt. Koaxial zur Bohrung 7 ist im Ventilhaltekörper 1 eine Kolbenbohrung 38 ausgebildet, die in den Federraum 32 mündet. In der Kolbenbohrung 38 ist ein Druckkolben 39 längsverschiebbar angeordnet, der an seinem brennraumzugewandten Ende bis in den Federraum 32 ragt und dort am Druckstück 37 anliegt und mit seiner brennraumabgewandten Stirnfläche 41 einen Steuerraum 40 begrenzt. Der Öffnungshub der Düsennadel 12 wird hierbei durch den Anschlag des Druckkolbens 39 am brennraumabgewandten Ende der Kolbenbohrung 38 gestoppt. Der Steuerraum 40 ist über eine Zulaufdrossel 42 mit dem Zulaufkanal 30 verbunden und über eine Ablaufdrossel 43 mit einem im Ventilhaltekörper 1 ausgebildeten Leckölraum 48. Dieser Leckölraum 48 ist mit einem in der Zeichnung nicht dargestellten Leckölsystem verbunden und so ständig drucklos. Im Leckölraum 48 ist ein Magnetanker 45 angeordnet, an dessen dem Steuerraum 40 zugewandten Ende eine Dichtkugel 47 angeordnet ist. Der Magnetanker 45 wird durch eine Feder 53 in Richtung des Steuerraums 40 beaufschlagt, so daß die Dichtkugel 47 auf die Ablaufdrossel 43 gedrückt wird und die Ablaufdrossel 43 verschließt. Im Ventilhaltekörper 1 ist ein die Feder 53 umgebender Elektromagnet 51 angeordnet, der bei entsprechender Bestromung eine anziehende Kraft auf den Magnetanker 45 ausübt, so daß dieser entgegen der Kraft der Feder 53 in Richtung des Elektromagneten 51 gezogen wird, so daß die Dichtkugel 47 die Ablaufdrossel 43 freigibt. Wird der Elektromagnet 51 nicht bestromt, so drückt die Feder 53 den Magnetanker 45 und damit die Dichtkugel 47 wieder auf die Ablaufdrossel 43 und verschließt so den Steuerraum 40 gegen den Leckölraum 48.The nozzle needle 12 is located at its end facing away from the combustion chamber on a cylindrical pressure piece 37, which is arranged in a formed in the valve holding body 1 spring chamber 32. Between the combustion chamber facing away from the end of the spring chamber 32 and the pressure piece 37, a closing spring 34 is arranged under pressure bias, on the pressure piece 37 on the nozzle needle 12 acts and so the nozzle needle 12 in the closed position - that is, when the valve sealing surface 17 abuts the valve seat surface 10 - presses. Coaxially to the bore 7, a piston bore 38 is formed in the valve holding body 1, which opens into the spring chamber 32. In the piston bore 38, a pressure piston 39 is arranged longitudinally displaceable, which protrudes at its end facing the combustion chamber into the spring chamber 32 and there rests on the pressure piece 37 and limited with its combustion chamber facing away face 41 a control chamber 40. The opening stroke of the nozzle needle 12 is stopped by the abutment of the pressure piston 39 at the combustion chamber end facing away from the piston bore 38. The control chamber 40 is connected via an inlet throttle 42 to the inlet channel 30 and via an outlet throttle 43 with a formed in the valve holding body 1 leakage oil space 48. This leakage oil chamber 48 is connected to a drain oil, not shown in the drawing and thus constantly depressurized. In the leakage oil chamber 48, a magnet armature 45 is arranged, on whose the control chamber 40 facing the end of a sealing ball 47 is arranged. The armature 45 is acted upon by a spring 53 in the direction of the control chamber 40, so that the sealing ball 47 is pressed onto the outlet throttle 43 and the outlet throttle 43 closes. In the valve holding body 1, a spring 53 surrounding the electromagnet 51 is arranged, which exerts an attractive force to the armature 45 with appropriate energization, so that it is pulled against the force of the spring 53 in the direction of the electromagnet 51, so that the sealing ball 47, the outlet throttle 43 releases. If the electromagnet 51 is not energized, then the spring 53 pushes the magnet armature 45 and thus the sealing ball 47 back onto the outlet throttle 43 and thus closes off the control chamber 40 against the leakage oil chamber 48.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Über den Hochdruckanschluß 49 wird ständig Kraftstoff unter hohem Druck bis in den Druckraum 16 geleitet, so daß im Druckraum 16 ein konstanter vorgegebener Kraftstoffhochdruck herrscht. Hierdurch ergibt sich eine hydraulische Kraft auf die Druckschulter 22 der Düsennadel 12, die in Öffnungsrichtung der Düsennadel 12 gerichtet ist. Soll keine Einspritzung erfolgen, so ist der Elektromagnet 51 nicht bestromt und die Ablaufdrossel 43 somit durch die Dichtkugel 47 verschlossen. Hierdurch herrscht im Steuerraum 40 bedingt durch die Zulaufdrossel 42 derselbe Druck wie im Zulaufkanal 30 oder im Druckraum 16, so daß sich eine entsprechende hydraulische Kraft auf die brennraumabgewandte Stirnfläche 41 des Druckkolbens 39 ergibt. Da der Druckkolben 39 einen größeren Durchmesser aufweist, und damit eine größere hydraulisch wirksame Fläche als die Düsennadel 12, überwiegt die vom Druckkolben 39 über das Druckstück 37 auf die Düsennadel 12 ausgeübte Kraft, so daß die Düsennadel 12 in Schließstellung verharrt und die Einspritzöffnungen 9 verschließt. Soll eine Einspritzung erfolgen, so wird der Elektromagnet 51 bestromt und der Magnetanker 45 bewegt sich in Richtung des Elektromagneten 51. Hierdurch gibt die Dichtkugel 47 die Ablaufdrossel 43 frei und der Steuerraum 40 wird mit dem Leckölraum 48 verbunden. Hierdurch sinkt der Druck im Steuerraum 40, so daß nun die hydraulische Kraft auf die Druckschulter 22 der Düsennadel 12 überwiegt und die Düsennadel von der Ventilsitzfläche 10 abhebt und die Einspritzöffnungen 9 freigibt. Die Schließfeder 34 spielt hierbei nur eine untergeordnete Rolle und dient hauptsächlich dazu, bei abgeschaltetem Kraftstoffeinspritzsystem die Düsennadel 12 in geschlossener Stellung zu halten. Soll die Einspritzung beendet werden, wird der Elektromagnet 51 stromlos geschaltet, und der Kraftstoffhochdruck des Zulaufkanals 30 baut sich wieder im Steuerraum 40 auf.The operation of the fuel injection valve is as follows: Via the high pressure port 49 fuel is constantly passed under high pressure into the pressure chamber 16, so that in the pressure chamber 16 a constant predetermined high pressure fuel prevails. This results in a hydraulic force on the pressure shoulder 22 of the nozzle needle 12, which is directed in the opening direction of the nozzle needle 12. If no injection takes place, then the electromagnet 51 is not energized and the outlet throttle 43 is thus closed by the sealing ball 47. As a result, prevails in the control chamber 40 due to the inlet throttle 42, the same pressure as in the inlet channel 30 or in the pressure chamber 16 so that a corresponding hydraulic force on the combustion chamber facing away from face 41 of the pressure piston 39 results. Since the pressure piston 39 has a larger diameter, and thus a larger hydraulically effective area than the nozzle needle 12, the force exerted by the pressure piston 39 via the pressure piece 37 on the nozzle needle 12 force prevails, so that the nozzle needle 12 remains in the closed position and the injection openings 9 closes , If an injection takes place, then the electromagnet 51 is energized and the magnet armature 45 moves in the direction of the electromagnet 51. In this way, the sealing ball 47 releases the outlet throttle 43 and the control chamber 40 is connected to the leakage oil chamber 48. As a result, the pressure in the control chamber 40 decreases, so that now the hydraulic force on the pressure shoulder 22 of the nozzle needle 12 outweighs and lifts the nozzle needle from the valve seat surface 10 and the injection openings 9 releases. The closing spring 34 plays only a minor role and is mainly used to keep the nozzle needle 12 in the closed position when the fuel injection system is switched off. If the injection is terminated, the electromagnet 51 is de-energized, and the high fuel pressure of the inlet channel 30 builds up again in the control chamber 40.

Bei der Montage der Düsennadel 12 und der Innennadel 14 in der Bohrung 7 geht man beispielsweise folgendermaßen vor: Die Innennadel 14 wird in die Düsennadel 12 eingeführt und anschließend werden beide gemeinsam in die Bohrung 7 eingeführt. Hierbei sind die Ringstege 20 der Innennadel 14 so ausgebildet, daß sie in die Bohrung 7 eingepreßt werden müssen, so daß eine ortsfeste Fixierung der Innennadel 14 in der Bohrung 7 entlang deren Längsachse 6 erfolgt. Die Düsennadel 12 braucht nicht weiter fixiert zu werden, da sie durch die Fixierung der Innennadel 14 eindeutig in der Bohrung 7 angeordnet ist. Anschließend wird der Ventilhaltekörper 1 mit dem darin bereits angeordneten Druckkolben 39, der Schließfeder 34 und dem Druckstück 37 mittels der Spannmutter 4 gegen den Ventilkörper 3 verspannt.When mounting the nozzle needle 12 and the inner needle 14 in the bore 7, for example, proceed as follows: The inner needle 14 is inserted into the nozzle needle 12 and then both are introduced together into the hole 7. Here, the annular webs 20 of the inner needle 14 are formed so that they must be pressed into the bore 7, so that a stationary fixation of the inner needle 14 takes place in the bore 7 along its longitudinal axis 6. The nozzle needle 12 does not need to be fixed further, since it is arranged uniquely in the bore 7 by the fixation of the inner needle 14. Subsequently, the valve holding body 1 is braced with the pressure piston 39 already arranged therein, the closing spring 34 and the pressure piece 37 by means of the clamping nut 4 against the valve body 3.

In Figur 4 ist ein weiteres Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils gezeigt. Die Innennadel 14 hat hierbei keinen konstanten Außendurchmesser, sondern weist zwischen einem ersten brennraumzugewandten Führungsabschnitt 114 und einem zweiten brennraumabgewandten Führungsabschnitt 214 einen Freistich 25 auf, in dessen Bereich die Innennadel 14 im Außendurchmesser verringert ist. Die Düsennadel 12 wird nur auf dem ersten Führungsabschnitt 114 und dem zweiten Führungsabschnitt 214 geführt, wodurch die Gefahr des Fressens der Düsennadel 12 auf der Innennadel 14 verringert ist, und es werden sowohl der Verschleiß als auch die Reibung der Düsennadel 12 auf der Innennadel 14 reduziert. Hierbei kann es auch vorgesehen sein, daß der zweite Führungsabschnitt 214 ebenfalls entfällt und die Düsennadel 12 auf der Innennadel 14 nur auf dem ersten Führungsabschnitt 114 geführt wird. Die Düsennadel 12 ist im brennraumabgewandten Abschnitt der Bohrung 7 an ihrer Außenmantelfläche ohnehin dichtend geführt, so daß eine Führung der Düsennadel 12 in diesem Bereich auf der Innennadel 14 zur Stabilisierung je nach Anforderung an das Kraftstoffeinspritzventil nicht unbedingt notwendig ist.FIG. 4 shows a further exemplary embodiment of the fuel injection valve according to the invention. The inner needle 14 in this case has no constant outer diameter, but has between a first combustion chamber facing guide portion 114 and a second combustion chamber away from the guide portion 214 an undercut 25, in the region of the inner needle 14 is reduced in outer diameter. The nozzle needle 12 is guided only on the first guide portion 114 and the second guide portion 214, whereby the risk of seizing the nozzle needle 12 is reduced to the inner needle 14, and both the wear and the friction of the nozzle needle 12 are reduced on the inner needle 14 , It can also be provided that the second guide portion 214 is also omitted and the nozzle needle 12 is guided on the inner needle 14 only on the first guide portion 114. The nozzle needle 12 is already sealingly guided in the combustion chamber facing away from the bore 7 on its outer lateral surface, so that a guide of the nozzle needle 12 in this area on the inner needle 14 for stabilization depending on the requirements of the fuel injection valve is not essential.

Claims (6)

  1. Fuel injection valve for internal combustion engines having a valve body (3) in which is formed a bore (7), at the end of which bore (7) are formed a valve seat face (10) and at least one injection opening (9), by means of which injection opening (9) the bore (7) can be connected to a combustion chamber of the internal combustion engine, and having a nozzle needle (12) which is longitudinally displaceable within the bore (7) and has at its combustion chamber end a sealing face (17) which interacts with the valve seat face (10) and thus controls the at least one injection opening (9), the nozzle needle (12) having a central longitudinal bore (19) in which is arranged an inner needle (14) which is fixed in terms of position relative to the valve body (3), the nozzle needle (12) being guided over at least part of its length on the inner needle (14), characterized in that the inner needle (14) has at least two radially outwardly projecting fixing webs (20) which bear against the inner wall of the bore (7) and thus lodge the inner needle (14) in the bore (7).
  2. Fuel injection valve according to Claim 1, characterized in that the fixing webs (20) are arranged in that end region of the inner needle (14) which faces away from the combustion chamber.
  3. Fuel injection valve according to Claim 1, characterized in that the fixing webs (20) are arranged so as to be uniformly distributed about the circumference of the inner needle (14).
  4. Fuel injection valve according to Claim 1, characterized in that the outer needle (12) is guided at least at its combustion chamber end on the inner needle (14).
  5. Fuel injection valve according to Claim 1, characterized in that the inner needle (14) has an undercut (25).
  6. Fuel injection valve according to Claim 1, characterized in that the nozzle needle (12) is guided, in an end section nearest the combustion chamber, on the inner needle (14) and, in an end section which faces away from the combustion chamber, in the bore (7).
EP02727267A 2001-03-28 2002-03-26 Fuel-injection valve for internal combustion engines Expired - Lifetime EP1373710B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10115215 2001-03-28
DE10115215A DE10115215A1 (en) 2001-03-28 2001-03-28 Fuel injection valve for internal combustion engines
PCT/DE2002/001094 WO2002077442A1 (en) 2001-03-28 2002-03-26 Fuel-injection valve for internal combustion engines

Publications (2)

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EP1373710A1 EP1373710A1 (en) 2004-01-02
EP1373710B1 true EP1373710B1 (en) 2006-07-26

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US (1) US6874704B2 (en)
EP (1) EP1373710B1 (en)
JP (1) JP2004526895A (en)
CN (1) CN1298991C (en)
DE (2) DE10115215A1 (en)
WO (1) WO2002077442A1 (en)

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Publication number Priority date Publication date Assignee Title
DE10222196A1 (en) * 2002-05-18 2003-11-27 Bosch Gmbh Robert Fuel injection valve for combustion engine, has control valve with valve chamber and valve member that is moveable between two end positions for opening or closing connections to certain chambers
JP4013912B2 (en) * 2004-03-29 2007-11-28 トヨタ自動車株式会社 Fuel injection valve
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
JP4552890B2 (en) * 2006-05-11 2010-09-29 株式会社デンソー Injector
DE102006040645A1 (en) * 2006-08-30 2008-03-13 Robert Bosch Gmbh Injector for internal combustion engines
DE102006047935A1 (en) 2006-10-10 2008-04-17 Robert Bosch Gmbh Fuel injector for an internal combustion engine
DE102008061400A1 (en) * 2008-12-10 2010-06-17 Man Diesel Se Fuel injection valve for an internal combustion engine
DE102009054441A1 (en) * 2009-11-25 2011-06-30 L'Orange GmbH, 70435 Fuel injection nozzle for internal combustion engines
DE102016209249A1 (en) * 2016-05-27 2017-11-30 Robert Bosch Gmbh Gas valve for dosing gaseous fuels

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WO1999019619A1 (en) * 1997-10-09 1999-04-22 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

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DE2030445A1 (en) 1970-06-20 1972-01-27 Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Injector
DE2710216A1 (en) * 1977-03-09 1978-09-14 Bosch Gmbh Robert FUEL INJECTOR
DE4303813C1 (en) 1993-02-10 1994-06-30 Bosch Gmbh Robert Fuel injection nozzle for internal combustion engines
AU4627797A (en) 1997-10-09 1999-05-03 Renault Method for producing a synchronising signal for controlling an internal combustion engine electronic injection system
JPH11280588A (en) 1998-03-31 1999-10-12 Denso Corp Fuel injection nozzle
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GB9914644D0 (en) * 1999-06-24 1999-08-25 Lucas Ind Plc Fuel injector
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WO1999019619A1 (en) * 1997-10-09 1999-04-22 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

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WO2002077442A1 (en) 2002-10-03
EP1373710A1 (en) 2004-01-02
CN1460151A (en) 2003-12-03
CN1298991C (en) 2007-02-07
US6874704B2 (en) 2005-04-05
DE10115215A1 (en) 2002-10-10
DE50207640D1 (en) 2006-09-07
US20030155441A1 (en) 2003-08-21
JP2004526895A (en) 2004-09-02

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