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EP1404964B1 - Fuel injector with a switchable control chamber feed - Google Patents

Fuel injector with a switchable control chamber feed Download PDF

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Publication number
EP1404964B1
EP1404964B1 EP02758062A EP02758062A EP1404964B1 EP 1404964 B1 EP1404964 B1 EP 1404964B1 EP 02758062 A EP02758062 A EP 02758062A EP 02758062 A EP02758062 A EP 02758062A EP 1404964 B1 EP1404964 B1 EP 1404964B1
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EP
European Patent Office
Prior art keywords
valve
pressure
space
switching valve
fuel
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.)
Expired - Lifetime
Application number
EP02758062A
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German (de)
French (fr)
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EP1404964A2 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1404964A2 publication Critical patent/EP1404964A2/en
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Publication of EP1404964B1 publication Critical patent/EP1404964B1/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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0068—Actuators specially adapted for partial and full opening of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • DE 199 10 589 A1 refers to an injection valve for an internal combustion engine.
  • a servo valve which has a movable valve element.
  • the valve element comprises a throttle in the fuel path to the injection nozzle for the initial phase of the injection. Further, it has a piston-shaped shoulder over a groove which emerges from a bore in the main phase of injection and thereby releases a direct path for the fuel bypassing the throttle.
  • DE 197.44 518 A1 also relates to a fuel injection valve for internal combustion engines.
  • a valve body an axially displaceable valve member is arranged. This has at its the combustion chamber of the internal combustion engine facing the ends of a conical valve sealing surface, with which it has a conical valve seat surface in the valve body interacts.
  • the conical valve seat surface has on the valve member on a sealing edge forming annular edge.
  • at least one injection opening is provided in the combustion chamber of the internal combustion engine, in which, when the injection valve is closed, the region of the valve seat surface adjacent to the sealing edge is provided downstream.
  • the valve member has a guide bore, with which it is slidably guided on a pin of a stationary inserted in the valve body insert body.
  • a fuel injection valve in which a valve chamber of a three-way valve is selectively connected to a drain or a high-pressure line.
  • the high pressure line opens into a valve chamber of the switching valve.
  • valve member In this known from the prior art arrangement of a fuel injection valve very small actuating forces and thus very fast valve lift movements of the valve member of the injection valve are possible. These fast adjustment movements are made possible by the small hydraulically effective surfaces on the valve member and the small control volume, with only small moving masses are to be adjusted.
  • the valve member is provided with a guide bore, with which it is slidably guided on a pin of a stationary inserted into the valve body insert body.
  • a higher pressure rise speed can be achieved in the control chamber of the fuel injector.
  • a faster rise in pressure in the control chamber of the fuel injector causes a rapid movement of the nozzle needle from these and consequently a rapid closing of the injection openings at the combustion chamber end of the fuel injector.
  • the formation of soot in the combustion chamber of self-igniting internal combustion engines is significantly reduced.
  • a switching valve can be to increase the rate of pressure rise in the control chamber of the injector another, in addition to a permanently acting inlet throttle in a high pressure side inlet to the pressure build-up in the control room.
  • control chamber respectively associated permanent throttle pressure relief of the control chamber in the direction of flow of the fuel acts Leckagagereduplicd;
  • the throttling element provided in the discharge passage of the control space acts - in the opposite direction, i.e., in the opposite direction. seen in the direction of supply to the control room out - as inlet throttle for the control room.
  • the valve body of the switching valve can be in a switchable high-pressure side feed to the control room releasing or bring this closing position.
  • the nozzle needle / plunger arrangement in the injector body can be given a first or a second closing speed with which the injection chamber-side injection openings on the injector body are closed.
  • FIG. 1 is an injector with opening on the valve chamber of the switching valve, permanently effective high-pressure side inlet can be seen.
  • An injector body 1 of a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a control chamber 2.
  • the control chamber 2 is delimited by a control chamber wall 3, a control chamber surface 4 and an end face 8 of a nozzle needle / plunger arrangement 6.
  • an outlet / inlet opening 9 surrounding a ring-shaped configured stop surface 5 is formed.
  • the nozzle needle / tappet arrangement 6 can be either a nozzle needle closing or releasing the injection openings at the combustion chamber end of the injector body 1, and also an indirect tappet actuating tappet.
  • the nozzle needle / plunger assembly 6 is imparted a movement according to the double arrow 7 in the injector body 1 of the fuel injector.
  • a flow channel 10 is the pressure-relieved or pressurizable, the nozzle needle / plunger assembly 6 actuated control chamber 2 in conjunction with a valve chamber 18 of a switching valve 16, which is preferably designed as a multi-way valve.
  • the flow channel 10 is formed in a cross section 15; in the flow channel 10, a first throttle element 13 is inserted.
  • the first throttle element 13 is formed in a substantially smaller cross section 14 in comparison to the cross sectional area 15 of the flow channel 10 Fig. 1 illustrated flow channel 10 is acted upon both in the inlet direction 11 of the fuel to the control chamber 2 and opposite thereto in the flow direction 12 of the fuel from the control chamber 2 to the valve chamber 18 of the switching valve 16.
  • the switching valve 16 preferably designed as a multi-way switching valve, is likewise integrated in the injector body 1.
  • the switching valve 16 comprises a valve body 17 which is surrounded by a valve chamber 18 in the injector body 1. Opposite one another, a first valve seat 19 and a second valve seat 20 are formed on the valve space.
  • the valve body 17 of the switching valve 16 is preferably formed as a spherically configured valve body and actuated via a transmission element 22 schematically indicated here.
  • the transmission element 22 is in operative connection with an actuator not shown here, be it a piezoelectric actuator or a mechanical-hydraulic translator, which the transmission element 22 a vertical movement corresponding double arrow 23 imparts, whereby the valve body 17 of the switching valve 16 respectively in the first valve seat 19 and ., the second valve seat 20 is adjustable.
  • an annular gap 21 is formed, from which at a branch point 25 is formed in the low pressure region of the fuel injection system extending drain 24.
  • a permanently acting high-pressure side inlet 28 Perpendicular to the direction of actuation 23 of the valve body 17 opens into the valve chamber 18 of the switching valve 16 is a permanently acting high-pressure side inlet 28, in the line cross section, a second throttle element 26 is integrated. Since this high-pressure side inlet is oriented perpendicular to the actuation direction of the valve body 17 in the valve chamber 18, the permanently acting high-pressure side inlet 28 is not closed upon actuation of the valve body 17 of the switching valve 16, so that the pending there pressure permanently on the flow channel 10 and thus in the control chamber 2 is present ,
  • the transmission element 22 opposite, opens in the region of the second valve seat 20 below the adjustable in the valve chamber 18 valve body 17, another high pressure side inlet 29 from a high pressure source, not shown here, be it a high-pressure pump or a high-pressure accumulator (common rail) with integrated third throttle element 27.
  • a high pressure source not shown here, be it a high-pressure pump or a high-pressure accumulator (common rail) with integrated third throttle element 27.
  • high-pressure side inlet is closed when placed in the second valve seat 20 valve body 17, so that the control chamber 2 in the inlet direction 11 only via the opening into the valve chamber 18 of the switching valve 16, permanently acting high pressure side inlet 28 with control volume is charged.
  • the underlying idea is a pressure relief of the control chamber 2 when placed in the second valve seat 20 valve body 17 of the switching valve 16 in flow direction 12 of the fuel from the control chamber 2.
  • the integrated into the flow channel 10 first throttle element 13 acts here as a drain throttle
  • a pressurization of the control chamber 2 via flow channel 10 can according to the embodiment in Fig. 1 either via the valve space 18 permanently acting on the high-pressure side inlet 28 with second throttle element 26 done so that adjusts a pressure build-up in the control chamber 2 in the inlet direction 11 of the fuel in the flow channel 10 via the then acting as inflow throttle element first throttle 13.

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

Description

Technisches GebietTechnical area

Bei direkteinspritzenden Verbrennungskraftmaschinen werden heute in zunehmendem Maße Kraftstoffeinspritzsysteme mit einem Druckspeicherraum eingesetzt, um das an den einzelnen Kraftstoffinjektoren anstehende Kraftstoffdruckniveau weitestgehend konstant zu halten. Die im Injektorkörper des Kraftstoffinjektors aufgenommene Düsennadel wird über einen druckentlastbaren Steuerraum betätigt, der über einen hochdruckseitigen Zulauf mit einer Hochdruckquelle in Verbindung steht. Um ein schnelles Schließen der Düsennadel, d.h. deren schnelles Einfahren in den Düsennadelsitz zu gewährleisten, ist ein schneller Druckanstieg im Steuerraum erforderlich.In direct-injection internal combustion engines today fuel injection systems are increasingly used with a pressure storage chamber to keep the pending at the individual fuel injectors fuel pressure level largely constant. The nozzle needle accommodated in the injector body of the fuel injector is actuated via a pressure-relievable control chamber, which is connected via a high-pressure-side inlet to a high-pressure source. To ensure rapid closing of the nozzle needle, i. To ensure their rapid retraction into the nozzle needle seat, a rapid increase in pressure in the control room is required.

Stand der TechnikState of the art

DE 199 10 589 A1 bezieht sich auf ein Einspritzventil für eine Brennkraftmaschine. Gemäß dieser Lösung wird ein Servoventil eingesetzt, welches ein bewegliches Ventilelement aufweist. Das Ventilelement umfasst eine Drossel im Kraftstoffweg zur Einspritzdüse für die Anfangsphase der Einspritzung. Ferner weist es einen kolbenförmigen Absatz über einer Nut auf, der in der Hauptphase der Einspritzung aus einer Bohrung auftaucht und dadurch einen direkten Weg für den Kraftstoff unter Umgehung der Drossel freigibt. Diese Maßnahmen dienen dem Zweck, zu Beginn der Verbrennung ein langsames, kontrolliertes Öffnen der Einspritzöffnungen zu erreichen und während der Hauptphase der Einspritzung eine höhere Einspritzrate von Kraftstoff in den Brennraum der Verbrennungskraftmaschine zu realisieren. DE 199 10 589 A1 refers to an injection valve for an internal combustion engine. According to this solution, a servo valve is used, which has a movable valve element. The valve element comprises a throttle in the fuel path to the injection nozzle for the initial phase of the injection. Further, it has a piston-shaped shoulder over a groove which emerges from a bore in the main phase of injection and thereby releases a direct path for the fuel bypassing the throttle. These measures serve the purpose of achieving a slow, controlled opening of the injection openings at the beginning of the combustion and to realize a higher injection rate of fuel into the combustion chamber of the internal combustion engine during the main phase of the injection.

DE 197.44 518 A1 betrifft ebenfalls ein Kraftstoffeinspritzventil für Brennkraftmaschinen. In einen Ventilkörper ist ein axial verschiebbares Ventilglied angeordnet. Dieses weist an seinem den Brennraum der Verbrennungskraftmaschine zugewandten Enden eine konische Ventildichtfläche auf, mit welcher es mit einer konischen Ventilsitzfläche im Ventilkörper zusammenwirkt. Die konische Ventilsitzfläche weist am Ventilglied eine eine Dichtkante bildende Ringkante auf. Ferner ist wenigstens eine Einspritzöffnung in den Brennraum der Verbrennungskraftmaschine, in dem sich bei geschlossenem Einspritzventil stromabwärts an die Dichtkante anschließenden Bereich der Ventilsitzfläche vorgesehen. Das Ventilglied weist eine Führungsbohrung auf, mit der es gleitverschiebbar auf einem Zapfen eines ortsfest im Ventilkörper eingelassenen Einsatzkörpers geführt ist. DE 197.44 518 A1 also relates to a fuel injection valve for internal combustion engines. In a valve body, an axially displaceable valve member is arranged. This has at its the combustion chamber of the internal combustion engine facing the ends of a conical valve sealing surface, with which it has a conical valve seat surface in the valve body interacts. The conical valve seat surface has on the valve member on a sealing edge forming annular edge. Furthermore, at least one injection opening is provided in the combustion chamber of the internal combustion engine, in which, when the injection valve is closed, the region of the valve seat surface adjacent to the sealing edge is provided downstream. The valve member has a guide bore, with which it is slidably guided on a pin of a stationary inserted in the valve body insert body.

Aus DE-A 100 55 714 ist ein Kraftstoffeinspritzventil bekannt, bei dem eine Ventilkammer eines Dreiwegeventils wahlweise mit einer Ablass- oder einer Hochdruckleitung verbunden wird. Die Hochdruckleitung mündet dabei in einem Ventilraum des Schaltventils.Out DE-A 100 55 714 a fuel injection valve is known in which a valve chamber of a three-way valve is selectively connected to a drain or a high-pressure line. The high pressure line opens into a valve chamber of the switching valve.

Bei dieser aus dem Stand der Technik bekannten Anordnung eines Kraftstoffeinspritzventiles sind sehr kleine Stellkräfte und somit sehr schnelle Ventilhubbewegungen des Ventilgliedes des Einspritzventiles möglich. Diese schnellen Verstellbewegungen werden dabei durch die kleinen hydraulisch wirksamen Flächen am Ventilglied und das kleine Steuervolumen ermöglicht, wobei nur kleine bewegte Massen zu verstellen sind. Dazu ist das Ventilglied mit einer Führungsbohrung versehen, mit der es gleitverschiebbar auf einem Zapfen eines ortsfest in den Ventilkörper eingelassenen Einsatzkörpers geführt wird.In this known from the prior art arrangement of a fuel injection valve very small actuating forces and thus very fast valve lift movements of the valve member of the injection valve are possible. These fast adjustment movements are made possible by the small hydraulically effective surfaces on the valve member and the small control volume, with only small moving masses are to be adjusted. For this purpose, the valve member is provided with a guide bore, with which it is slidably guided on a pin of a stationary inserted into the valve body insert body.

Darstellung der ErfindungPresentation of the invention

Mit dem erfindungsgemäßen Verfahren kann eine höhere Druckanstiegsgeschwindigkeit im Steuerraum des Kraftstoffinjektors erreicht werden. Ein schnellerer Druckanstieg im Steuerraum des Kraftstoffinjektors bewirkt ein schnelles Auffahren der Düsennadel aus diesen und demzufolge ein schnelles Verschließen der Einspritzöffnungen am brennraumseitigen Ende des Kraftstoffinjektors. Dadurch wird die Rußbildung im Brennraum von selbstzündenden Verbrennungskraftmaschinen signifikant reduziert. Mittels eines Schaltventils läßt sich zu Steigerung der Druckanstiegsgeschwindigkeit im Steuerraum des Injektorkörpers ein weiteres, neben einer permanent wirkenden Zulaufdrossel in einem hochdruckseitigen Zulauf zum Druckaufbau im Steuerraum zuschalten. Bei alleinig wirksamen, permanenten hochdruckseitigen Zulauf in den Steuerraum, stellt sich in diesem eine erste Druckanstiegsgeschwindgkeit ein. Mit dieser ersten durch die permanente Zulaufdrossel festgelegten Druckanstiegsgeschwindigkeit im Steuerraum erfolgt ein Einfahren der Düsennadel/Düsenanordnung im Ventilkörper des Kraftstoffinjektors in den brennraumseitigen Düsennadelsitz mit einer ersten Schließgeschwindigkeit. Wird ein weiterer, zuschaltbarer hochdruckseitiger Zulauf aktiviert, strömt ein im wesentlichen verdoppeltes Volumen in den Steuerraum des Kraftstoffinjektors ein, so daß sich ein schnellerer Druckaufbau in diesem und demzufolge ein schnelleres Schließen der Düsennadel in deren brennraumseitigen Sitz einstellt. Durch die zweite, im Vergleich zur ersten Düsengeschwindigkeit höhere Schließgeschwindigkeit, d.h. Verschließgeschwindigkeit der Einspritzdüsen an der brennraumseitigen Öffnung des Injektors, lässt sich ein wohldefiniertes Ende des Einspritzvorganges herbeiführen, so dass eine Rußbildung im Brennraum gegen Ende des in diesem ablaufenden Verbrennungsvorganges wirksam unterbunden wird.With the method according to the invention, a higher pressure rise speed can be achieved in the control chamber of the fuel injector. A faster rise in pressure in the control chamber of the fuel injector causes a rapid movement of the nozzle needle from these and consequently a rapid closing of the injection openings at the combustion chamber end of the fuel injector. As a result, the formation of soot in the combustion chamber of self-igniting internal combustion engines is significantly reduced. By means of a switching valve can be to increase the rate of pressure rise in the control chamber of the injector another, in addition to a permanently acting inlet throttle in a high pressure side inlet to the pressure build-up in the control room. When only effective, permanent high-pressure side inlet into the control room, this is a first Druckanstiegsgeschwindgkeit. With this first set by the permanent inlet throttle pressure rise speed in the control chamber, retraction of the nozzle needle / nozzle assembly in the valve body of the fuel injector in the combustion chamber side nozzle needle seat with a first closing speed. Will be another, switchable high-pressure side inlet activated, flows in a substantially doubled volume in the control chamber of the fuel injector, so that a faster pressure build-up in this and thus a faster closing of the nozzle needle is adjusted in the combustion chamber side seat. By the second, compared to the first nozzle speed higher closing speed, ie closing speed of the injectors at the combustion chamber side opening of the injector, can be a well-defined end of the injection process bring about, so that a soot formation in the combustion chamber is effectively prevented towards the end of the running in this combustion process.

Bei der Ausführungsform des der Erfindung zugrundeliegenden Gedankens wirkt die dem Steuerraum jeweils zugeordnete permanente Drossel bei Druckentlastung des Steuerraumes in Ablaufrichtung des Kraftstoffes leckagereduzierend; das im Entlastungskanal des Steuerraums vorgesehene Drosselelement wirkt - in entgegengesetzte Richtung, d.h. in Zulaufrichtung auf den Steuerraum gesehen hin - als Zulaufdrossel für den Steuerraum.In the embodiment of the underlying idea of the invention, the control chamber respectively associated permanent throttle pressure relief of the control chamber in the direction of flow of the fuel acts Leckagagereduzierend; the throttling element provided in the discharge passage of the control space acts - in the opposite direction, i.e., in the opposite direction. seen in the direction of supply to the control room out - as inlet throttle for the control room.

Der Ventilkörper des Schaltventils lässt sich in eine den zuschaltbaren hochdruckseitigen Zulauf zum Steuerraum freigebende oder eine diese verschließende Position bringen. Dadurch lässt sich der Düsennadel-/Stößel-Anordnung im Injektorkörper eine erste oder eine zweite Verschließgeschwindigkeit aufprägen, mit welcher die brennraumseitigen Einspritzöffnungen am Injektorkörper verschlossen werden.The valve body of the switching valve can be in a switchable high-pressure side feed to the control room releasing or bring this closing position. As a result, the nozzle needle / plunger arrangement in the injector body can be given a first or a second closing speed with which the injection chamber-side injection openings on the injector body are closed.

Zeichnungdrawing

Anhand der Zeichnung wird die Erfindung nachstehend näher erläutert.Reference to the drawings, the invention will be explained in more detail below.

Es zeigt:

Figur 1
eine erste Injektorbauform mit am Ventilraum des Schaltventils mündenden, permanent wirksamen hochdruckseitigen Zulauf,
It shows:
FIG. 1
a first injector with opening on the valve chamber of the switching valve, permanently effective high-pressure side inlet,

Ausführungsformembodiment

Figur 1 ist eine Injektorbauform mit am Ventilraum des Schaltventils mündenden, permanent wirksamen hochdruckseitigen Zulauf zu entnehmen. FIG. 1 is an injector with opening on the valve chamber of the switching valve, permanently effective high-pressure side inlet can be seen.

Ein Injektorkörper 1 eines Kraftstoffinjektors zum Einspritzen von Kraftstoff in den Brennraum einer Verbrennungskraftmaschine umfasst einen Steuerraum 2. Der Steuerraum 2 ist von einer Steuerraumwandung 3, einer Steuerraumfläche 4 sowie einer Stirnfläche 8 einer Düsennadel-/Stößel-Anordnung 6 begrenzt. Im Bereich der Steuerraumfläche 4 ist, eine Ablauf-/Zulauföffnung 9 umgebend, eine ringförmig konfigurierte Anschlagfläche 5 ausgebildet. Bei der Düsennadel-/Stößel-Anordnung 6 kann es sich sowohl um eine unmittelbar die Einspritzöffnungen am brennraumseitigen Ende des Injektorkörpers 1 verschliessende bzw. freigebende Düsennadel als auch um eine mittelbare eine Düsennadel betätigenden Stößel handeln. Je nach Druckniveau im Steuerraum 2, welches auf die diesem zugewandte Steuerfläche 8 der Düsennadel-/Stößel-Anordnung 6 einwirkt, wird der Düsennadel-/Stößel-Anordnung 6 eine Bewegung gemäß des Doppelpfeiles 7 im Injektorkörpers 1 des Kraftstoffinjektors aufgeprägt.An injector body 1 of a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a control chamber 2. The control chamber 2 is delimited by a control chamber wall 3, a control chamber surface 4 and an end face 8 of a nozzle needle / plunger arrangement 6. In the area of the control chamber area 4, an outlet / inlet opening 9 surrounding a ring-shaped configured stop surface 5 is formed. The nozzle needle / tappet arrangement 6 can be either a nozzle needle closing or releasing the injection openings at the combustion chamber end of the injector body 1, and also an indirect tappet actuating tappet. Depending on the pressure level in the control chamber 2, which acts on this facing control surface 8 of the nozzle needle / plunger assembly 6, the nozzle needle / plunger assembly 6 is imparted a movement according to the double arrow 7 in the injector body 1 of the fuel injector.

Über einen Strömungskanal 10 steht der druckentlastbare bzw. druckbeaufschlagbare, die Düsennadel-/Stößel-Anordnung 6 betätigende Steuerraum 2 in Verbindung mit einem Ventilraum 18 eines Schaltventiles 16, welches bevorzugt als Mehrwegeventil ausgebildet ist. Der Strömungskanal 10 ist in einem Querschnitt 15 ausgebildet; in den Strömungskanal 10 ist ein erstes Drosselelement 13 eingelassen. Das erste Drosselelement 13 ist in einem wesentlich geringeren Querschnitt 14 ausgebildet im Vergleich zur Querschnittsfläche 15 des Strömungskanales 10. Der in Fig. 1 dargestellte Strömungskanal 10 ist sowohl in Zulaufrichtung 11 des Kraftstoffs zum Steuerraum 2 hin als auch entgegengesetzt dazu in Ablaufrichtung 12 des Kraftstoffes vom Steuerraum 2 zum Ventilraum 18 des Schaltventils 16 beaufschlagbar.Via a flow channel 10 is the pressure-relieved or pressurizable, the nozzle needle / plunger assembly 6 actuated control chamber 2 in conjunction with a valve chamber 18 of a switching valve 16, which is preferably designed as a multi-way valve. The flow channel 10 is formed in a cross section 15; in the flow channel 10, a first throttle element 13 is inserted. The first throttle element 13 is formed in a substantially smaller cross section 14 in comparison to the cross sectional area 15 of the flow channel 10 Fig. 1 illustrated flow channel 10 is acted upon both in the inlet direction 11 of the fuel to the control chamber 2 and opposite thereto in the flow direction 12 of the fuel from the control chamber 2 to the valve chamber 18 of the switching valve 16.

Das Schaltventil 16, bevorzugt ausgestaltet als ein Mehrwegeschaltventil, ist ebenfalls im Injektorkörper 1 integriert. Das Schaltventil 16 umfasst einen Ventilkörper 17, der von einem Ventilraum 18 im Injektorkörper 1 umgeben ist. Einander gegenüberliegend sind am Ventilraum ein erster Ventilsitz 19 und ein zweiter Ventilsitz 20 ausgebildet. Der Ventilkörper 17 des Schaltventils 16 wird bevorzugt als kugelförmig konfigurierter Ventilkörper ausgebildet und über ein hier schematisch angedeutetes Übertragungselement 22 betätigt. Das Übertragungselement 22 steht in Wirkverbindung mit einem hier nicht näher dargestellten Aktor, sei es ein Piezoaktor oder ein mechanisch-hydraulischer Übersetzer, welcher dem Übertragungselement 22 eine Vertikalbewegung entsprechendes Doppelpfeiles 23 aufprägt, wodurch der Ventilkörper 17 des Schaltventils 16 entsprechend in den ersten Ventilsitz 19 bzw. dem zweiten Ventilsitz 20 stellbar ist. Im oberen Bereich des Ventilraumes ist zwischen der Wandung des Injektorkörpers 1 und der Aussenfläche des Übertragungselementes 22 ein Ringspalt 21 ausgebildet, von dem an einer Abzweigstelle 25 ein sich in den Niederdruckbereich des Kraftstoffeinspritzsystems erstreckender Ablauf 24 ausgebildet ist.The switching valve 16, preferably designed as a multi-way switching valve, is likewise integrated in the injector body 1. The switching valve 16 comprises a valve body 17 which is surrounded by a valve chamber 18 in the injector body 1. Opposite one another, a first valve seat 19 and a second valve seat 20 are formed on the valve space. The valve body 17 of the switching valve 16 is preferably formed as a spherically configured valve body and actuated via a transmission element 22 schematically indicated here. The transmission element 22 is in operative connection with an actuator not shown here, be it a piezoelectric actuator or a mechanical-hydraulic translator, which the transmission element 22 a vertical movement corresponding double arrow 23 imparts, whereby the valve body 17 of the switching valve 16 respectively in the first valve seat 19 and ., the second valve seat 20 is adjustable. In the upper region of the valve space is between the wall of the injector body 1 and the outer surface the transmission element 22, an annular gap 21 is formed, from which at a branch point 25 is formed in the low pressure region of the fuel injection system extending drain 24.

Senkrecht zur Betätigungsrichtung 23 des Ventilkörpers 17 mündet in den Ventilraum 18 des Schaltventiles 16 ein permanent wirkender hochdruckseitiger Zulauf 28, in dessen Leitungsquerschnitt ein zweites Drosselelement 26 integriert wird. Da dieser hochdruckseitige Zulauf senkrecht zur Betätigungsrichtung des Ventilkörpers 17 im Ventilraum 18 orientiert ist, wird der permanent wirkende hochdruckseitige Zulauf 28 bei Betätigung des Ventilkörpers 17 des Schaltventiles 16 nicht verschlossen, so dass der dort anstehende Druck permanent am Strömungskanal 10 und damit im Steuerraum 2 ansteht.Perpendicular to the direction of actuation 23 of the valve body 17 opens into the valve chamber 18 of the switching valve 16 is a permanently acting high-pressure side inlet 28, in the line cross section, a second throttle element 26 is integrated. Since this high-pressure side inlet is oriented perpendicular to the actuation direction of the valve body 17 in the valve chamber 18, the permanently acting high-pressure side inlet 28 is not closed upon actuation of the valve body 17 of the switching valve 16, so that the pending there pressure permanently on the flow channel 10 and thus in the control chamber 2 is present ,

Im unteren Bereich des Ventilraumes 18, dem Übertragungselement 22 gegenüberliegend, mündet im Bereich des zweiten Ventilsitzes 20 unterhalb des im Ventilraum 18 verstellbaren Ventilkörpers 17 ein weiterer hochdruckseitiger Zulauf 29 von einer hier nicht dargestellten Hochdruckquelle, sei es eine Hochdruckpumpe oder ein Hochdrucksammelraum (Common Rail) mit integriertem dritten Drosselelement 27. Dieser weitere, hochdruckseitige Zulauf ist bei in den zweiten Ventilsitz 20 gestellten Ventilkörper 17 verschlossen, so dass der Steuerraum 2 in Zulaufrichtung 11 lediglich über die in den Ventilraum 18 des Schaltventiles 16 mündende, permanent wirkende hochdruckseitigen Zulauf 28 mit Steuervolumen beaufschlagt wird.In the lower region of the valve chamber 18, the transmission element 22 opposite, opens in the region of the second valve seat 20 below the adjustable in the valve chamber 18 valve body 17, another high pressure side inlet 29 from a high pressure source, not shown here, be it a high-pressure pump or a high-pressure accumulator (common rail) with integrated third throttle element 27. This further, high-pressure side inlet is closed when placed in the second valve seat 20 valve body 17, so that the control chamber 2 in the inlet direction 11 only via the opening into the valve chamber 18 of the switching valve 16, permanently acting high pressure side inlet 28 with control volume is charged.

Gemäss der in Fig. 1 dargestellten Ausführungsform des der Erfindung zugrundeliegenden Gedankens erfolgt eine Druckentlastung des Steuerraumes 2 bei in den zweiten Ventilsitz 20 gestellten Ventilkörper 17 des Schaltventiles 16 in Ablaufrichtung 12 des Kraftstoffes aus dem Steuerraum 2. Das in den Strömungskanal 10 integrierte erste Drosselelement 13 wirkt hierbei als Ablaufdrossel Eine Druckbeaufschlagung des Steuerraumes 2 via Strömungskanal 10 kann gemäß der Ausführungsform in Fig. 1 entweder über den den Ventilraum 18 permanent beaufschlagenden hochdruckseitigen Zulauf 28 mit zweitem Drosselelement 26 erfolgen, so daß sich in Zulaufrichtung 11 des Kraftstoffs im Strömungskanal 10 über die dann als Zulaufdrosselelement wirkende erste Drossel 13 ein Druckaufbau im Steuerraum 2 einstellt. Es stellt sich bei Druckbeaufschlagung des Steuerraumes 2 über den permanent wirkenden hochdruckseitigen Zulauf 28 eine erste Druclcanstiegsgeschwindigkeit 2 in diesen und damit eine erste Düsennadelschließgeschwindigkeit ein. Wird der Ventilkörper 17 des Schaltventiles 16 hingegen in seinen ersten Ventilsitz 19 gestellt, erfolgt eine Druckbeaufschlagung des Strömungskanales 10 sowohl über den permanent wirkenden hochdruckseitigen Zulauf 28 sowie über den weiteren hochdruckseitigen Zulauf 29 mit in diesem integriertem dritten Drosselelement 27. Demzufolge stellt sich im Strömungskanal 10 in Zulaufrichtung 11 auf den Steuerraum 2 durch Parallelschaltung der beiden Zuläufe 28, 29 eine höhere Druckanstiegsgeschwindigkeit im Steuerraum 2, d.h. eine höhere Schließgeschwindigkeit der Düsennadel 6 und damit ein schnelleres Schließen der Einspritzöffnungen am brennraumseitigen Ende des Ventilkörpers 1 ein.According to the in Fig. 1 illustrated embodiment of the invention, the underlying idea is a pressure relief of the control chamber 2 when placed in the second valve seat 20 valve body 17 of the switching valve 16 in flow direction 12 of the fuel from the control chamber 2. The integrated into the flow channel 10 first throttle element 13 acts here as a drain throttle A pressurization of the control chamber 2 via flow channel 10 can according to the embodiment in Fig. 1 either via the valve space 18 permanently acting on the high-pressure side inlet 28 with second throttle element 26 done so that adjusts a pressure build-up in the control chamber 2 in the inlet direction 11 of the fuel in the flow channel 10 via the then acting as inflow throttle element first throttle 13. When pressure is applied to the control chamber 2 via the permanently acting high-pressure side inlet 28, a first pressure rise speed 2 occurs in the latter and thus a first nozzle needle closing speed. If the valve body 17 of the switching valve 16, however, placed in its first valve seat 19, there is a Pressurization of the flow channel 10 both via the permanently acting high-pressure side inlet 28 and the other high-pressure side inlet 29 with this third integrated throttle element 27. Consequently, in the flow channel 10 in the inlet direction 11 to the control chamber 2 by parallel connection of the two inlets 28, 29 a higher Pressure rise speed in the control chamber 2, ie a higher closing speed of the nozzle needle 6 and thus a faster closing of the injection openings at the combustion chamber end of the valve body 1 a.

Claims (5)

  1. Fuel injector for direct-injection internal combustion engines having an injector body (1) which comprises a control space (2), by means of the pressurization/pressure release of which a nozzle-needle/plunger arrangement (6) in the injector body (1) can be actuated, with it being possible for the control space (2) to be relieved of pressure via a flow duct (10) with a first throttle element (13) and with the control space (2) being connected via a high-pressure-side permanently acting inlet (28) with a second throttle element (26) to a high pressure source and with a switching valve (16) being held in the injector body (1), which switching valve (16) is connected by means of the flow duct (10) to the control space (2), with it being possible, for building up pressure in the control space (2) by means of the switching valve (16), for a further high-pressure-side inlet (29) with a third throttle element (27) to be connected in parallel with the permanently acting high-pressure-side inlet (28), with the opening-out point of the further high-pressure-side inlet (29) opening out in a valve space (18) of the switching valve (16) and being aligned, on a seat (20) of a valve body (17), in the actuating direction (23) of the valve body (17), characterized in that the permanently acting high-pressure-side inlet (28) opens out in a valve space (18) of the switching valve (16).
  2. Fuel injector according to Claim 1, characterized in that the flow duct (10) which connects the control space (2) and a valve space (18) of the switching valve (16) can be acted on in the inflow direction (11) of the fuel to the control space (2) or in the outflow direction (12) of the fuel from the control space (2) to the valve space (18).
  3. Fuel injector according to Claim 1, characterized in that the permanently acting high-pressure-side inlet (28) in the valve space (18) of the switching valve (16) opens out perpendicularly with respect to the actuating direction (23) of the valve body (17) of the switching valve (16).
  4. Fuel injector according to Claim 1, characterized in that the valve body (17) of the switching valve (16) is of spherical design and can be placed by means of a transmission element (22) into a first valve seat (19) or into a second valve seat (20).
  5. Fuel injector according to Claim 4, characterized in that an annular gap (21) is formed between the transmission element (22) and the injector body (1) at the valve space (18), via which annular gap (21) outflowing control volume flows to an outlet (24) during a pressure release of the control space (2).
EP02758062A 2001-06-29 2002-06-21 Fuel injector with a switchable control chamber feed Expired - Lifetime EP1404964B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10131618 2001-06-29
DE2001131618 DE10131618A1 (en) 2001-06-29 2001-06-29 Fuel injector with switchable control room inlet
PCT/DE2002/002292 WO2003004860A2 (en) 2001-06-29 2002-06-21 Fuel injector with a switchable control chamber feed

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EP1404964A2 EP1404964A2 (en) 2004-04-07
EP1404964B1 true EP1404964B1 (en) 2008-02-13

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EP02758062A Expired - Lifetime EP1404964B1 (en) 2001-06-29 2002-06-21 Fuel injector with a switchable control chamber feed

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DE (2) DE10131618A1 (en)
WO (1) WO2003004860A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007034319A1 (en) * 2007-07-24 2009-01-29 Robert Bosch Gmbh injector

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0976924A2 (en) * 1998-07-31 2000-02-02 Siemens Aktiengesellschaft Servo valve for an injector and injector
DE10055714A1 (en) * 1999-11-10 2001-06-13 Denso Corp Fuel injection valve for vehicle of common rail type, has three way valve and main and secondary apertures to connect channels to high or low pressure lines according to valve position
WO2001088366A1 (en) * 2000-05-18 2001-11-22 Robert Bosch Gmbh Accumulator fuel-injection system for an internal combustion engine

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Publication number Priority date Publication date Assignee Title
AT2110U3 (en) * 1997-06-16 1998-09-25 Avl List Gmbh INJECTION NOZZLE
DE19744518A1 (en) 1997-10-09 1999-04-15 Bosch Gmbh Robert Fuel injection valve for internal combustion engine
DE19910589C2 (en) 1999-03-10 2002-12-05 Siemens Ag Injection valve for an internal combustion engine
JP3557996B2 (en) * 1999-06-21 2004-08-25 トヨタ自動車株式会社 Fuel injection device
JP3551898B2 (en) * 2000-06-15 2004-08-11 トヨタ自動車株式会社 Fuel injection valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0976924A2 (en) * 1998-07-31 2000-02-02 Siemens Aktiengesellschaft Servo valve for an injector and injector
DE10055714A1 (en) * 1999-11-10 2001-06-13 Denso Corp Fuel injection valve for vehicle of common rail type, has three way valve and main and secondary apertures to connect channels to high or low pressure lines according to valve position
WO2001088366A1 (en) * 2000-05-18 2001-11-22 Robert Bosch Gmbh Accumulator fuel-injection system for an internal combustion engine

Also Published As

Publication number Publication date
EP1404964A2 (en) 2004-04-07
WO2003004860A3 (en) 2003-04-17
WO2003004860A2 (en) 2003-01-16
DE50211686D1 (en) 2008-03-27
DE10131618A1 (en) 2003-01-23

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