EP1771651B1 - Fuel injector comprising a direct multi-stage injection valve member control system - Google Patents

Fuel injector comprising a direct multi-stage injection valve member control system Download PDF

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Publication number
EP1771651B1
EP1771651B1 EP05749972A EP05749972A EP1771651B1 EP 1771651 B1 EP1771651 B1 EP 1771651B1 EP 05749972 A EP05749972 A EP 05749972A EP 05749972 A EP05749972 A EP 05749972A EP 1771651 B1 EP1771651 B1 EP 1771651B1
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EP
European Patent Office
Prior art keywords
valve member
fuel injector
injection valve
booster piston
control 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.)
Not-in-force
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EP05749972A
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German (de)
French (fr)
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EP1771651A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve

Definitions

  • high-pressure accumulator injection systems Today, in addition to pump nozzle fuel injection systems, high-pressure accumulator injection systems (common rail) are used on modern self-igniting internal combustion engines.
  • the individual fuel injectors assigned to the cylinders of the internal combustion engine are supplied with fuel from a high-pressure accumulator (common rail).
  • the fuel injectors can be actuated either via solenoid valves or else via piezo actuators. If the fuel injectors are actuated via piezoactuators, an injection valve member which can be actuated directly via the piezoactuator can be realized.
  • the injection valve comprises a valve needle, which is tensioned by a spring located within a spring chamber against a seat surface.
  • the spring is sandwiched between a spring abutment which communicates with the valve needle and a movable stop.
  • the injector further includes a valve including a movable abutment surface, which valve may be actuated during operation of the injector such that fuel may exit the spring chamber at a second, higher rate.
  • the valve is formed by a seating surface formed around an opening communicating with the spring chamber, the movable fence being engageable with the seating so that fuel flow through the opening can be controlled.
  • the movable stop can be designed to be movable under the action of the fuel pressure within a pump chamber.
  • the actuator To be able to open the injection valve member in fuel injectors with direct controllability of the injection valve member via an actuator, the actuator must overcome a high opening force.
  • the high required opening force applied by the actuator is, finds its cause in that the nozzle needle formed injector member with system pressure (pressure level in the high-pressure reservoir common rail) is applied, is pressed into its seat.
  • the force required to open the injection valve member from its seat is on the order of several hundred N, such as about 400 N.
  • Said variables ie the force of several 100 N required to open the injection valve member and the maximum representable stroke of the injection valve member from its fully closed to its fully open position are essentially the determining parameters for the size of a piezoelectric actuator to be integrated into a fuel injector.
  • the length / diameter ratio of the piezoelectric actuator can be varied by integration of a hydraulic ratio, as in the example of FIG DE19500706 A1
  • the size of the actuator also referred to as Aktorvolumen, is substantially proportional to the applied opening force and the maximum stroke to be represented of the needle-shaped injection valve member.
  • the driver engages in a recess of a the piston, which is so dimensioned that the driver takes only from a certain sub-stroke an outer, slidably mounted on an inner booster piston booster piston
  • the gear ratio in the lower Operahub Scheme is by the diameter ratio d 1 to d 2 , ie the diameter ratio between the diameter of the Given the head portion of the injection valve member and the diameter of an internally arranged booster piston, while the effective in the upper Generalhub Scheme the injection valve member gear ratio by the diameter ratio d 1 to d 3 , ie the diameter of the head portion of the injection valve member and the outer diameter of a second booster piston is given over the already mentioned driver is coupled to the first booster piston
  • the single FIGURE shows a section through a fuel injector with a multi-stage controllable directly operated nozzle needle-shaped injection valve member.
  • the figure shows a fuel injector 1, which comprises an injector body 2, an intermediate disk 3 and a nozzle body 4.
  • the injector 2 and the nozzle body 4 are screwed together by means of a nozzle lock nut 5; Before screwing the injector body 2 and the nozzle body 4, the washer 3 is applied to the nozzle body 4, which has at least two flow channels 26 and 40, which will be described in more detail below.
  • the fuel injector 1 comprises a needle-shaped injection valve member 6 which can be configured in one or more parts and with which injection openings (not illustrated in the drawing) formed on the combustion chamber end of the fuel injector 1 can be closed or released.
  • the intermediate disk 3 between the injector body 2 and the nozzle body 4 comprises an upper end face 7 which assigns a lower end face of the injector body 2 and a lower end face 8 which assigns the upper end face of the nozzle body 4.
  • a cavity 9 is formed in the injector body 2 of the fuel injector 1, in which an actuator 39 is formed, for example, as one of a piezocrystal stack constructed piezoelectric actuator can be formed.
  • a fuel inlet 10 opens from a high-pressure accumulator (common rail), not shown in the drawing, in which fuel held at system pressure fuel is stored. Via the fuel inlet 10, this fuel, which is under system pressure (rail pressure), enters the cavity 9 and flows from it along a multistage pressure booster 12 accommodated in the fuel injector 1 to the channel 40 of the intermediate plate and from there into the nozzle body 4.
  • the multistage pressure booster 12 comprises a first booster piston 13 and a second booster piston 14 surrounding and guided on the first booster piston 13.
  • the first booster piston 13, formed in diameter d 2 comprises a groove 30 for a ring-shaped driver 20, which is inserted into a recess 19 of the first booster piston 13 enclosing the second booster piston 14 engages.
  • the recess 19 in the second booster piston 14 is bounded by a first stop side 21 and a second stop side 22.
  • the outer, second booster piston 14 has an end face 16 which is acted upon by a spring element 15 which can be embodied as a spiral spring, which is supported on a support disk 11 formed below the piezoactuator 39, which undergoes a vertical movement when the actuator 39 is energized.
  • the support disk 11 is supported by a tubular spring 17, which is supported with its opposite end of the support disk 11 on the upper plane surface 7 of the washer 3. By means of the tubular spring 17, the support disk 11 is set in its rest position when the energization of the piezocrystal stack of the actuator 39 is canceled.
  • the tubular spring 17 between the support plate 11 and the upper end surface 7 of the washer 3 surrounds a stop sleeve 18.
  • the stop sleeve 18 extends below a shoulder of the second booster piston 14 and surrounds a spring 28, a control chamber 25 defining a first control chamber sleeve 27 to the upper Plane 7 of the washer 3 of the fuel injector 1 hires.
  • the spring 28 is permanently tensioned due to the pressure prevailing in the cavity 9 fuel pressure, so that it is ensured that the first control chamber sleeve 27 is always employed with its formed on the underside biting edge 29 against the upper end surface 7 of the washer 3, so that the control chamber 25 is sealed is.
  • control chamber 25 is acted on the one hand by the upper end face 7 of the intermediate disc 3 and on the other hand both from the end face 23 of the first booster piston 13 and from the end face 24 of the second booster piston 14.
  • the needle-shaped injection valve member 6 arranged below the intermediate disk 3 has a head 31 which is formed in a diameter d 1 .
  • the second booster piston 14 has an outer diameter d 3 , which exceeds both the diameter d 2 of the first booster piston 13 and the head diameter d 1 of the needle-shaped injection valve member 6.
  • the hydraulic space between the lower face 8 of the washer 3 and the upper end of the needle-shaped injection valve member 6 is limited by a second control sleeve 32
  • the second control chamber sleeve 32 is in turn acted upon by a spring 33, which is supported on a support ring 34, for example the designedsff kaue a needle-shaped injection valve member 6 may be shrunk, that is connected by means of a press fit with the lateral surface of the needle-shaped injection valve member 6.
  • the free surfaces 36 can be oriented by 120 °, in the case of the formation of three flow relief surfaces 36 or at an angle of 90 °, in the case of the formation of four flow relief surfaces 36 on the needle-shaped injection valve member 6.
  • the piezocrystal stack of the actuator 39 and pulls together Elongation in the vertical direction decreases. Due to the pre-tensioned tube spring 17, the support plate 11 moves in the vertical direction according to the Reduction of the elongation of the piezocrystal stack of the actuator 39 upwards, so that the first booster piston 13 extends with its the control chamber 25 facing end face 23 from the control chamber 25, whereby there the pressure decreases. Due to the pressure drop in the control chamber 25 and its hydraulic connection to the hydraulic space above the head 31 of the needle-shaped injection valve member 6 also moves the needle-shaped injection valve member 6 upwards and the injection ports are released.
  • the multi-stage pressure intensifier 12 works with a transmission ratio of 1: 1-1.5.
  • the transmission ratio within the sketched sectionhub Symposiumes is defined by the diameter d 1 / d 2 , wherein d 1 denotes the diameter of the head 31 of the needle-shaped injection valve member 6 and d 2 denotes the outer diameter of the first booster piston 13 of the multistage pressure booster 12. Due to the effective in this Sectionhub Scheme gear ratio of 1: 1-1.5 can be done quickly, precisely and stably opening the injection ports formed at the combustion chamber end of the fuel injector 1.
  • the multistage pressure intensifier now operates with a second transmission ratio of 1: 4 -7, which is defined by the diameter ratio of d 1 / d 3 .
  • d 1 is - as already mentioned above - the head diameter of the head 31 of the needle-shaped injection valve member 6 denotes, while d 3 denotes the outer diameter of the first booster piston 13 displaceably movable second booster piston 14. Due to the exceeding of the stroke h 1 together from the control chamber 25 extending end faces 23 and 24, the pressure in the control chamber 25 decreases faster compared to the state in which only the end face 23 of the first booster piston 13 extends out of the control chamber 25. Due to this, a complete actuator needle opening can achieve complete opening of the needle-shaped injection valve member 6 by moving a larger hydraulic surface (23 +24), which is important in the full load range of the internal combustion engine.
  • the crystal stack of the piezoelectric actuator 39 is energized again, then an elongation of this crystal stack corresponding to the energization level of the piezocrystal stack sets in, whereby the support disk 11 is compressed against the action of the tubular spring 17, which is supported on the upper planar surface 7 of the intermediate disk 3.
  • the tube spring 17 surrounds the stop sleeve 18, which in turn engages with its upper edge a paragraph on the outer circumference of the second booster piston 14 and define its basic position.
  • the inner, first booster piston 13 is moved with its end face 23 into the control chamber 25 and, as soon as the underside of the driver 20 on the second stop side 22 of FIG Recess 19 abuts - and the second booster piston 14 moves to its normal position, which is defined by the stop sleeve 18, which is also supported on the upper end face 7 of the washer 3
  • the fuel flows via the channel 40 into the nozzle body 4 and enters via the provided at the periphery of the needle-shaped injection valve member 6 free surface 36 in an annular gap 37 which is defined between the outer periphery of the needle-shaped injection valve member 6 and the inside of the nozzle body
  • Fuel volume flowing in the flow direction 38 flows to the injection openings formed at the combustion chamber end of the fuel injector 1 and, via this, when the injection valve member 6 is open or only partially opened, enters the combustion chamber of the self-igniting internal combustion engine.
  • the proposed solution according to the invention is characterized in particular by the fact that in the first Generalhub Scheme of the needle-shaped injection valve member 6 opening the needle-shaped injection valve member with a high rigidity, effected by the small ratio of 1: 1-1.5, realized between Aktorhub and Einspritzvenhlglied can be. Accordingly, the following in the first Generalhub Scheme the injection valve member opening of the combustion chamber side arranged injection openings is controlled, ie occurring due to rapid opening of the needle-shaped injection valve member 6 occurring Volume jumps with regard to the amount of fuel introduced into the combustion chamber are avoided, so that the production of soot during combustion drops to a considerable extent.

Abstract

A fuel injector having an injection valve member for injecting fuel into the combustion chamber of an autoignition internal combustion engine. The injection valve member is directly controllable by means of an actuator that directly actuates a pressure booster, which is able to influence the pressure in a control chamber that acts on the injection valve member. The pressure booster has a first booster piston and a second booster piston coupled to each other by means of a driver that is able to move between a first stop side and a second stop side inside a recess.

Description

Technisches GebietTechnical area

An modernen, selbstzündenden Verbrennungskmftmaschinen kommen heute neben PumpeDüse-Kraftstoffeinspritzsystemen auch Hochdruckspeichereinspritzsystem (common rail) zum Einsatz. Bei Hochdruckspeichereinspritzsystemen werden die einzelnen, den Zylindern der Verbrennungskraftmaschine jeweils zugeordneten Kraftstoffinjektoren von einem Hochdruckspeicher (common rail) aus mit Kraftstoff versorgt Die Kraftstoffinjektoren können entweder über Magnetventile oder aber über Piezoaktoren betätigt werden. Werden die Kraftstoffinjektoren über Piezoaktoren betätigt, so lässt sich ein unmittelbar über den Piezoaktor betätigbares Einspritzventilglied realisieren.Today, in addition to pump nozzle fuel injection systems, high-pressure accumulator injection systems (common rail) are used on modern self-igniting internal combustion engines. In the case of high-pressure accumulator injection systems, the individual fuel injectors assigned to the cylinders of the internal combustion engine are supplied with fuel from a high-pressure accumulator (common rail). The fuel injectors can be actuated either via solenoid valves or else via piezo actuators. If the fuel injectors are actuated via piezoactuators, an injection valve member which can be actuated directly via the piezoactuator can be realized.

Stand der TechnikState of the art

Aus DE 697 20 145 C2 ist ein Einspritzventilglied bekannt. Das Einspritzventil umfasst eine Ventilnadel, die durch eine innerhalb einer Federkammer befindlich Feder gegen eine Sitzfläche gespannt ist. Die Feder ist zwischen einem Feder-Widerlager, welches mit der Ventilnadel in Verbindung steht und einem beweglichen Anschlag eingebettet. Es ist ein verengter Durchflussweg vorgesehen, durch den Kraftstoff mit einer beschränkten Geschwindigkeit bzw. in beschränkter Menge aus der Federkammer fließen kann. Das Einspritzventil weist ferner ein Ventil unter Einschluss einer beweglichen Anschlagsfläche auf, wobei dieses Ventil während des Betriebs des Einspritzventils derart betätigt werden kann, dass Kraftstoff mit einer zweiten, höheren Geschwindigkeit bzw. Menge aus der Federkammer austreten kann. Das Ventil wird durch eine Sitzfläche gebildet, die rund um eine mit der Federkammer kommunizierende Öffnung ausgebildet ist, wobei der bewegliche Anschlag mit der Sitzfläche in Anlage kommen kann, so dass sich der Kraftstofffluss durch die Öffnung steuern lässt. Der bewegliche Anschlag kann unter Einwirkung des Kraftstoffdruckes innerhalb eines Pumpenraumes bewegbar ausgebildet werden.Out DE 697 20 145 C2 an injection valve member is known. The injection valve comprises a valve needle, which is tensioned by a spring located within a spring chamber against a seat surface. The spring is sandwiched between a spring abutment which communicates with the valve needle and a movable stop. There is a restricted flow path through which fuel can flow from the spring chamber at a limited rate or in a limited amount. The injector further includes a valve including a movable abutment surface, which valve may be actuated during operation of the injector such that fuel may exit the spring chamber at a second, higher rate. The valve is formed by a seating surface formed around an opening communicating with the spring chamber, the movable fence being engageable with the seating so that fuel flow through the opening can be controlled. The movable stop can be designed to be movable under the action of the fuel pressure within a pump chamber.

Um bei Kraftstoffinjektoren mit direkter Ansteuerbarkeit des Einspritzventilgliedes über einen Aktor das Einspritzventilglied öffnen zu können, muss der Aktor eine hohe Öffnungskraft überwinden. Die hohe erforderliche Öffnungskraft, die durch den Aktor aufzubringen ist, findet ihre Ursache darin, dass das düsennadelförmig ausbildbare Einspritzventilglied mit Systemdruck (Druckniveau im Hochdruckspeicherraum common rail) beaufschlagt, in seinen Sitz gedrückt wird. Die zum Öffnen des Einspritzventilgliedes aus seinem Sitz erforderliche Kraft liegt in der Größenordnung von mehreren hundert N, so z.B. bei etwa 400 N. Um für einen ausreichenden Kraftstofffluss bei vollständig geöffnetem Einspritzventilglied durch die Einspritzöffnungen in den Brennraum einer selbstzündenden Verbrennungskraftmaschine zu sorgen, ist es außerdem erforderlich, dass das Einspritzventilglied einen maximalen Hubweg von mehreren 100 µm, so z.B. in der Größenordnung zwischen 200 µm und 300 µm, ausführt. Die genannten Größen, d.h. die zum Öffnen des Einspritzventilgliedes erforderliche Kraft von mehreren 100 N sowie der maximal darstellbare Hubweg des Einspritzventilgliedes von seiner vollständig geschlossenen in seine vollständige geöffnete Position sind im Wesentlichen die bestimmenden Parameter für die Größe eines in einen Kraftstoffinjektor zu integrierenden Piezoaktors. Zwar lässt sich durch Integration einer hydraulischen Übersetzung das Längen-/Durchmesser-Verhältnis des Piezoaktors variieren wie zum beispiel in der DE19500706 A1 , jedoch ist die Baugröße des Aktors, auch als Aktorvolumen bezeichnet, im Wesentlichen proportional zur aufzubringenden Öffnungskraft und dem darzustellenden maximalen Hubweg des nadelförmig ausbildbaren Einspritzventilgliedes.To be able to open the injection valve member in fuel injectors with direct controllability of the injection valve member via an actuator, the actuator must overcome a high opening force. The high required opening force applied by the actuator is, finds its cause in that the nozzle needle formed injector member with system pressure (pressure level in the high-pressure reservoir common rail) is applied, is pressed into its seat. The force required to open the injection valve member from its seat is on the order of several hundred N, such as about 400 N. In order to ensure sufficient fuel flow at fully open injection valve member through the injection openings in the combustion chamber of a self-igniting internal combustion engine, it is also required that the injection valve member a maximum stroke of several 100 microns, for example in the order of 200 microns to 300 microns, performs. Said variables, ie the force of several 100 N required to open the injection valve member and the maximum representable stroke of the injection valve member from its fully closed to its fully open position are essentially the determining parameters for the size of a piezoelectric actuator to be integrated into a fuel injector. Although the length / diameter ratio of the piezoelectric actuator can be varied by integration of a hydraulic ratio, as in the example of FIG DE19500706 A1 However, the size of the actuator, also referred to as Aktorvolumen, is substantially proportional to the applied opening force and the maximum stroke to be represented of the needle-shaped injection valve member.

Bei aus dem Stand der Technik bekannten Lösungen ist die hohe erforderliche Übersetzung von 1:3-4 von Nachteil, die notwendig ist, um den Hub des Einspritzventilgliedes in den erforderlichen Grenzen zu steuern, da aufgrund des hohen Übersetzungsverhältnisses die Baugröße eines Piezoaktors erheblich ansteigt.In solutions known from the prior art, the high required ratio of 1: 3-4 disadvantageous, which is necessary to control the stroke of the injection valve member in the required limits, since due to the high transmission ratio, the size of a piezoelectric actuator increases significantly.

Darstellung der ErfindungPresentation of the invention

Erfindungsgemäß wird vorgeschlagen, durch eine mehrstufige, beispielsweise eine zweistufige Übersetzung eine Ansteuerungsmöglichkeit für ein Einspritzventilglied bereitzustellen, die die vorstehend aufgeführten Nachteile vermeidet Durch die erfindungsgemäße Lösung kann eine Einspritzverlaufsformung dargestellt werden, die sich im unteren Teilhubbereich des Einspritzventilgliedes durch eine 1:1-1,5-fache Übersetzung auszeichnet und dadurch eine präzise schnelle und insbesondere stabile Ansteuerungsmöglichkeit bietet. Im oberen Hubbereich des Einspritzventilgliedes verläuft das Übersetzungsverhältnis auf einem höheren Niveau, so z.B. 1:4-7.According to the invention, it is proposed to provide a control possibility for an injection valve member by a multi-stage, for example, a two-stage translation, which avoids the disadvantages listed above. By the solution according to the invention, a Einspritzverlaufsformung be represented in the lower Teilhubbereich the injection valve member by a 1: 1-1, 5-fold translation and thus provides a precise fast and particularly stable control option. In the upper stroke range of the injection valve member, the gear ratio is at a higher level, e.g. 1: 4-7.

Die Aufteilung des Übersetzungsverhältnisses für einen unteren Teilhubbereich des Einspritzventilgliedes und für den oberen Teilhubbereich des Einspritzventilgliedes kann in vorteilhafter Weise dadurch realisiert werden, dass ein mehrstufig ausgebildeter Druckübersetzer innerhalb eines Kraftstoffinjektors zwei ineinander geführte Kolben umfasst, die miteinander über einen Mitnehmer gekoppelt sind. Der Mitnehmer greift in eine Ausnehmung eines der Kolben ein, welche so bemessen ist, dass der Mitnehmer erst ab einem bestimmten Teilhub einen äußeren, an einem inneren Übersetzerkolben verschieblich gelagerten Übersetzerkolben mitnimmt Das Übersetzungsverhältnis im unteren Teilhubbereich ist durch das Durchmesserverhältnis d1 zu d2, d.h. das Durchmesserverhältnis zwischen dem Durchmesser des Kopfbereiches des Einspritzventilgliedes und dem Durchmesser eines innenliegend angeordneten Übersetzerkolbens gegeben, während das im oberen Teilhubbereich des Einspritzventilgliedes wirksame Übersetzungsverhältnis durch das Durchmesserverhältnis d1 zu d3, d.h. dem Durchmesser des Kopfbereiches des Einspritzventilgliedes und dem Außendurchmesser eines zweiten Übersetzerkolbens gegeben ist, der über den bereits erwähnten Mitnehmer mit dem ersten Übersetzerkolben gekoppelt istThe division of the transmission ratio for a lower Teilhubbereich the injection valve member and the upper Teilhubbereich the injection valve member can be realized in an advantageous manner that a multi-stage trained pressure intensifier within a fuel injector comprises two pistons guided into each other, which are coupled together via a driver. The driver engages in a recess of a the piston, which is so dimensioned that the driver takes only from a certain sub-stroke an outer, slidably mounted on an inner booster piston booster piston The gear ratio in the lower Teilhubbereich is by the diameter ratio d 1 to d 2 , ie the diameter ratio between the diameter of the Given the head portion of the injection valve member and the diameter of an internally arranged booster piston, while the effective in the upper Teilhubbereich the injection valve member gear ratio by the diameter ratio d 1 to d 3 , ie the diameter of the head portion of the injection valve member and the outer diameter of a second booster piston is given over the already mentioned driver is coupled to the first booster piston

Zeichnungdrawing

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

Die einzige Figur zeigt einen Schnitt durch einen Kraftstoffinjektor mit einem mehrstufig ansteuerbaren direkt betätigten düsennadelförmigen Einspritzventilglied.The single FIGURE shows a section through a fuel injector with a multi-stage controllable directly operated nozzle needle-shaped injection valve member.

Ausführungsvariantenvariants

Der Figur ist ein Kraftstoffinjektor 1 zu entnehmen, der einen Injektorkörper 2, eine Zwischenscheibe 3 und einen Düsenkörper 4 umfasst. Der Injektor 2 und der Düsenkörper 4 sind mittels einer Düsenspannmutter 5 miteinander verschraubt; vor der Verschraubung von Injektorkörper 2 und Düsenkörper 4 wird auf den Düsenkörper 4 die Zwischenscheibe 3 aufgebracht, die mindestens zwei Strömungskanäle 26 bzw. 40 aufweist, die nachfolgend noch eingehender beschrieben werden.The figure shows a fuel injector 1, which comprises an injector body 2, an intermediate disk 3 and a nozzle body 4. The injector 2 and the nozzle body 4 are screwed together by means of a nozzle lock nut 5; Before screwing the injector body 2 and the nozzle body 4, the washer 3 is applied to the nozzle body 4, which has at least two flow channels 26 and 40, which will be described in more detail below.

Der Kraftstoffinjektor 1 umfasst daneben ein nadelförmig ausgebildetes ein- oder mehrteilig konfigurierbares Einspritzventilglied 6, mit welchem in der Zeichnung nicht dargestellte, am brennraumseitigen Ende des Kraftstoffinjektors 1 ausgebildete Einspritzöffnungen verschließbar bzw. freigebbar sind.In addition, the fuel injector 1 comprises a needle-shaped injection valve member 6 which can be configured in one or more parts and with which injection openings (not illustrated in the drawing) formed on the combustion chamber end of the fuel injector 1 can be closed or released.

Die Zwischenscheibe 3 zwischen dem Injektorkörper 2 und dem Düsenkörper 4 umfasst eine obere Planfläche 7, die einer unteren Planfläche des Injektorkörpers 2 zuweist sowie eine untere Planfläche 8, die der oberen Planfläche des Düsenkörpers 4 zuweist.The intermediate disk 3 between the injector body 2 and the nozzle body 4 comprises an upper end face 7 which assigns a lower end face of the injector body 2 and a lower end face 8 which assigns the upper end face of the nozzle body 4.

Im Injektorkörper 2 des Kraftstoffinjektors 1 ist darüber hinaus ein Hohlraum 9 ausgebildet, in welchem ein Aktor 39 ausgebildet ist, der beispielsweise als ein aus einem Piezokristallstapel aufgebauter Piezoaktor ausgebildet sein kann. In den Hohlraum 9 mündet ein Kraftstoffzulauf 10 von einem in der Zeichnung nicht dargestellten Hochdruckspeicher (common rail), in welchem auf Systemdruck gehaltener Kraftstoff bevorratet wird. Über den Kraftstoffzulauf 10 tritt dieser unter Systemdruck (Rail-Druck) stehende Kraftstoff in den Hohlraum 9 ein und strömt von diesem entlang eines im Kraftstoffinjektor 1 aufgenommenen mehrstufigen Druckübersetzers 12 dem Kanal 40 der Zwischenscheibe zu und von dort in den Düsenkörper 4.In addition, a cavity 9 is formed in the injector body 2 of the fuel injector 1, in which an actuator 39 is formed, for example, as one of a piezocrystal stack constructed piezoelectric actuator can be formed. In the cavity 9, a fuel inlet 10 opens from a high-pressure accumulator (common rail), not shown in the drawing, in which fuel held at system pressure fuel is stored. Via the fuel inlet 10, this fuel, which is under system pressure (rail pressure), enters the cavity 9 and flows from it along a multistage pressure booster 12 accommodated in the fuel injector 1 to the channel 40 of the intermediate plate and from there into the nozzle body 4.

Im Hohlraum 9 des Kraftstoffinjektors 1 ist der mehrstufig ausgebildete Druckübersetzer 12 angeordnet. Der mehrstufige Druckübersetzer 12 umfasst einen ersten Übersetzerkolben 13 sowie einen den ersten Übersetzerkolben 13 umschließenden und an diesem geführten zweiten Übersetzerkolben 14. Der erste Übersetzerkolben 13, ausgebildet im Durchmesser d2 umfasst eine Nut 30 für einen ringförmig ausgebildeten Mitnehmer 20, der in eine Ausnehmung 19 des den ersten Übersetzerkolben 13 umschließenden zweiten Übersetzerkolbens 14 eingreift. Die Ausnehmung 19 im zweiten Übersetzerkolben 14 ist durch eine erste Anschlagseite 21 sowie eine zweite Anschlagseite 22 begrenzt.In the cavity 9 of the fuel injector 1 of the multistage pressure intensifier 12 is arranged. The multistage pressure booster 12 comprises a first booster piston 13 and a second booster piston 14 surrounding and guided on the first booster piston 13. The first booster piston 13, formed in diameter d 2, comprises a groove 30 for a ring-shaped driver 20, which is inserted into a recess 19 of the first booster piston 13 enclosing the second booster piston 14 engages. The recess 19 in the second booster piston 14 is bounded by a first stop side 21 and a second stop side 22.

Der äußere, zweite Übersetzerkolben 14 weist eine Stirnfläche 16 auf, die von einem als Spiralfeder ausbildbaren Federelement 15 beaufschlagt wird, welches sich an einer unterhalb des Piezoaktor 39 ausgebildeten Stützscheibe 11 abstützt, die bei Bestromung des Aktors 39 eine Vertikalbewegung erfährt. Die Stützscheibe 11 ist über eine Rohrfeder 17 abgestützt, welche sich mit ihrem der Stützscheibe 11 gegenüberliegenden Ende auf der oberen Planfläche 7 der Zwischenscheibe 3 abstützt. Mittels der Rohrfeder 17 wird die Stützscheibe 11 in ihre Ruhelage gestellt, wenn die Bestromung des Piezokristallstapels des Aktors 39 aufgehoben wird. Die Rohrfeder 17 zwischen der Stützscheibe 11 und der oberen Planfläche 7 der Zwischenscheibe 3 umgibt eine Anschlaghülse 18. Die Anschlaghülse 18 erstreckt sich unterhalb eines Absatzes des zweiten Übersetzerkolbens 14 und umschließt eine Feder 28, die eine einen Steuerraum 25 begrenzende erste Steuerraumhülse 27 an die obere Planfläche 7 der Zwischenscheibe 3 des Kraftstoffinjektors 1 anstellt. Die Feder 28 ist permanent aufgrund des im Hohlraum 9 herrschenden Kraftstoffdruckes gespannt, so dass sichergestellt ist, dass die erste Steuerraumhülse 27 mit ihrer an deren Unterseite ausgebildeten Beißkante 29 stets gegen die obere Planfläche 7 der Zwischenscheibe 3 angestellt ist, so dass der Steuerraum 25 abgedichtet ist. Vom Steuerraum 25 strömt der in diesem enthaltene Kraftstoff und entsprechend der Einfahrbewegung des ersten Übersetzerkolbens 13 bzw. des zweiten Übersetzerkolbens 14 oder beider Kolben in den Steuerraum 25 entsprechend verdichtet über den Kanal 26 ein unterhalb der unteren Planfläche 8 der Zwischenscheibe 3 liegenden hydraulischen Raum zu, der einen Kopf 31 des nadelförmig ausgebildeten Einspritzventilgliedes 6 hydraulisch beaufschlagt.The outer, second booster piston 14 has an end face 16 which is acted upon by a spring element 15 which can be embodied as a spiral spring, which is supported on a support disk 11 formed below the piezoactuator 39, which undergoes a vertical movement when the actuator 39 is energized. The support disk 11 is supported by a tubular spring 17, which is supported with its opposite end of the support disk 11 on the upper plane surface 7 of the washer 3. By means of the tubular spring 17, the support disk 11 is set in its rest position when the energization of the piezocrystal stack of the actuator 39 is canceled. The tubular spring 17 between the support plate 11 and the upper end surface 7 of the washer 3 surrounds a stop sleeve 18. The stop sleeve 18 extends below a shoulder of the second booster piston 14 and surrounds a spring 28, a control chamber 25 defining a first control chamber sleeve 27 to the upper Plane 7 of the washer 3 of the fuel injector 1 hires. The spring 28 is permanently tensioned due to the pressure prevailing in the cavity 9 fuel pressure, so that it is ensured that the first control chamber sleeve 27 is always employed with its formed on the underside biting edge 29 against the upper end surface 7 of the washer 3, so that the control chamber 25 is sealed is. From the control chamber 25, the fuel contained in this and corresponding to the retraction movement of the first booster piston 13 and the second booster piston 14 or both pistons in the control chamber 25 corresponding compressed over the channel 26 flows below the lower end surface 8 of the washer 3 hydraulic space, the one head 31 of the needle-shaped injection valve member 6 hydraulically applied.

Der Steuerraum 25 wird einerseits von der oberen Planfläche 7 der Zwischenscheibe 3 und andererseits sowohl von der Stirnseite 23 des ersten Übersetzerkolbens 13 als auch von der Stirnseite 24 des zweiten Übersetzerkolbens 14 beaufschlagt.The control chamber 25 is acted on the one hand by the upper end face 7 of the intermediate disc 3 and on the other hand both from the end face 23 of the first booster piston 13 and from the end face 24 of the second booster piston 14.

Das unterhalb der Zwischenscheibe 3 angeordnete, nadelförmig ausbildbare Einspritzventilglied 6 weist einen Kopf 31 auf, der in einem Durchmesser d1 ausgebildet ist. Im Vergleich zu diesem Durchmesser d1 weist der zweite Übersetzerkolben 14 einen Außendurchmesser d3 auf, welcher sowohl den Durchmesser d2 des ersten Übersetzerkolbens 13 als auch den Kopfdurchmesser d1 des nadelförmig ausgebildeten Einspritzventilgliedes 6 übersteigt. Der hydraulische Raum zwischen der unteren Planfläche 8 der Zwischenscheibe 3 und der oberen Stirnseite des nadelförmig ausgebildeten Einspritzventilgliedes 6 wird durch eine zweite Steuemaumhülse 32 begrenzt Die zweite Steuerraumhülse 32 ist ihrerseits über eine Feder 33 beaufschlagt, welche sich an einem Stützring 34 abstützt, der beispielsweise auf die Umfangsffäche eines nadelförmig ausgebildeten Einspritzventilgliedes 6 aufgeschrumpft sein kann, d.h. mittels eines Presssitzes mit der Mantelfläche des nadelförmig ausgebildeten Einspritzventilgliedes 6 verbunden ist. Unterhalb des Stützringes 34 sind am Umfang des nadelförmig ausgebildeten Einspritzventilgliedes 6 zwei oder mehr Freiflächen 36 angeordnet, über welche Kraftstoff in Strömungsrichtung 38 gesehen einem Ringspalt 37 zuströmt Unterhalb des Ringspalts 37 zwischen dem nadelförmig ausgebildeten Einspritzventilglied 6 und dem Düsenkörper 4 befinden sich die in der Zeichnung nicht dargestellten Einsprizöffnungen am brennraumseitigen Ende des Kraftstoffinjektors 1.The needle-shaped injection valve member 6 arranged below the intermediate disk 3 has a head 31 which is formed in a diameter d 1 . Compared to this diameter d 1 , the second booster piston 14 has an outer diameter d 3 , which exceeds both the diameter d 2 of the first booster piston 13 and the head diameter d 1 of the needle-shaped injection valve member 6. The hydraulic space between the lower face 8 of the washer 3 and the upper end of the needle-shaped injection valve member 6 is limited by a second control sleeve 32 The second control chamber sleeve 32 is in turn acted upon by a spring 33, which is supported on a support ring 34, for example the Umfangsffäche a needle-shaped injection valve member 6 may be shrunk, that is connected by means of a press fit with the lateral surface of the needle-shaped injection valve member 6. Below the support ring 34, two or more free surfaces 36 are arranged on the circumference of the needle-shaped injection valve member 6, via which fuel flows in the flow direction 38 an annular gap 37 flows below the annular gap 37 between the needle-shaped injection valve member 6 and the nozzle body 4 are in the drawing Not shown injection ports at the combustion chamber end of the fuel injector. 1

Die Freiflächen 36 können je nach Ausführung des nadelförmig ausgebildeten Einspritzventilgliedes 6 um jeweils 120 °, im Falle einer Ausbildung von drei Strömungsfreiflächen 36 oder in einem Winkel von 90 °, im Falle der Ausbildung von vier Strömungsfreiflächen 36 am nadelförmig ausgebildeten Einspritzventilglied 6 zueinander orientiert sein.Depending on the design of the needle-shaped injection valve member 6, the free surfaces 36 can be oriented by 120 °, in the case of the formation of three flow relief surfaces 36 or at an angle of 90 °, in the case of the formation of four flow relief surfaces 36 on the needle-shaped injection valve member 6.

Im geschlossenen Zustand des Einspritzventilgliedes 6 ist der Piezokristallstapel des Aktors 39 bestromt und demzufolge in vertikale Richtung gelängt. Demzufolge ist die Stützscheibe 11 in vertikale Richtung nach unten ausgelenkt und beaufschlagt die Rohrfeder 17, so dass diese entgegen der vertikalen Hubrichtung des Aktors 39 vorgespannt ist Aufgrund der Bestromung des Piezokristallstapels des Aktors 39 sind sowohl der erste Übersetzerkolben 13 als auch der zweite Übersetzerkolben 14 des mehrstufig ausgebildeten Druckübersetzers 12 in den Steuerraum 25 eingefahren. In diesem herrscht somit ein erhöhter Druck, welcher über den Kanal 26 in der Zwischenscheibe 3 auf den hydraulischen Raum oberhalb des Kopfes 31 des nadelförmig ausgebildeten Einspritzventilgliedes 6 wirkt Wird die Bestromung des Aktors 39 nun zurückgenommen, zieht sich der Piezokristallstapel des Aktors 39 zusammen und dessen Längung in vertikale Richtung verringert sich. Bedingt durch die vorgespannte Rohrfeder 17 fährt die Stützscheibe 11 in vertikale Richtung entsprechend des Rückgangs der Längung des Piezokristallstapels des Aktors 39 nach oben, so dass der erste Übersetzerkolben 13 mit seiner dem Steuerraum 25 zuweisenden Stirnseite 23 aus dem Steuerraum 25 ausfährt, wodurch dort der Druck sinkt. Aufgrund des Druckabfalls im Steuerraum 25 und dessen hydraulischer Verbindung zum hydraulischen Raum oberhalb des Kopfes 31 des nadelförmig ausgebildeten Einspritzventilglieds 6 fährt auch das nadelförmig ausgebildete Einspritzventilglied 6 nach oben und die Einspritzöffnungen werden freigegeben. Innerhalb des skizzierten Teilhubbereiches arbeitet der mehrstufig ausgebildete Druckübersetzer 12 mit einem Übersetzungsverhältnis von 1:1-1,5. Das Übersetzungsverhältnis innerhalb des skizzierten Teilhubbereiches wird definiert durch das Durchmesser d1/d2, wobei d1 den Durchmesser des Kopfes 31 des nadelförmig ausgebildeten Einspritzventilgliedes 6 bezeichnet und mit d2 der Außendurchmesser des ersten Übersetzerkolbens 13 des mehrstufig ausgebildeten Druckübersetzers 12 bezeichnet. Aufgrund des in diesem Teilhubbereich wirksamen Übersetzungsverhältnisses von 1:1-1,5 kann ein schnelles, präzises und stabiles Öffnen der am brennraumseitigen Ende des Kraftstoffinjektors 1 ausgebildeten Einspritzöffnungen erfolgen.In the closed state of the injection valve member 6, the piezocrystal stack of the actuator 39 is energized and thus elongated in the vertical direction. Consequently, the support disk 11 is deflected in the vertical direction downwards and acts on the pipe spring 17, so that it is biased against the vertical stroke direction of the actuator 39 Due to the energization of the piezocrystal stack of the actuator 39, both the first booster piston 13 and the second booster piston 14 of retracted multistage pressure intensifier 12 retracted into the control chamber 25. In this there is thus an increased pressure, which acts on the channel 26 in the washer 3 to the hydraulic space above the head 31 of the needle-shaped injection valve member 6. If the energization of the actuator 39 is now withdrawn, the piezocrystal stack of the actuator 39 and pulls together Elongation in the vertical direction decreases. Due to the pre-tensioned tube spring 17, the support plate 11 moves in the vertical direction according to the Reduction of the elongation of the piezocrystal stack of the actuator 39 upwards, so that the first booster piston 13 extends with its the control chamber 25 facing end face 23 from the control chamber 25, whereby there the pressure decreases. Due to the pressure drop in the control chamber 25 and its hydraulic connection to the hydraulic space above the head 31 of the needle-shaped injection valve member 6 also moves the needle-shaped injection valve member 6 upwards and the injection ports are released. Within the sketched Teilhubbereiches the multi-stage pressure intensifier 12 works with a transmission ratio of 1: 1-1.5. The transmission ratio within the sketched Teilhubbereiches is defined by the diameter d 1 / d 2 , wherein d 1 denotes the diameter of the head 31 of the needle-shaped injection valve member 6 and d 2 denotes the outer diameter of the first booster piston 13 of the multistage pressure booster 12. Due to the effective in this Teilhubbereich gear ratio of 1: 1-1.5 can be done quickly, precisely and stably opening the injection ports formed at the combustion chamber end of the fuel injector 1.

Erfolgt eine weitere Rücknahme der Bestromung des Aktors 39, zieht sich dessen Piezokristallstapel weiter zusammen, d.h. seine Längung in vertikale Richtung wird weiter reduziert. Aufgrunddessen bewegt sich auch der erste Übersetzerkolben 13 mit seiner den Steuerraum 25 beaufschlagenden Stirnseite 23 immer weiter aus dem Steuerraum 25 hinaus. Schlägt die Oberseite des ringförmig ausgebildeten Mitnehmers 20 an einer ersten Anschlagseite 21 der Ausnehmung 19 im zweiten Übersetzerkolben 14 an, wird nach Überwindung des mit h1 bezeichneten Hubes der zweite Übersetzerkolben 14, der am Umfang des ersten Übersetzerkolbens 13 verschiebbar aufgenommen ist, durch den Mitnehmer nach oben mitgenommen. Dadurch fährt auch die ringförmig ausgebildete Stirnfläche 24 des zweiten Übersetzerkolbens 14, welche ebenfalls den Steuerraum 25 beaufschlagt, weiter aus diesem aus. Nach Überwinden des Hubes h1 arbeitet der mehrstufig ausgebildete Druckübersetzer nunmehr mit einem zweiten Übersetzungsverhältnis von 1:4 -7, welches durch das Durchmesserverhältnis von d1/d3 definiert wird. Mit d1 ist - wie bereits oben erwähnt - der Kopfdurchmesser des Kopfes 31 des nadelförmig ausgebildeten Einspritzventilgliedes 6 bezeichnet, während d3 den Außendurchmesser des am ersten Übersetzerkolben 13 verschieblich bewegbaren zweiten Übersetzerkolbens 14 bezeichnet. Aufgrund der ab Überschreiten des Hubes h1 gemeinsam aus dem Steuerraum 25 ausfahrenden Stirnflächen 23 und 24 sinkt der Druck im Steuerraum 25 schneller, verglichen zu dem Zustand, in dem lediglich die Stirnfläche 23 des ersten Übersetzerkolbens 13 aus dem Steuerraum 25 ausfährt. Aufgrunddessen lässt sich durch einen geringen Aktorhub ein vollständiges Öffnen des nadelförmig ausgebildeten Einspritzventilglieds 6 erreichen, durch Bewegung einer größeren hydraulischen Fläche (23 +24) was im Volllastbereich der Verbrennungskraftmaschine von Bedeutung ist.If there is a further reduction in the energization of the actuator 39, its piezocrystal stack continues to contract, ie its elongation in the vertical direction is further reduced. As a result, the first booster piston 13, with its end face 23 acting on the control chamber 25, also moves further and further out of the control chamber 25. If the upper side of the annular driver 20 strikes against a first stop side 21 of the recess 19 in the second booster piston 14, after overcoming the stroke designated by h 1 , the second booster piston 14, which is slidably received on the circumference of the first booster piston 13, will move through the driver taken upstairs. As a result, the ring-shaped end face 24 of the second booster piston 14, which likewise acts on the control chamber 25, continues to move out of this. After overcoming the stroke h 1 , the multistage pressure intensifier now operates with a second transmission ratio of 1: 4 -7, which is defined by the diameter ratio of d 1 / d 3 . With d 1 is - as already mentioned above - the head diameter of the head 31 of the needle-shaped injection valve member 6 denotes, while d 3 denotes the outer diameter of the first booster piston 13 displaceably movable second booster piston 14. Due to the exceeding of the stroke h 1 together from the control chamber 25 extending end faces 23 and 24, the pressure in the control chamber 25 decreases faster compared to the state in which only the end face 23 of the first booster piston 13 extends out of the control chamber 25. Due to this, a complete actuator needle opening can achieve complete opening of the needle-shaped injection valve member 6 by moving a larger hydraulic surface (23 +24), which is important in the full load range of the internal combustion engine.

Wird der Kristallstapel des Piezoaktors 39 hingegen wieder bestromt, so stellt sich eine dem Bestromungsniveau des Piezokristallstapels entsprechende Längung dieses Kristallstapels ein, wodurch die Stützscheibe 11 entgegen der Wirkung der Rohrfeder 17, die sich an der oberen Planfläche 7 der Zwischenscheibe 3 abstützt, komprimiert wird. Die Rohrfeder 17 umgibt die Anschlaghülse 18, welche ihrerseits mit ihrer Oberkante einen Absatz am Außeinumfang des zweiten Übersetzerkolbens 14 untergreift und dessen Grundstellung definiere. Fährt die Stützscheibe 11 aufgrund der Längung des Piezokristallstapels des Aktors 39 in vertikale Richtung nach unten, so wird zunächst der innenliegende, erste Übersetzerkolben 13 mit seiner Stirnseite 23 in den Steuerraum 25 eingefahren und - sobald die Unterseite des Mitnehmers 20 an der zweiten Anschlagseite 22 der Ausnehmung 19 anliegt - auch der zweite Übersetzerkolben 14 in seine Grundstellung bewegt, die durch die Anschlaghülse 18, die sich ebenfalls an der oberen Planfläche 7 der Zwischenscheibe 3 abstützt, definiert istIf, however, the crystal stack of the piezoelectric actuator 39 is energized again, then an elongation of this crystal stack corresponding to the energization level of the piezocrystal stack sets in, whereby the support disk 11 is compressed against the action of the tubular spring 17, which is supported on the upper planar surface 7 of the intermediate disk 3. The tube spring 17 surrounds the stop sleeve 18, which in turn engages with its upper edge a paragraph on the outer circumference of the second booster piston 14 and define its basic position. If the support disk 11 moves downwards in a vertical direction due to the elongation of the piezocrystal stack of the actuator 39, then the inner, first booster piston 13 is moved with its end face 23 into the control chamber 25 and, as soon as the underside of the driver 20 on the second stop side 22 of FIG Recess 19 abuts - and the second booster piston 14 moves to its normal position, which is defined by the stop sleeve 18, which is also supported on the upper end face 7 of the washer 3

Über den Zulauf 10 tritt unter Systemdruck (Rail-Druck) stehender Kraftstoff in den Hohlraum 9 im Injektorkörper 2 ein und strömt über den in der Zwischenscheibe 3 vorgesehenen Kanal 40 dem Düsenkörper 4 zu. Aufgrund der Wirkung der Beißkanten 29 an der ersten Steuerraumhülse 27 und der Beißkante 35 der zweiten Steuerraumhülse 32 ist das im Steuerraum 25 sowie in dem hydraulischen Raum oberhalb des Kopfes 31 des nadelförmig ausgebildeten Einspritzventilgliedes 6 aufgenommene Steuervolumen vom zum Einspritzventilglied 6 strömenden Kraftstoff separiert.Via the inlet 10, fuel that is under system pressure (rail pressure) enters the cavity 9 in the injector body 2 and flows to the nozzle body 4 via the channel 40 provided in the intermediate disc 3. Due to the action of the Beißkanten 29 on the first control chamber sleeve 27 and the biting edge 35 of the second control chamber sleeve 32 which is recorded in the control chamber 25 and in the hydraulic space above the head 31 of the needle-shaped injection valve member 6 control volume separated from the injection valve member 6 flowing fuel.

Der Kraftstoff strömt über den Kanal 40 in den Düsenkörper 4 ein und tritt über die am Umfang des nadelförmig ausgebildeten Einspritzventilgliedes 6 vorgesehenen Freifläche 36 in einen Ringspalt 37 ein, welcher zwischen dem Außenumfang des nadelförmig ausgebildeten Einspritzventilglieds 6 und der Innenseite des Düsenkörpers 4 definiert ist Das in Strömungsrichtung 38 strömende Kraftstoffvolumen strömt den am brennraumseitigen Ende des Kraftstoffinjektors 1 ausgebildeten Einspritzöffnungen zu und gelangt über diese bei geöffnetem oder lediglich teilgeöffneten Einspritzventilglied 6 in den Brennraum der selbstzündenden Verbrennungskraftmaschine.The fuel flows via the channel 40 into the nozzle body 4 and enters via the provided at the periphery of the needle-shaped injection valve member 6 free surface 36 in an annular gap 37 which is defined between the outer periphery of the needle-shaped injection valve member 6 and the inside of the nozzle body Fuel volume flowing in the flow direction 38 flows to the injection openings formed at the combustion chamber end of the fuel injector 1 and, via this, when the injection valve member 6 is open or only partially opened, enters the combustion chamber of the self-igniting internal combustion engine.

Die erfindungsgemäß vorgeschlagene Lösung zeichnet sich vor allem dadurch aus, dass im ersten Teilhubbereich des nadelförmig ausgebildeten Einspritzventilgliedes 6 ein Öffnen des nadelförmig ausgebildeten Einspritzventilgliedes mit einer hohen Steifigkeit, bewirkt durch die kleine Übersetzung von 1:1-1,5, zwischen Aktorhub und Einspritzvenhlglied realisiert werden kann. Demzufolge ist die im ersten Teilhubbereich des Einspritzventilgliedes folgende Öffnung der brennraumseitig angeordneten Einspritzöffnungen kontrolliert, d.h. aufgrund zu schnellem Öffnen des nadelförmig ausgebildeten Einspritzventilgliedes 6 auftretende Mengensprünge hinsichtlich der in den Brennraum eingebrachten Kraftstoffmenge werden vermieden, so dass die Rußproduktion bei der Verbrennung in erheblichem Maße zurückgeht. Aufgrund der nach Erreichen des Teilhubes h1 gemeins amen Ouckentlastungsbewegung der beiden Übersetzerkolben 13, 14 des mehrstufigen Druckübersetzers 12 stellt sich ein höheres Übersetzungsverhältnis zwischen 1:4-7 des mehrstufig ausgebildeten Druckübersetzers 12 dann ein, wenn der Teilhub h1 in Öffnungsrichtung überwunden ist. Damit kann durch einen kleinen Aktorhub ein weiteres Öffnen des nadelförmig ausgebildeten Einspritzventilgliedes 6 mit größerer Übersetzung erfolgen da die Stirnflächen 23 und 24 gemeinsam bewegt werden.The proposed solution according to the invention is characterized in particular by the fact that in the first Teilhubbereich of the needle-shaped injection valve member 6 opening the needle-shaped injection valve member with a high rigidity, effected by the small ratio of 1: 1-1.5, realized between Aktorhub and Einspritzvenhlglied can be. Accordingly, the following in the first Teilhubbereich the injection valve member opening of the combustion chamber side arranged injection openings is controlled, ie occurring due to rapid opening of the needle-shaped injection valve member 6 occurring Volume jumps with regard to the amount of fuel introduced into the combustion chamber are avoided, so that the production of soot during combustion drops to a considerable extent. Due to the common after the partial stroke h 1 amen Ouckentlastungsbewegung the two booster piston 13, 14 of the multi-stage pressure booster 12, a higher ratio between 1: 4-7 of the multi-stage pressure booster 12 then turns when the partial stroke h 1 is overcome in the opening direction. This can be done with a larger translation by a small Aktorhub a further opening of the needle-shaped injection valve member 6 since the end faces 23 and 24 are moved together.

Aufgrund der erfindungsgemäß vorgeschlagenen Lösung kann im Gegensatz zu den aus dem Stand der Technik bekannten Lösungen das Aktorbauvolumen erheblich verringert werden. Durch die beiden den Teilhüben des nadelförmig ausgebildeten Einspritzventilgliedes 6 entsprechenden Übersetzungsverhältnisse von 1:1-1,5 im ersten Teilhubbereich sowie 1:4-7 im weiteren Teilhubbereich lässt sich eine Formung des Einspritzverlaufes in den Brennraum der selbstzimdenden Verbrennungskraftmaschine realisieren, wobei insbesondere dem Erfordernis Rechnung getragen ist, den das nadelförmig ausgebildete Einspritzventilglied 6 ansteuernden Aktor 39 möglichst bauraumsparend im Hohlraum 9 des Kraftstoffinjektors 1 unterzubringen.Due to the proposed solution according to the invention, in contrast to the solutions known from the prior art Aktorbauvolumen can be significantly reduced. By the two partial strokes of the needle-shaped injection valve member 6 corresponding gear ratios of 1: 1-1.5 in the first Teilhubbereich and 1: 4-7 in the next Teilhubbereich can be a shaping of the injection curve in the combustion chamber of selbstzimdenden internal combustion engine, in particular the requirement Account is taken to accommodate the needle-shaped injection valve member 6 controlling actuator 39 as possible to save space in the cavity 9 of the fuel injector 1.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Kraftstoffinjektorfuel injector
22
Injektorkörperinjector
33
Zwischenscheibewasher
44
Düsenkörpernozzle body
55
DüsenspannmutterNozzle clamping nut
66
EinspritzventilgliedInjection valve member
77
obere Planflächeupper plane
88th
untere Planflächelower plane
99
Hohlraumcavity
1010
Kraftstoffzulauf (von Common Rail)Fuel intake (from Common Rail)
1111
Stützscheibesupport disc
1212
mehrstufiger Druckübersetzermulti-stage intensifier
1313
erster Übersetzerkolbenfirst booster piston
1414
zweiter Übersetzerkolbensecond booster piston
1515
Federelement für ersten ÜbersetzerkolbenSpring element for first booster piston
1616
Stirnfläche zweiter Übersetzerkolben 14End face of the second booster piston 14
1717
RohrfederBourdon tube
1818
Anschlaghülsestop sleeve
1919
Ausnehmungrecess
2020
Mitnehmer
h1 Vorhubmitnehmer 20takeaway
h 1 forward lift driver 20
2121
erste Anschlagseite Ausnehmung 19first stop side recess 19
2222
zweite Anschlagseite Ausnehmung 19second stop side recess 19
2323
Stirnseite erster Übersetzerkolben 13Front side of the first booster piston 13
2424
Stirnseite zweiter Übersetzerkolben 14Front side of the second booster piston 14
2525
Steuerraumcontrol room
2626
Kanalchannel
2727
erste Steuerrautnhülsefirst control worm sleeve
2828
Federfeather
2929
Beißkante v. 27Biting edge v. 27
d1 d 1
Kopfdurchmesser Einspritzventilglied 6Head diameter of injection valve member 6
d2 d 2
Durchmesser erster Übersetzerkolben 13Diameter of first booster piston 13
d3 d 3
Durchmesser zweiter Übersetzerkolben 14Diameter of the second booster piston 14
3030
Aufnahmenut für Mitnehmer 20Receiving groove for driver 20
3131
Kopf Einspritzventilglied 6Head injection valve member 6
3232
zweite Steuerraumhülsesecond control chamber sleeve
3333
Federfeather
3434
Stützungsupport
3535
Beißkante v. 32Biting edge v. 32
3636
Freiflächen (120°, 90°)Open spaces (120 °, 90 °)
3737
Ringspaltannular gap
3838
Strömungsrichtung KraftstoffFlow direction fuel
3939
Aktoractuator

Claims (12)

  1. Fuel injector having an injection valve member (6) for injecting fuel into the combustion chamber of an auto-ignition internal combustion engine, with it being possible for the injection valve member (6) to be activated by means of an actuator (39) which directly actuates a pressure booster (12) with which the pressure in a control chamber (25) which acts on the injection valve member (6) can be manipulated, characterized in that the pressure booster (12) has a first and a second booster piston (13, 14) which are coupled by means of a driver (20) which is movable within a recess (19) between a first stop side (21) and a second stop side (22).
  2. Fuel injector according to Claim 1, characterized in that the second booster piston (14) of the multi-stage pressure booster (12) is mounted in a movable fashion on the first, inner booster piston (13).
  3. Fuel injector according to Claim 1, characterized in that a transmission element (11) which is assigned to the booster pistons (13, 14) can be acted on by a tubular spring element (17) which is supported in the injector body (2).
  4. Fuel injector according to Claim 1, characterized in that, within a first partial stroke range, which corresponds to a pilot stroke h1, of the needle-shaped injection valve member (6), the first booster piston (13) moves out of the control chamber (25) when the current supply to the actuator (39) is withdrawn.
  5. Fuel injector according to Claim 1, characterized in that, after the first partial stroke range, which corresponds to a pilot stroke h1, of the needle-shaped injection valve member (6) is exceeded, the driver (20) moves the second booster piston (14) out of the control chamber (25) together with the first booster piston (13).
  6. Fuel injector according to Claim 1, characterized in that the pilot stroke h1 corresponds to the spacing between a plane side of the driver (20) and a first stop side (21) of a recess (19) in the second booster piston (14).
  7. Fuel injector according to Claim 1, characterized in that the control chamber (25), which can be acted on either by means of the end side (23) of the first booster piston (13) or by means of the end sides (23, 24) of the first booster piston (13) and of the second booster piston (14), is hydraulically connected via a hydraulic duct (26) to a hydraulic chamber above a head region (31) of the needle-shaped injection valve member (6).
  8. Fuel injector according to Claim 7, characterized in that both the control chamber (25) and the hydraulic chamber above the needle-shaped injection valve member (6) are delimited by means of spring-loaded control chamber sleeves (27, 32).
  9. Fuel injector according to Claim 8, characterized in that the first control chamber sleeve (27) bears, at a biting edge (29), against an upper plane surface (7) of an intermediate disc (3) of the fuel injector (1).
  10. Fuel injector according to Claim 8, characterized in that the second control chamber sleeve (32) bears with its biting edge (35) against the lower plane surface (8) of an intermediate disc (3) of the fuel injector (1).
  11. Fuel injector according to Claim 1, characterized in that the spring (28) which loads the first control chamber sleeve (27) against the upper plane surface (7) of the intermediate disc (3) bears against an annular shoulder of the second booster piston (14) which is mounted in a movable fashion on the first booster piston (13).
  12. Fuel injector according to Claim 1, characterized in that an end side (16) of the second booster piston (14) of the multi-stage pressure booster (12) is acted on by means of a spring element (15), which in turn is supported on the transmission element (11) below the piezoelectric actuator (39).
EP05749972A 2004-07-21 2005-05-13 Fuel injector comprising a direct multi-stage injection valve member control system Not-in-force EP1771651B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004035280A DE102004035280A1 (en) 2004-07-21 2004-07-21 Fuel injector with direct multi-stage injection valve element control
PCT/EP2005/052201 WO2006008200A1 (en) 2004-07-21 2005-05-13 Fuel injector comprising a direct multi-stage injection valve member control system

Publications (2)

Publication Number Publication Date
EP1771651A1 EP1771651A1 (en) 2007-04-11
EP1771651B1 true EP1771651B1 (en) 2009-10-07

Family

ID=34969382

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05749972A Not-in-force EP1771651B1 (en) 2004-07-21 2005-05-13 Fuel injector comprising a direct multi-stage injection valve member control system

Country Status (6)

Country Link
US (1) US20080093483A1 (en)
EP (1) EP1771651B1 (en)
JP (1) JP2008506888A (en)
AT (1) ATE445096T1 (en)
DE (2) DE102004035280A1 (en)
WO (1) WO2006008200A1 (en)

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DE102005029976A1 (en) * 2005-06-28 2007-01-11 Robert Bosch Gmbh Fuel injector
DE102005040912A1 (en) * 2005-08-30 2007-03-08 Robert Bosch Gmbh injection
DE102007002758A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh fuel injector
DE102006036781A1 (en) * 2006-08-07 2008-02-14 Robert Bosch Gmbh Injector and associated operating method
DE102007002278A1 (en) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Fuel injector for combustion chamber of internal combustion engine, has valve piston formed in two areas with two different diameters, where valve piston is enclosed in one of areas by ring unit, which is movable relative to valve piston
DE102007002282A1 (en) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Fuel injector with coupler
DE102007016866A1 (en) 2007-04-10 2008-10-16 Robert Bosch Gmbh High-density fuel injector, has throttle plate surrounded by retaining body of fuel injector, where luggage compartment and control chamber stand in hydraulic connection with each other over throttle plate
JP4633766B2 (en) * 2007-06-08 2011-02-16 株式会社日本自動車部品総合研究所 Fuel injection valve
FR2919022B1 (en) * 2007-07-19 2012-10-26 Vianney Rabhi HYDRAULIC POWER PLANT FOR VARIABLE COMPRESSION RATE MOTOR.
JP4831131B2 (en) * 2008-06-06 2011-12-07 株式会社デンソー Fuel injection valve
JP4911435B2 (en) * 2008-10-03 2012-04-04 株式会社デンソー Fuel injection valve
DE102009047560A1 (en) * 2009-12-07 2011-06-09 Robert Bosch Gmbh fuel injector
DE102010002845A1 (en) * 2010-03-15 2011-09-15 Robert Bosch Gmbh Fuel injector
DE102010044205A1 (en) * 2010-11-22 2012-05-24 Robert Bosch Gmbh fuel injector
US9012489B2 (en) 2011-08-03 2015-04-21 Boehringer Ingelheim International Gmbh Phenyl-3-aza-bicyclo[3.1.0]hex-3-yl-methanones and the use thereof as medicament
DE102012212266B4 (en) * 2012-07-13 2015-01-22 Continental Automotive Gmbh fluid injector
DE102012212264B4 (en) 2012-07-13 2014-02-13 Continental Automotive Gmbh Method for producing a solid state actuator
DE102012021643B4 (en) 2012-11-03 2014-12-24 Peter Lischka Inexpensive pressure booster for high pressures
JP6443109B2 (en) * 2015-02-17 2018-12-26 株式会社Ｓｏｋｅｎ Fuel injection valve
CN116753096B (en) * 2023-08-11 2023-10-13 山西焦煤集团正仁煤业有限公司 Oil supply part structure for coal mine truck

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DE3224769A1 (en) * 1981-11-19 1983-05-26 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES, IN PARTICULAR PUMPEDUESE FOR DIESEL INTERNAL COMBUSTION ENGINES
DE19500706C2 (en) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Metering valve for dosing liquids or gases
DE19720145A1 (en) 1997-05-14 1998-11-19 Beiersdorf Ag Double-sided tape and its use
DE69911670T2 (en) * 1998-02-19 2004-08-12 Delphi Technologies, Inc., Troy Fuel injection valve
DE19817320C1 (en) * 1998-04-18 1999-11-11 Daimler Chrysler Ag Injector for fuel injection systems
DE10034444A1 (en) * 2000-07-15 2002-01-24 Bosch Gmbh Robert Fuel injector

Also Published As

Publication number Publication date
US20080093483A1 (en) 2008-04-24
EP1771651A1 (en) 2007-04-11
WO2006008200A1 (en) 2006-01-26
DE502005008285D1 (en) 2009-11-19
ATE445096T1 (en) 2009-10-15
DE102004035280A1 (en) 2006-03-16
JP2008506888A (en) 2008-03-06

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