EP1404966B1 - Fuel injector switch valve for the compression/decompression of a control chamber - Google Patents

Fuel injector switch valve for the compression/decompression of a control chamber Download PDF

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Publication number
EP1404966B1
EP1404966B1 EP02754253A EP02754253A EP1404966B1 EP 1404966 B1 EP1404966 B1 EP 1404966B1 EP 02754253 A EP02754253 A EP 02754253A EP 02754253 A EP02754253 A EP 02754253A EP 1404966 B1 EP1404966 B1 EP 1404966B1
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EP
European Patent Office
Prior art keywords
valve
space
pressure
control chamber
control
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
EP02754253A
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German (de)
French (fr)
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EP1404966A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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

Definitions

  • Fuel injection systems for air-compressing internal combustion engines today injection systems with high pressure common rail (Common Rail) are used to ensure a uniform, pulsation-free injection pressure level during the injections.
  • the cylinders of an air-compressing internal combustion engine are each assigned fuel injectors, via which the fuel is injected into the combustion chambers of an internal combustion engine.
  • the course of injection depends on the injection processes u.a. from the speed at which the nozzle needle in the housing of the fuel injector opens or closes the injection nozzle. From the course of the injection into the combustion chamber, the exhaust gas composition of the internal combustion engine is highly dependent on, for example, HC emissions.
  • a servo valve has a movable valve element on which a throttle element is formed in the fuel flow direction to the injection nozzle.
  • the throttle element serves to influence the initial phase of the injection and also has a piston-shaped projection on a groove which emerges from a bore in the main phase of the injection and then releases a direct path for the fuel, bypassing the throttle.
  • WO 99 617 79 A discloses a fuel injector with an injector body, wherein in the housing of the injector body a valve chamber of a multi-way valve is formed, wherein the control chamber of the injector is connected to the valve chamber of the multi-way valve via a control chamber channel which is acted upon with respect to the control chamber both in the relief direction and in the loading direction , wherein the control chamber channel, an inlet and an outlet open into the valve chamber of the multiway valve.
  • US 5,460,329 refers to a fuel injector with pressure boosting ratio.
  • the fuel passes through a designed as a slide valve electromagnetic control valve to the pressure intensifier in the injector.
  • the fuel is put under high pressure by the pressure intensifier at fixed times or crankshaft angles.
  • the high pressure fuel causes the valve needle of the injector to lift off its seat. This clears the path for the fuel to the injector injector.
  • DE 199 08 418 C1 refers to a control valve for use in a storage injection system for a diesel engine.
  • the control valve includes a housing having an input port, an output port, and a return port.
  • first seat valve with a first valve body and a second seat valve with a second valve body
  • the first poppet valve is disposed between the output port and the return port and normally closed with the second poppet valve normally open between the input port and the output port.
  • the second valve body is arranged coaxially in the first valve body.
  • US 4,972,997 relates to a fuel injection valve with an axially displaceable, piston-shaped valve member.
  • the valve member has at its combustion chamber end on a conical valve sealing surface, with which it cooperates with a conical valve seat surface on the valve body, which is formed at the inwardly cantilevered end of the closed valve bore.
  • a contact edge between the valve sealing surface on the valve member and the valve seat surface forms a peripheral sealing edge.
  • This sealing edge formed when the injection valve is closed seals a pressure space adjacent to the sealing edge upstream of the closed injection valve. Downstream of this sealing edge, at least one injection opening opening into the combustion chamber of the internal combustion engine to be supplied is provided in the wall of the valve body, which discharges from the valve seat surface.
  • valve member The operating times of the valve member are too long due to the large hydraulic forces occurring for fast-switching injectors. Furthermore, due to the large number of components arranged axially one behind the other, this fuel injection valve is very large, which limits its applicability to engines with a small available installation space.
  • DE 197 44 518 A1 shows a fuel injection valve for internal combustion engines. It is a fuel injection valve for internal combustion engines with an axially displaceable valve member arranged in a valve body, which has a conical valve sealing surface at its end facing the combustion chamber of the internal combustion engine, with which it has a conical valve seat surface on the valve body for controlling an injection cross section interacts.
  • the valve member is slidably guided via an inner guide on a pin of a stationary insert body.
  • DE 100 55 714 A1 discloses a fuel injector in which a valve chamber of a three-way valve is selectively connected to a bleed or a high pressure line. Furthermore, the valve chamber is connected via a main orifice to a control chamber for controlling the valve opening and closing operation of a nozzle needle.
  • the control chamber may be connected via the main orifice and the valve chamber to the exhaust pipe or the high pressure pipe when a valve body is driven by a piezoelectric actuator to open or close the exhaust pipe and close or open the high pressure pipe.
  • the control chamber is always connected via an auxiliary orifice to the high-pressure line without bypassing the three-way valve. Accordingly, the hydraulic pressure in the control chamber is slowly decreased at the valve opening time and rapidly increased at the valve closing timing, so that a lift characteristic of the nozzle needle is improved.
  • the pressure relief is brought about via a switching valve, which is designed as a 3/3-way valve.
  • the valve body of the 3/3-way switching valve can be switched in several positions in the surrounding valve space. In one of the switching positions, the permanent pressurization of the control chamber via the inlet throttle can be interrupted by closing this inlet, so that the pressure relief of the control chamber via the pressure relief line and the throttle element integrated in this takes place.
  • the throttle associated with the discharge from the control chamber of the nozzle needle acts as a drain and when pressure is applied to the control chamber as pressure-reducing valve of the control chamber as its inlet throttle.
  • valve body is in the form of a sphere, its actuation can take place, for example, via a piezoactuator and two opening speeds can be set.
  • actuation can take place, for example, via a piezoactuator and two opening speeds can be set.
  • two opening speeds can be set.
  • a complete closing of the inlet throttle in a lower seat of the valve body can be switched to a middle position in which the control chamber is indeed also relieved of pressure, but a simultaneous pressurization of the valve chamber given the switching valve, so that the pressure relief of the control chamber is carried out at a lower speed.
  • the feed from a high-pressure source such as a high-pressure collecting chamber is still provided with an inlet throttle element, but according to this further embodiment of the solution according to the invention, the outlet throttle in the drain line from the valve chamber of the valve body of a 3 / 3- Routing control valve relocated.
  • a very rapid pressure relief of the control chamber can be achieved because the inlet throttle can be completely closed.
  • the valve body of the 3/3-way control valve can be in a Move center position, whereby the outflow of the control volume from the control room, however, can also be slowed down.
  • FIG. 1 is to remove a control chamber of a nozzle needle, which is associated with a switching valve, wherein the pressure and pressure relief line of the control chamber is provided with a throttle element.
  • This embodiment of the invention is based solution idea can be removed that in a housing 2 of an injector body 1, a multi-way valve 3 is added.
  • the multi-way valve 3 is preferably formed as a 3/3-way control valve, the valve body 4 in the illustrated embodiment is a spherically shaped element.
  • the valve body 4 is movable in the surrounding valve chamber 5 in the housing 2 of the injector 1 in a plurality of switching positions.
  • a transmission element 6 which is actuated by an actuator not shown here, be it a piezoelectric actuator or a solenoid valve.
  • a mechanical / hydraulic translator may be provided as an actuating element of the transmission element 6.
  • the transmission element passes through a bore in the housing 2 of the injector body 1. Between the outer surface of the transmission element 6 and the bore in the housing 2 of the injector 1, an annular space 8 is formed, from which a leakage oil outlet 9 runs in the low-pressure region of the fuel injector.
  • the annular gap 8 between the transmission element 6 and the housing 2 of the fuel injector 1 acts as a ring throttle element.
  • an inlet throttle element 14 which is formed in an inlet throttle 15.
  • the inlet 13 opens on the transfer element 6, with which the valve body 4 of the multi-way valve 3 can be actuated, opposite side.
  • a control chamber channel 16 opens into the valve chamber 5 of the multi-way valve 3, a control chamber channel 16.
  • the control chamber 20 of the fuel injector is bounded by a wall 21 of the housing 2.
  • a stop surface 22 is received, which faces an upper end face 24 of a nozzle needle 23, wherein the nozzle needle 23 in the housing 2 of the injector body 1 in the vertical direction according to the double arrow 25 is moved up and down.
  • the control chamber 20 can be relieved of pressure by a control volume enclosed in the relief direction 17.
  • a throttle element 19 accommodated in the control chamber duct 16 acts in the pressure relief direction 17 with respect to the control chamber 20 as an outlet throttle, whereas the throttle element 19 acts as an inlet throttle to the control chamber 20 when the control chamber duct 16 is loaded in the loading direction 18.
  • the valve body 4 of the multiway valve 3 can be moved in a first switching position 10.1.
  • the first switching position 10.1 the spherical outer surface of the valve body 4 bears against the seat 10 of the valve chamber 5.
  • the high-pressure fuel flows through the control chamber passage 16 in the loading direction 18 the throttle element 19 passing into the control chamber 20 a.
  • a pressure buildup in the control chamber 20 so that the nozzle needle 23 is moved in the downward direction and closes one or more injection openings.
  • the inlet 13 is sealed off from the high pressure source, not shown here.
  • a very rapid pressure relief of the control chamber 20 via the control chamber channel 16 in the pressure relief direction 17 via the valve chamber 5, the annular gap in the leak oil 9 take place.
  • Advantageous in the embodiment according to FIG. 1 is the fact that an otherwise permanently acting inlet throttle 14 of an inlet 13 can be sealed off from a high-pressure source of a control chamber volume, so that it is ensured that a rapid pressure relief in the control chamber 20 takes place.
  • the spherical valve body 4 If, however, the spherical valve body 4 is moved to its central position 12, so can the outflow of the control chamber volume from the control chamber 20 slow down, as in the middle position 12 of the inlet 13, which opens into the valve chamber 5, is open and thereby a back pressure with respect to the Flow direction of the control chamber volume from the control chamber 20 is generated.
  • the control chamber 20 is relieved more slowly in the housing 2 of the injector body 1, i. the nozzle needle 23 moves slower in the direction of the stop surface 22 formed on the wall 21, so that the injection openings open more slowly in accordance with a second, compared to the second switching position 11.2 slower speed.
  • FIG. 2 is a further embodiment of the invention of the underlying idea, in which a control chamber associated switching valve comprises a valve chamber, the inlet and outlet are provided with throttle elements.
  • Analogous to the representation according to FIG. 1 is the valve chamber of the multi-way valve 3, preferably designed as a 3/3-way control valve, connected via an inlet 13 with a throttle element 14 with a high pressure source not shown here.
  • a control chamber duct 16 extends to a control chamber 20 in the housing 2 of the injector body 1, which on the one hand by a wall 21 of the housing 2 and on the other hand by an end face 24 of the housing 2 of the injector 1 in the direction of movement 25 movable nozzle needle 23 is limited.
  • a stop surface 22 is formed on the housing side control room wall 21 of the control chamber 20 .
  • control chamber passage 16 which connects the pressure-relieving control chamber 20 with the valve chamber 5, no throttle element.
  • the control chamber passage 16 is only in a pressure relief direction 17 with respect to the control chamber 20 and in a loading direction 18 with a fluid, for example fuel acted upon.
  • Throttle element 19 accommodated in control chamber channel 16 is now integrated in leakage oil outlet 9 branching off from annular gap 8 between transmission element 6 and housing 2.
  • valve body 4 of the multi-way valve 3 At the valve chamber 5, which encloses the spherically configured valve body 4 of the multi-way valve 3, an upper seat 10 corresponding to a first switching position 10.1 and a lower seat 11 opposed thereto are formed, in which the valve body 4 of the multi-way valve 3 is adjustable to a second switching position 11.1. Im in FIG. 2 shown state, the valve body 4 of the multi-way valve 3 is connected in a middle position 12.
  • the switching positions 10.1, 11.1 and 12 of the valve body 4 substantially correspond to the switching positions 10.1, 11.1 and 12, respectively, already in connection with the embodiment according to FIG. 1 have been described.
  • FIG. 2 closes in its second switching position 11.1 asked multi-way valve 3 the otherwise permanently acting inlet of fuel via the inlet 13 from a high pressure source, not shown here in the valve chamber 5 and from there via the control chamber passage 16 into the control chamber 20.
  • the inlet 13 is in the second Switched position 11.1 of the valve body 4 of the multi-way valve 3 completely switched off. This ensures that no bypass occurs during the injection;
  • given in the middle position 12 of the valve body 4 in the valve chamber 5 between the upper seat 10 and the lower seat 11 is a possibility of variation, whereby a fast and slow opening can be achieved, takes the valve body 4 its center position 12 as shown in FIG FIG. 2 between the upper seat 10 and lower seat 11 a.

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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)

Abstract

The invention relates to a fuel switch valve for an internal combustion engine comprising an injector body (1), wherein the housing thereof (2) accommodates a displaceable nozzle needle (23) which opens or closes the injection openings. Said nozzle needle (23) is actuated by means of a control chamber (20) which can be decompressed and impinged upon by high-pressure fuel from a high-pressure source via a feed (13). The housing (2) of the injector body (1) includes a valve chamber (5) for a multiple-way valve. The control chamber (20) is connected to the valve chamber (5) of the multiple-way valve by channel (16), which in relation to the control chamber (20), can be impinged upon both in the direction of decompression (17) as well as in the direction of compression (18).

Description

Technisches GebietTechnical area

Bei Kraftstoffeinspritzsystemen für luftverdichtende Verbrennungskraftmaschinen werden heute Einspritzsysteme mit Hochdrucksammelräumen (Common Rail) eingesetzt, um während den Einspritzungen ein gleichmäßiges, pulsationsfreies Einspritzdruckniveau zu gewährleisten. Den Zylindern einer luftverdichtenden Verbrennungskraftmaschine sind jeweils Kraftstoffinjektoren zugeordnet, über die der Kraftstoff in die Brennräume einer Verbrennungskraftmaschine eingespritzt wird. Der Einspritzverlauf hängt bei den Einspritzvorgängen u.a. von der Geschwindigkeit ab, mit welcher die Düsennadel im Gehäuse des Kraftstoffinjektors die Einspritzdüse öffnet bzw. verschließt. Vom Verlauf der Einspritzung in den Brennraum ist die Abgaszusammensetzung der Verbrennungskraftmaschine zum Beispiel hinsichtlich der HC-Emissionen in hohem Maße abhängig.Fuel injection systems for air-compressing internal combustion engines today injection systems with high pressure common rail (Common Rail) are used to ensure a uniform, pulsation-free injection pressure level during the injections. The cylinders of an air-compressing internal combustion engine are each assigned fuel injectors, via which the fuel is injected into the combustion chambers of an internal combustion engine. The course of injection depends on the injection processes u.a. from the speed at which the nozzle needle in the housing of the fuel injector opens or closes the injection nozzle. From the course of the injection into the combustion chamber, the exhaust gas composition of the internal combustion engine is highly dependent on, for example, HC emissions.

Stand der TechnikState of the art

DE 199 10 589 A1 betrifft ein Einspritzventil für eine Brennkraftmaschine. Ein Servoventil weist ein bewegliches Ventilelement auf, an dem ein Drosselelement in Kraftstofffließrichtung zur Einspritzdüse ausgebildet ist. Das Drosselelement dient der Beeinflussung der Anfangsphase der Einspritzung und weist ferner einen kolbenförmigen Ansatz über einer Nut auf, der in der Hauptphase der Einspritzung aus einer Bohrung austaucht und danach einen direkten Weg für den Kraftstoff unter Umgehung Drossel freigibt. Mittels dieser Lösung soll in der Anfangsphase der Einspritzung eine gedrosselte Verbindung zur Einspritzdüse des Einspritzsystems hergestellt werden. Im weiteren Verlauf des Einspritzvorganges wird, wenn sich das Servoventil weiter öffnet, unter Umgehung der anfänglich wirksamen Drossel eine direkte Verbindung zur Einspritzdüse aufgebaut. DE 199 10 589 A1 relates to an injection valve for an internal combustion engine. A servo valve has a movable valve element on which a throttle element is formed in the fuel flow direction to the injection nozzle. The throttle element serves to influence the initial phase of the injection and also has a piston-shaped projection on a groove which emerges from a bore in the main phase of the injection and then releases a direct path for the fuel, bypassing the throttle. By means of this solution is to be made in the initial phase of the injection, a throttled connection to the injection nozzle of the injection system. In the course of the injection process, when the servo valve opens further, establishing a direct connection to the injection nozzle, bypassing the initially effective throttle.

Dokument WO 99 617 79 A offenbart ein Kraftstoffinjektor mit einem Injektorkörper, wobei im Gehäuse des Injektorkörpers ein Ventilraum eines Mehrwegeventils ausgebildet ist, wobei der Steuerraum des Injektors mit dem Ventilraum des Mehrwegeventils über einen Steuerraumkanal verbunden ist, der in bezug auf den Steuerraum sowohl in Entlastungsrichtung als auch in Belastungsrichtung beaufschlagbar ist, wobei der Steuerraumkanal, eine Zulauf und ein Ablauf in den Ventilraum des Mehrwegeventils münden.document WO 99 617 79 A discloses a fuel injector with an injector body, wherein in the housing of the injector body a valve chamber of a multi-way valve is formed, wherein the control chamber of the injector is connected to the valve chamber of the multi-way valve via a control chamber channel which is acted upon with respect to the control chamber both in the relief direction and in the loading direction , wherein the control chamber channel, an inlet and an outlet open into the valve chamber of the multiway valve.

US 5,460,329 bezieht sich auf einen Kraftstoffinjektor mit druckverstärkender Übersetzung. Dabei gelangt der Kraftstoff über ein als Schieberventil ausgestaltetes elektromagnetisches Steuerventil zu dem Druckverstärker im Injektor. Über die elektromagnetische Ansteuerung des Steuerventils wird zu festgelegten Zeiten bzw. Kurbelwellenwinkeln der Kraftstoff vom Druckverstärker unter hohen Druck gesetzt. Der unter hohen Druck gesetzte Kraftstoff bewirkt ein Abheben der Ventilnadel des Injektors von ihrem Sitz. Dadurch ist der Weg für den Kraftstoff zur Einspritzdüse des Injektors freigegeben. DE 199 08 418 C1 bezieht sich auf ein Steuerventil zum Einsatz in einem Speichereinspritzsystem für einen Dieselmotor. Das Steuerventil umfaßt ein Gehäuse mit einem Eingangsanschluß, einem Ausgangsanschluß und einem Rücklaufanschluß. Ferner ist ein erstes Sitzventil mit einem ersten Ventilkörper sowie ein zweites Sitzventil mit einem zweiten Ventilkörper vorgesehen. Das erste Sitzventil ist zwischen Ausgangsanschluß und Rücklaufanschluß angeordnet und normalerweise geschlossen, wobei das zweite Sitzventil zwischen Eingangsanschluß und Ausgangsanschluß normalerweise offensteht. Der zweite Ventilkörper ist koaxial im ersten Ventilkörper angeordnet. US 5,460,329 refers to a fuel injector with pressure boosting ratio. In this case, the fuel passes through a designed as a slide valve electromagnetic control valve to the pressure intensifier in the injector. By means of the electromagnetic control of the control valve, the fuel is put under high pressure by the pressure intensifier at fixed times or crankshaft angles. The high pressure fuel causes the valve needle of the injector to lift off its seat. This clears the path for the fuel to the injector injector. DE 199 08 418 C1 refers to a control valve for use in a storage injection system for a diesel engine. The control valve includes a housing having an input port, an output port, and a return port. Furthermore, a first seat valve with a first valve body and a second seat valve with a second valve body is provided. The first poppet valve is disposed between the output port and the return port and normally closed with the second poppet valve normally open between the input port and the output port. The second valve body is arranged coaxially in the first valve body.

US 4,972,997 betrifft ein Kraftstoffeinspritzventil mit einem axial verschiebbaren, kolbenförmigen Ventilglied. Das Ventilglied weist dabei an seinem brennraumseitigen Ende eine konische Ventildichtfläche auf, mit der es mit einer konischen Ventilsitzfläche am Ventilkörper zusammenwirkt, die am nach innen kragenden Ende der geschlossenen Ventilbohrung gebildet ist. Dabei bildet eine Berührungskante zwischen der Ventildichtfläche am Ventilglied und der Ventilsitzfläche eine umlaufende Dichtkante. Diese bei geschlossenem Einspritzventil gebildete Dichtkante dichtet dabei eine stromaufwärts an der Dichtkante angrenzenden Druckraum bei geschlossenem Einspritzventil ab. Stromabwärts dieser Dichtkante ist wenigstens eine in den Brennraum der zu versorgenden Brennkraftmaschine mündende Einspritzöffnung in der Wand des Ventilkörpers vorgesehen, die dabei von der Ventilsitzfläche abführt. Die Stellzeiten des Ventilgliedes sind aufgrund der auftretenden großen hydraulischen Kräfte für schnellschaltende Einspritzventile zu lang. Des weiteren baut dieses Kraftstoffeinspritzventil aufgrund der Vielzahl von axial hintereinanderliegenden Bauteilen sehr groß, was die Einsetzbarkeit an Motoren mit geringem zur Verfügung stehenden Bauraum einschränkt. US 4,972,997 relates to a fuel injection valve with an axially displaceable, piston-shaped valve member. The valve member has at its combustion chamber end on a conical valve sealing surface, with which it cooperates with a conical valve seat surface on the valve body, which is formed at the inwardly cantilevered end of the closed valve bore. In this case, a contact edge between the valve sealing surface on the valve member and the valve seat surface forms a peripheral sealing edge. This sealing edge formed when the injection valve is closed seals a pressure space adjacent to the sealing edge upstream of the closed injection valve. Downstream of this sealing edge, at least one injection opening opening into the combustion chamber of the internal combustion engine to be supplied is provided in the wall of the valve body, which discharges from the valve seat surface. The operating times of the valve member are too long due to the large hydraulic forces occurring for fast-switching injectors. Furthermore, due to the large number of components arranged axially one behind the other, this fuel injection valve is very large, which limits its applicability to engines with a small available installation space.

DE 197 44 518 A1 zeigt ein Kraftstoffeinspritzventil für Brennkraftmaschinen. Es handelt sich um ein Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem in einem Ventilkörper angeordneten, axial verschiebbaren Ventilglied, das an seinem dem Brennraum der Brennkraftmaschine zugewandten Ende eine konische Ventildichtfläche aufweist, mit der es mit einer konischen Ventilsitzfläche am Ventilkörper zur Steuerung eines Einspritzquerschnittes zusammenwirkt. Dabei ist das Ventilglied über eine Innenführung gleitverschiebbar auf einem Zapfen eines ortsfesten Einsatzkörpers geführt. DE 197 44 518 A1 shows a fuel injection valve for internal combustion engines. It is a fuel injection valve for internal combustion engines with an axially displaceable valve member arranged in a valve body, which has a conical valve sealing surface at its end facing the combustion chamber of the internal combustion engine, with which it has a conical valve seat surface on the valve body for controlling an injection cross section interacts. In this case, the valve member is slidably guided via an inner guide on a pin of a stationary insert body.

DE 100 55 714 A1 offenbart ein Kraftstoffeinspritzventil, bei dem eine Ventilkammer eines Dreiwegeventils wahlweise mit einer Ablass- oder einer Hochdruckleitung verbunden wird. Weiterhin wird die Ventilkammer über eine Hauptblende mit einer Regelkammer zum Regeln des Ventilöffnungs- und Schließvorgangs einer Düsennadel verbunden. Die Regelkammer kann verbunden werden über die Hauptblende und die Ventilkammer mit der Ablassleitung oder der Hochdruckleitung, wenn ein Ventilkörper durch ein piezoelektrisches Stellglied angetrieben wird, um die Ablassleitung zu öffnen oder zu schließen und die Hochdruckleitung zu schließen oder zu öffnen. Die Regelkammer ist immer über eine Hilfsblende mit der Hochdruckleitung verbunden ohne Umgehen des Dreiwegeventils. Demgemäß wird der hydraulische Druck in der Regelkammer langsam vermindert bei der Ventilöffnungszeit und schnell erhöht bei der Ventilschließzeit, so dass eine Hubcharakteristik der Düsennadel verbessert ist. DE 100 55 714 A1 discloses a fuel injector in which a valve chamber of a three-way valve is selectively connected to a bleed or a high pressure line. Furthermore, the valve chamber is connected via a main orifice to a control chamber for controlling the valve opening and closing operation of a nozzle needle. The control chamber may be connected via the main orifice and the valve chamber to the exhaust pipe or the high pressure pipe when a valve body is driven by a piezoelectric actuator to open or close the exhaust pipe and close or open the high pressure pipe. The control chamber is always connected via an auxiliary orifice to the high-pressure line without bypassing the three-way valve. Accordingly, the hydraulic pressure in the control chamber is slowly decreased at the valve opening time and rapidly increased at the valve closing timing, so that a lift characteristic of the nozzle needle is improved.

Darstellung der ErfindungPresentation of the invention

Bei der erfindungsgemäß vorgeschlagenen Lösung wird die Druckentlastung über ein Schaltventil herbeigeführt, welches als 3/3-Wege-Ventil beschaffen ist. Der Ventilkörper des 3/3-Wege-Schaltventils ist im diesen umgebenden Ventilraum in mehrere Positionen schaltbar. In einer der Schaltstellungen kann die permanente Druckbeaufschlagung des Steuerraumes über die Zulaufdrossel durch ein Verschließen dieses Zulaufs unterbrochen werden, so daß die Druckentlastung des Steuerraumes über die Druckentlastungsleitung und das in diese integrierte Drosselelement erfolgt. Durch Unterbinden des gleichzeitigen Zulaufs von der Zulaufdrossel erfolgt lediglich ein Abströmen des Steuervolumens aus dem Steuerraum, so daß die Düsennadel schneller öffnet, da das gleichzeitige Zuströmen von Steuervolumen über die Zulaufdrossel abgeriegelt ist.In the proposed solution according to the invention, the pressure relief is brought about via a switching valve, which is designed as a 3/3-way valve. The valve body of the 3/3-way switching valve can be switched in several positions in the surrounding valve space. In one of the switching positions, the permanent pressurization of the control chamber via the inlet throttle can be interrupted by closing this inlet, so that the pressure relief of the control chamber via the pressure relief line and the throttle element integrated in this takes place. By inhibiting the simultaneous supply of the inlet throttle only an outflow of the control volume from the control chamber, so that the nozzle needle opens faster because the simultaneous flow of control volume is sealed off via the inlet throttle.

In dieser Ausführungsvariante fungiert die in den Ablauf vom Steuerraum der Düsennadel zugeordnete Drossel bei Druckentlastung des Steuerraumes als Ablauf- und bei Druckbeaufschlagung des Steuerraumes als dessen Zulaufdrossel.In this embodiment, the throttle associated with the discharge from the control chamber of the nozzle needle acts as a drain and when pressure is applied to the control chamber as pressure-reducing valve of the control chamber as its inlet throttle.

Ist der Ventilkörper in Kugelform beschaffen, kann dessen Betätigung zum Beispiel über einen Piezoaktor erfolgen und es können zwei Öffnungsgeschwindigkeiten eingestellt werden. Neben einem vollständigen Verschließen der Zulaufdrossel in einen unteren Sitz kann der Ventilkörper in eine Mittelstellung geschaltet werden, bei welcher der Steuerraum zwar auch druckentlastet wird, jedoch eine gleichzeitige Druckbeaufschlagung des Ventilraums des Schaltventils gegeben ist, so daß die Druckentlastung des Steuerraums mit geringerer Geschwindigkeit erfolgt.If the valve body is in the form of a sphere, its actuation can take place, for example, via a piezoactuator and two opening speeds can be set. In addition to a complete closing of the inlet throttle in a lower seat of the valve body can be switched to a middle position in which the control chamber is indeed also relieved of pressure, but a simultaneous pressurization of the valve chamber given the switching valve, so that the pressure relief of the control chamber is carried out at a lower speed.

In einer weiteren Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung ist der Zulauf von einer Hochdruckquelle wie zum Beispiel einem Hochdrucksammelraum nach wie vor mit einem Zulaufdrosselelement versehen, jedoch ist gemäß dieser weiteren Ausführungsvariante der erfindungsgemäßen Lösung die Ablaufdrossel in die Ablaufleitung vom Ventilraum des Ventilkörpers eines 3/3-Wege-Steuerventils verlegt. Mit dieser Ausführungsvariante kann eine sehr schnelle Druckentlastung des Steuerraumes erzielt werden, da die Zulaufdrossel vollständig verschlossen werden kann. Auch bei dieser zweiten Ausführungsvariante läßt sich der Ventilkörper des 3/3-Wege-Steuerventils in eine Mittelstellung bewegen, wodurch das Abströmen des Steuervolumens aus dem Steuerraum hingegen auch verlangsamt werden kann.In a further embodiment of the proposed solution according to the invention, the feed from a high-pressure source such as a high-pressure collecting chamber is still provided with an inlet throttle element, but according to this further embodiment of the solution according to the invention, the outlet throttle in the drain line from the valve chamber of the valve body of a 3 / 3- Routing control valve relocated. With this embodiment, a very rapid pressure relief of the control chamber can be achieved because the inlet throttle can be completely closed. Also in this second embodiment, the valve body of the 3/3-way control valve can be in a Move center position, whereby the outflow of the control volume from the control room, however, can also be slowed down.

Beiden Ausführungsvarianten der erfindungsgemäßen Lösung ist gemeinsam, daß der bei aus dem Stande der Technik bekannten Lösungen permanent wirkende Zulauf von unter hohem Druck stehenden Kraftstoff von der Hochdruckquelle in den Steuerraum komplett abgeriegelt werden kann. Dadurch läßt sich bei Druckentlastung des Steuerraumes mit jeder der erfindungsgemäß vorgeschlagenen Ausführungsvarianten ein schnelles Auffahren, d.h. ein schnelles Öfnen der Düsennadel, in diesen erzielen.Both variants of the solution according to the invention have in common that the solutions known from the prior art can be completely sealed off from the high-pressure source into the control room by permanently acting inlets of high-pressure fuel. As a result, when the control chamber is relieved of pressure with each of the variants of the invention proposed according to the invention, a rapid start-up, that is to say a rapid start-up, can be achieved. a quick opening of the nozzle needle, achieve in this.

Zeichnungdrawing

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

Es zeigt:

Figur 1
ein einen Steuerraum einer Düsennadel zugeordnetes Schaltventil mit Druckbe- und Druckentlastungsleitung für den Steuerraum und
Figur 2
ein dem Steuerraum zugeordnetes Schaltventil, dessen Ventilraumzulauf bzw. Ventilraumablauf jeweils Drosselelemente enthalten.
It shows:
FIG. 1
a control chamber of a nozzle needle associated switching valve with pressure and pressure relief line for the control room and
FIG. 2
a control valve associated switching valve whose valve chamber inlet or valve chamber outlet respectively contain throttle elements.

Ausführungsvariantenvariants

Figur 1 ist ein Steuerraum einer Düsennadel zu entnehmen, dem ein Schaltventil zugeordnet ist, wobei die Druckbe- und Druckentlastungsleitung des Steuerraums mit einem Drosselelement versehen ist. FIG. 1 is to remove a control chamber of a nozzle needle, which is associated with a switching valve, wherein the pressure and pressure relief line of the control chamber is provided with a throttle element.

Dieser Ausführungsvariante des der Erfindung zugrundeliegenden Lösungsgedankens ist entnehmbar, daß in einem Gehäuse 2 eines Injektorkörpers 1 ein Mehrwegeventil 3 aufgenommen ist. Das Mehrwegeventil 3 wird bevorzugt als 3/3-Wege-Steuerventil ausgebildet, dessen Ventilkörper 4 im dargestellten Ausführungsbeispiel ein kugelförmig ausgebildetes Element ist. Der Ventilkörper 4 ist im diesen umgebenden Ventilraum 5 im Gehäuse 2 des Injektorgehäuses 1 in mehrere Schaltstellungen bewegbar.This embodiment of the invention is based solution idea can be removed that in a housing 2 of an injector body 1, a multi-way valve 3 is added. The multi-way valve 3 is preferably formed as a 3/3-way control valve, the valve body 4 in the illustrated embodiment is a spherically shaped element. The valve body 4 is movable in the surrounding valve chamber 5 in the housing 2 of the injector 1 in a plurality of switching positions.

Die Betätigung des kugelförmig konfigurierten Ventilkörpers 4 des Mehrwegeventils 3 erfolgt über ein Übertragungselement 6, welches durch einen hier nicht näher dargestellten Aktor, sei es ein Piezoaktor oder sei es ein Magnetventil betätigbar ist. Anstelle der aufgezählten Komponenten kann auch ein mechanisch/hydraulischer Übersetzer als Betätigungselement des Übertragungselementes 6 vorgesehen sein. Das Übertragungselement durchsetzt eine Bohrung im Gehäuse 2 des Injektorkörpers 1. Zwischen der Außenfläche des Übertragungselementes 6 und der Bohrung im Gehäuse 2 des Injektors 1 ist ein Ringraum 8 ausgebildet, von dem aus ein Leckölablauf 9 in den Niederdruckbereich des Kraftstoffinjektors verläuft. Der Ringspalt 8 zwischen Übertragungselement 6 und Gehäuse 2 des Kraftstoffinjektors 1 fungiert als ein Ringdrosselelement. Daneben mündet in den Ventilraum 5 im Gehäuse 2 des Injektorkörpers 1 ein Zulauf 13 von einer hier nicht näher dargestellten Hochdruckquelle wie zum Beispiel eines Hochdrucksammelraumes (Common Rail).The actuation of the spherically configured valve body 4 of the multi-way valve 3 via a transmission element 6, which is actuated by an actuator not shown here, be it a piezoelectric actuator or a solenoid valve. Instead of the enumerated components, a mechanical / hydraulic translator may be provided as an actuating element of the transmission element 6. The transmission element passes through a bore in the housing 2 of the injector body 1. Between the outer surface of the transmission element 6 and the bore in the housing 2 of the injector 1, an annular space 8 is formed, from which a leakage oil outlet 9 runs in the low-pressure region of the fuel injector. The annular gap 8 between the transmission element 6 and the housing 2 of the fuel injector 1 acts as a ring throttle element. In addition, flows into the valve chamber 5 in the housing 2 of the injector body 1, an inlet 13 from a high pressure source not shown here, such as a high-pressure accumulator (common rail).

In der Darstellung gemäß Figur 1 ist in den Zulauf 13 von der Hochdruckquelle ein Zulaufdrosselelement 14 integriert, welches in einem Zulaufdrosselquerschnitt 15 ausgebildet ist. Der Zulauf 13 mündet auf der dem Übertragungselement 6, mit welchem der Ventilkörper 4 des Mehrwegeventils 3 betätigbar ist, gegenüberliegenden Seite. Ferner mündet in den Ventilraum 5 des Mehrwegeventils 3 ein Steuerraumkanal 16. Über den Steuerraumkanal 16 stehen der Steuerraum 20 und der Ventilraum 5 des Mehrwegeventils 3 in Verbindung. Der Steuerraum 20 des Kraftstoffinjektors wird von einer Wandung 21 des Gehäuses 2 begrenzt. In der Wandung 21 des Gehäuses 2 des Injektorkörpers 1 ist zudem eine Anschlagfläche 22 aufgenommen, die einer oberen Stirnseite 24 einer Düsennadel 23 gegenüberliegt, wobei die Düsennadel 23 im Gehäuse 2 des Injektorkörpers 1 in vertikaler Richtung gemäß des Doppelpfeils 25 auf- und abbewegbar ist. Über den Steuerraumkanal 16 ist der Steuerraum 20 von einem darin eingeschlossenen Steuervolumen in Entlastungsrichtung 17 druckentlastbar. Ein im Steuerraumkanal 16 aufgenommenes Drosselelement 19 fungiert in Druckentlastungsrichtung 17 in bezug auf den Steuerraum 20 als Ablaufdrossel, wohingegen das Drosselelement 19 bei umgekehrter Beaufschlagung des Steuerraumkanals 16 in Belastungsrichtung 18 als Zulaufdrossel zum Steuerraum 20 fungiert.In the illustration according to FIG. 1 is integrated into the inlet 13 of the high-pressure source, an inlet throttle element 14, which is formed in an inlet throttle 15. The inlet 13 opens on the transfer element 6, with which the valve body 4 of the multi-way valve 3 can be actuated, opposite side. Furthermore, opens into the valve chamber 5 of the multi-way valve 3, a control chamber channel 16. About the control room channel 16 are the control chamber 20 and the valve chamber 5 of the multi-way valve 3 in conjunction. The control chamber 20 of the fuel injector is bounded by a wall 21 of the housing 2. In the wall 21 of the housing 2 of the injector body 1 also a stop surface 22 is received, which faces an upper end face 24 of a nozzle needle 23, wherein the nozzle needle 23 in the housing 2 of the injector body 1 in the vertical direction according to the double arrow 25 is moved up and down. Via the control chamber channel 16, the control chamber 20 can be relieved of pressure by a control volume enclosed in the relief direction 17. A throttle element 19 accommodated in the control chamber duct 16 acts in the pressure relief direction 17 with respect to the control chamber 20 as an outlet throttle, whereas the throttle element 19 acts as an inlet throttle to the control chamber 20 when the control chamber duct 16 is loaded in the loading direction 18.

Durch Betätigung des Übertragungselementes 6 mittels eines hier nicht dargestellten Aktorelementes läßt sich der Ventilkörper 4 des Mehrwegeventils 3 in eine erste Schaltstellung 10.1 bewegen. In der ersten Schaltstellung 10.1 liegt die kugelförmige Mantelfläche des Ventilkörpers 4 am Sitz 10 des Ventilraumes 5 an. In dieser Schaltstellung strömt über den Zulauf 13 von der Hochdruckquelle unter hohem Druck stehender Kraftstoff, das Drosselelement 14 im Zulauf 13 passierend, in den Ventilraum 5 ein. Von diesem strömt der unter hohem Druck stehende Kraftstoff über den Steuerraumkanal 16 in Belastungsrichtung 18 das Drosselelement 19 passierend in den Steuerraum 20 ein. Mithin stellt sich im Steuerraum 20 ein Druckaufbau ein, so daß die Düsennadel 23 in Abwärtsrichtung bewegt wird und eine oder mehrere Einspritzöffnungen verschließt.By actuating the transmission element 6 by means of an actuator element, not shown here, the valve body 4 of the multiway valve 3 can be moved in a first switching position 10.1. In the first switching position 10.1, the spherical outer surface of the valve body 4 bears against the seat 10 of the valve chamber 5. In this switching position flows through the inlet 13 from the high pressure source under high pressure fuel, the throttle element 14 passing in the inlet 13, in the valve chamber 5 a. From this, the high-pressure fuel flows through the control chamber passage 16 in the loading direction 18 the throttle element 19 passing into the control chamber 20 a. Thus, a pressure buildup in the control chamber 20, so that the nozzle needle 23 is moved in the downward direction and closes one or more injection openings.

Ist hingegen der kugelförmig konfigurierte Ventilkörper 4 des Mehrwegeventils 3 in seine zweite Schaltstellung 11.1, d.h. in seinen unteren Sitz 11 im Ventilraum 5 gefahren, so ist der Zulauf 13 von der hier nicht dargestellten Hochdruckquelle abgeriegelt. In der Schaltstellung kann eine sehr schnelle Druckentlastung des Steuerraums 20 über den Steuerraumkanal 16 in Druckentlastungsrichtung 17 über den Ventilraum 5, den Ringspalt in den Leckölablauf 9 erfolgen. Je schneller ein Druckabbau im Steuerraum 20 erfolgen kann, ein desto schnelleres Öffnen der Düsennadel 23 aus ihrem hier nicht dargestellten düsennadelseitigen Sitz läßt sich erreichen. Von Vorteil bei der Ausführungsvariante gemäß Figur 1 ist der Umstand, daß eine ansonsten permanent wirkende Zulaufdrossel 14 eines Zulaufs 13 von einer Hochdruckquelle von einem Steuerraumvolumen abgeriegelt werden kann, so daß sichergestellt ist, daß eine schnelle Druckentlastung im Steuerraum 20 erfolgt.If, however, the spherically configured valve body 4 of the multiway valve 3 in its second switching position 11.1, that is driven in its lower seat 11 in the valve chamber 5, the inlet 13 is sealed off from the high pressure source, not shown here. In the switching position, a very rapid pressure relief of the control chamber 20 via the control chamber channel 16 in the pressure relief direction 17 via the valve chamber 5, the annular gap in the leak oil 9 take place. The faster a pressure reduction in the control chamber 20 can take place, the faster the opening of the nozzle needle 23 from its nozzle needle-side seat, not shown here, can be achieved. Advantageous in the embodiment according to FIG. 1 is the fact that an otherwise permanently acting inlet throttle 14 of an inlet 13 can be sealed off from a high-pressure source of a control chamber volume, so that it is ensured that a rapid pressure relief in the control chamber 20 takes place.

Wird hingegen der kugelförmig konfigurierte Ventilkörper 4 in seine Mittelstellung 12 bewegt, so läßt sich das Abströmen des Steuerraumvolumens aus dem Steuerraum 20 verlangsamen, da in Mittelstellung 12 der Zulauf 13, der in den Ventilraum 5 mündet, offensteht und dadurch ein Gegendruck in bezug auf die Strömungsrichtung des Steuerraumvolumens aus dem Steuerraum 20 erzeugt wird. Dadurch wird der Steuerraum 20 im Gehäuse 2 des Injektorkörpers 1 langsamer entlastet, d.h. die Düsennadel 23 fährt langsamer in Richtung auf die an der Wandung 21 ausgebildete Anschlagfläche 22 zu, so daß die Einspritzöffnungen entsprechend mit einer zweiten, verglichen zur zweiten Schaltstellung 11.2 geringeren Geschwindigkeit langsamer öffnen.If, however, the spherical valve body 4 is moved to its central position 12, so can the outflow of the control chamber volume from the control chamber 20 slow down, as in the middle position 12 of the inlet 13, which opens into the valve chamber 5, is open and thereby a back pressure with respect to the Flow direction of the control chamber volume from the control chamber 20 is generated. As a result, the control chamber 20 is relieved more slowly in the housing 2 of the injector body 1, i. the nozzle needle 23 moves slower in the direction of the stop surface 22 formed on the wall 21, so that the injection openings open more slowly in accordance with a second, compared to the second switching position 11.2 slower speed.

Der Darstellung gemäß Figur 2 ist eine weitere Ausführungsvariante des der Erfindung zugrundeliegenden Gedankens zu entnehmen, bei dem ein dem Steuerraum zugeordnetes Schaltventil einen Ventilraum umfaßt, dessen Zu- bzw. Ablauf mit Drosselelementen versehen sind.The representation according to FIG. 2 is a further embodiment of the invention of the underlying idea, in which a control chamber associated switching valve comprises a valve chamber, the inlet and outlet are provided with throttle elements.

Analog zur Darstellung gemäß Figur 1 ist der Ventilraum des Mehrwegeventils 3, bevorzugt als 3/3-Wege-Steuerventil ausgestaltet, über einen Zulauf 13 mit einem Drosselelement 14 mit einer hier nicht dargestellten Hochdruckquelle verbindbar. Vom Ventilraum 5 erstreckt sich ein Steuerraumkanal 16 zu einem Steuerraum 20 im Gehäuse 2 des Injektorkörpers 1, welcher einerseits von einer Wandung 21 des Gehäuses 2 und andererseits von einer Stirnseite 24 der im Gehäuse 2 des Injektorkörpers 1 in Bewegungsrichtung 25 bewegbaren Düsennadel 23 begrenzt wird. Auch an der gehäuseseitigen Steuerraumwandung 21 des Steuerraumes 20 ist analog zur Darstellung gemäß Figur 1 eine Anschlagfläche 22 ausgebildet.Analogous to the representation according to FIG. 1 is the valve chamber of the multi-way valve 3, preferably designed as a 3/3-way control valve, connected via an inlet 13 with a throttle element 14 with a high pressure source not shown here. From the valve chamber 5, a control chamber duct 16 extends to a control chamber 20 in the housing 2 of the injector body 1, which on the one hand by a wall 21 of the housing 2 and on the other hand by an end face 24 of the housing 2 of the injector 1 in the direction of movement 25 movable nozzle needle 23 is limited. Also on the housing side control room wall 21 of the control chamber 20 is analogous to the representation according to FIG. 1 a stop surface 22 is formed.

Im Unterschied zur Darstellung gemäß Figur 1 umfaßt der Steuerraumkanal 16, der den druckentlastbaren Steuerraum 20 mit dem Ventilraum 5 verbindet, kein Drosselelement. Der Steuerraumkanal 16 ist lediglich in eine Druckentlastungsrichtung 17 in bezug auf den Steuerraum 20 sowie in eine Belastungsrichtung 18 mit einem Fluid, zum Beispiel Kraftstoff beaufschlagbar. Im Unterschied zur Darstellung gemäß Figur 1 ist das gemäß Figur 1 im Steuerraumkanal 16 aufgenommene Drosselelement 19 nunmehr im vom Ringspalt 8 zwischen Übertragungselement 6 und Gehäuse 2 abzweigenden Leckölablauf 9 integriert.In contrast to the representation according to FIG. 1 comprises the control chamber passage 16 which connects the pressure-relieving control chamber 20 with the valve chamber 5, no throttle element. The control chamber passage 16 is only in a pressure relief direction 17 with respect to the control chamber 20 and in a loading direction 18 with a fluid, for example fuel acted upon. In contrast to the representation according to FIG. 1 is that according to FIG. 1 Throttle element 19 accommodated in control chamber channel 16 is now integrated in leakage oil outlet 9 branching off from annular gap 8 between transmission element 6 and housing 2.

Am Ventilraum 5, welcher den kugelförmig konfigurierten Ventilkörper 4 des Mehrwegeventils 3 umschließt, sind ein oberer Sitz 10 entsprechend einer ersten Schaltstellung 10.1 sowie ein diesem gegenüberliegender unterer Sitz 11 ausgebildet, in welchen der Ventilkörper 4 des Mehrwegeventils 3 in eine zweite Schaltposition 11.1 stellbar ist. Im in Figur 2 dargestellten Zustand ist der Ventilkörper 4 des Mehrwegeventils 3 in eine Mittelstellung 12 geschaltet.At the valve chamber 5, which encloses the spherically configured valve body 4 of the multi-way valve 3, an upper seat 10 corresponding to a first switching position 10.1 and a lower seat 11 opposed thereto are formed, in which the valve body 4 of the multi-way valve 3 is adjustable to a second switching position 11.1. Im in FIG. 2 shown state, the valve body 4 of the multi-way valve 3 is connected in a middle position 12.

Die Schaltstellungen 10.1, 11.1 bzw. 12 des Ventilkörpers 4 entsprechen im wesentlichen den Schaltstellungen 10.1, 11.1 bzw. 12, die bereits im Zusammenhang mit der Ausführungsvariante gemäß Figur 1 beschrieben wurden.The switching positions 10.1, 11.1 and 12 of the valve body 4 substantially correspond to the switching positions 10.1, 11.1 and 12, respectively, already in connection with the embodiment according to FIG FIG. 1 have been described.

Im Unterschied zur Darstellung gemäß Figur 1 ist durch die Entfernung des Drosselelementes 19 aus dem Steuerraumkanal 16, der Steuerraum 20 und Ventilraum 5 miteinander verbindet, eine höhere Strömungsgeschwindigkeit des Steuerraumvolumens vom Steuerraum 20 in den Ventilraum 5 des Mehrwegeventils 3 erzielbar. Dadurch läßt sich eine im Vergleich zur Darstellung gemäß Figur 1 nochmals erhöhte Strömungsgeschwindigkeit bei der Druckentlastung des Steuerraumes 20 erzielen.In contrast to the representation according to FIG. 1 is achieved by the removal of the throttle element 19 from the control chamber passage 16, the control chamber 20 and the valve chamber 5 with each other, a higher flow rate of the control chamber volume from the control chamber 20 in the valve chamber 5 of the multi-way valve 3 achievable. As a result, in comparison to the representation according to FIG. 1 achieve again increased flow velocity in the pressure relief of the control chamber 20.

Auch gemäß der Ausführungsvariante nach Figur 2 verschließt das in seine zweite Schaltstellung 11.1 gestellte Mehrwegeventil 3 den ansonsten permanent wirkenden Zulauf von Kraftstoff über den Zulauf 13 von einer hier nicht dargestellten Hochdruckquelle in den Ventilraum 5 und von dort über den Steuerraumkanal 16 in den Steuerraum 20. Der Zulauf 13 wird in der zweiten Schaltstellung 11.1 des Ventilskörpers 4 des Mehrwegeventils 3 komplett abgeschaltet. Damit wird erreicht, daß sich kein Bypass während der Einspritzung einstellt; daneben ist in der Mittelstellung 12 des Ventilkörpers 4 im Ventilraum 5 zwischen dem oberen Sitz 10 und dem unteren Sitz 11 eine Variationsmöglichkeit gegeben, wodurch ein schnelles und langsames Öffnen erreicht werden kann, nimmt der Ventilkörper 4 seine Mittelstellung 12 gemäß der Darstellung in Figur 2 zwischen oberem Sitz 10 und unterem Sitz 11 ein.Also according to the embodiment according to FIG. 2 closes in its second switching position 11.1 asked multi-way valve 3 the otherwise permanently acting inlet of fuel via the inlet 13 from a high pressure source, not shown here in the valve chamber 5 and from there via the control chamber passage 16 into the control chamber 20. The inlet 13 is in the second Switched position 11.1 of the valve body 4 of the multi-way valve 3 completely switched off. This ensures that no bypass occurs during the injection; In addition, given in the middle position 12 of the valve body 4 in the valve chamber 5 between the upper seat 10 and the lower seat 11 is a possibility of variation, whereby a fast and slow opening can be achieved, takes the valve body 4 its center position 12 as shown in FIG FIG. 2 between the upper seat 10 and lower seat 11 a.

Bei einem schnelleren Öffnen der Düsennadel, d.h. bei schneller Druckentlastung des Steuerraums 20 und einem damit verbundenen schnellen Auffahren der Düsennadel 23 in vertikale Richtung entsprechend des Bewegungspfeils 25 bei vollständiger Abriegelung des Zulaufs 13 von der Hochdruckquelle, kann eine Druckentlastung des Steuerraumes 20 mit einer ersten höheren Geschwindigkeit erfolgen, wenn im Steuerraumkanal 16 gemäß der Darstellung in Figur 2 kein Drosselelement 19 aufgenommen ist. Wird der Ausführungsvariante in Figur 2 der Ventilkörper 4 in seine Mittelstellung 12 gefahren, so läßt sich eine etwas langsamere Druckentlastungsgeschwindigkeit in Druckentlastungsrichtung 17 im Steuerraumkanal 16 in den Ventilraum 5 einstellen. Dies trifft im wesentlichen auch auf die Ausführungsvariante gemäß der Darstellung in Figur 1 zu, wobei die Abströmgeschwindigkeit des Steuerraumvolumens aus dem Steuerraum 20 dadurch im Vergleich zur Lösung gemäß Figur 2 herabgesetzt ist, daß im Steuerraumkanal 16 ein Drosselelement 19 aufgenommen ist. Dieses befindet sich gemäß der Lösung nach Figur 2 im Leckölablauf 9 niederdruckseitig hinter dem Ventilraum 5 des vorzugsweise als 3/3-Wege-Steuerventils konfigurierten Mehrwegeventils.In a faster opening of the nozzle needle, ie at rapid pressure relief of the control chamber 20 and an associated rapid movement of the nozzle needle 23 in the vertical direction corresponding to the movement arrow 25 with complete closure of the inlet 13 from the high pressure source, a pressure relief of the control chamber 20 with a first higher Speed occur when in the control room channel 16 as shown in FIG FIG. 2 no throttle element 19 is received. Is the variant in FIG. 2 the valve body 4 moved to its central position 12, so can a slightly slower pressure relief rate in the pressure relief direction 17 in the control chamber channel 16 in the valve chamber 5 set. This applies essentially to the embodiment variant as shown in FIG FIG. 1 to, wherein the outflow velocity of the control chamber volume from the control chamber 20 thereby compared to the solution according to FIG. 2 is reduced, that in the control chamber channel 16, a throttle element 19 is received. This is according to the solution FIG. 2 in the drainage 9 low-pressure side behind the valve chamber 5 of the preferably configured as a 3/3-way control valve multi-way valve.

Das mit den dargestellten Ausführungsvarianten gemäß Figuren 1 und 2 erzielbare schnelle Öffnen der Düsennadel 23 aus ihrem Sitz führt zur Reduzierung von Abgasemissionen einer solcherart betriebenen selbstzündenden Brennkraftmaschine. Durch die Mittelstellung 12, in welche der Ventilkörper 4 des Mehrwegeventils 3 stellbar ist, kann auch ein langsames Öffnen der Düsennadel 3 in den Steuerraum 20 und dadurch bedingt eine langsamer erfolgende Freigabe der Einspritzöffnung erzielt werden. Dies gibt die Möglichkeit, den Einspritzverlauf zu formen und an den Fortschritt der Verbrennung im Brennraum der Verbrennungskraftmaschine anzupassen.The with the illustrated embodiments according to FIGS. 1 and 2 achievable fast opening of the nozzle needle 23 from its seat leads to the reduction of exhaust emissions of such a self-igniting internal combustion engine operated. By the center position 12, in which the valve body 4 of the multi-way valve 3 is adjustable, and a slow opening of the nozzle needle 3 in the control chamber 20 and thereby conditionally a slower successful release of the injection port can be achieved. This makes it possible to shape the course of injection and to adapt it to the progress of the combustion in the combustion chamber of the internal combustion engine.

Claims (7)

  1. Fuel injector for internal combustion engines having an injector body (1), in the housing (2) of which is held a nozzle needle (23) which opens or closes off injection openings and which can be actuated by means of a control space (20) which can be relieved of pressure and which is acted on with highly pressurized fuel from a high-pressure source via an inflow (13), with a valve space (5) of a multi-directional valve (3) being formed in the housing (2) of the injector body (1), with the multi-directional valve (3) comprising a spherical valve body (4), with the control space (20) being connected to the valve space (5) of the multi-directional valve (3) via a control space duct (16) which, with respect to the control space (20), can be acted on both in the release direction (17) and also in the loading direction (18), with the control space duct (16), the inflow (13) from the high-pressure source and an outflow (9) opening out into the valve space (5) of the multi-directional valve (3), characterized in that the multi-directional valve (3) is embodied as a 3/3 directional control valve and in that the valve body (4) of the multi-directional valve (3) in the valve space (5) can be placed into a first seat (10) in a first switching position (10.1), into a second seat (11) in a second switching position (11.1) and into a central position (12), wherein in the second switching position (11.1) of the valve body (4) in the valve space (5), the inflow (13) from the high-pressure source is closed off and a release of pressure from the control space (20) takes place in the release direction (17) through the control space duct (16) at a first speed, and wherein in the central position (12), the inflow (13) which opens out into the valve space (5) is open and, as a result, a back pressure which acts counter to the release direction (17) can be generated in order to slow the release of pressure from the control space (20).
  2. Fuel injector according to Claim 1, characterized in that the valve body (4) of the multi-directional valve (3) can be actuated by means of a transmission element (6) which is assigned to the outflow-side region of the valve space (5) which merges into a leakage oil outflow (9).
  3. Fuel injector according to Claim 2, characterized in that an annular gap (8) which functions as an annular throttle is formed between the transmission element (6) and the housing (2).
  4. Fuel injector according to Claim 1, characterized in that an outflow throttle element (19) is held in the control space duct (16).
  5. Fuel injector according to Claim 1, characterized in that an outflow throttle element (19) is held in the leakage oil outflow (9).
  6. Fuel injector according to Claim 1, characterized in that, in the central position (12) of the valve body (4) in the valve space (5), a release of pressure from the control space (20) takes place in the release direction (15) through the control space duct (16) at a second speed.
  7. Fuel injector according to Claim 1, characterized in that, in the first switching position (10.1) of the valve body (4) in the valve space (5), the pressure loading of the control space (20) takes place in the loading direction (18) via the control space duct (16).
EP02754253A 2001-06-29 2002-06-21 Fuel injector switch valve for the compression/decompression of a control chamber Expired - Lifetime EP1404966B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10131617 2001-06-29
DE2001131617 DE10131617A1 (en) 2001-06-29 2001-06-29 Fuel injector switching valve for pressure relief / loading of a control room
PCT/DE2002/002290 WO2003004864A1 (en) 2001-06-29 2002-06-21 Fuel injector switch valve for the compression/decompression of a control chamber

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EP1404966B1 true EP1404966B1 (en) 2008-02-20

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WO (1) WO2003004864A1 (en)

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DE102004024215A1 (en) * 2004-05-15 2005-12-08 L'orange Gmbh control valve
JP4855946B2 (en) 2006-06-08 2012-01-18 株式会社デンソー Fuel injection valve
JP2008002306A (en) * 2006-06-21 2008-01-10 Denso Corp Fuel injection valve
JP5043761B2 (en) 2008-06-18 2012-10-10 本田技研工業株式会社 Fuel injection device
DE102010040989A1 (en) * 2010-09-17 2012-03-22 Continental Automotive Gmbh Control valve unit for a fuel injector
CH704454A1 (en) * 2011-02-08 2012-08-15 Liebherr Machines Bulle Sa Injection apparatus for a fluid.
DE102012202055A1 (en) 2012-02-10 2013-08-14 Robert Bosch Gmbh Fuel injector for fuel injection system, particularly common-rail injection system, has pressure actuatable valve, which is formed in intake channel for separating connection of control chamber with intake channel
DE102012220025A1 (en) 2012-06-29 2014-01-02 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102012221624A1 (en) 2012-11-27 2014-05-28 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102012223199A1 (en) 2012-12-14 2014-06-18 Robert Bosch Gmbh Fuel injection valve for internal combustion engine, has control chamber that is connected to pressure chamber via opening formed in inlet throttle which is closed by longitudinal movement of shift sleeve
DE102012224398A1 (en) 2012-12-27 2014-07-03 Robert Bosch Gmbh Fuel injection valve for injecting fuel into combustion chambers of high-speed self-ignition engine of vehicle, has switching case cooperating with sealing seat placed at inner side of valve piece to open and close inlet throttle

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WO2003004864A1 (en) 2003-01-16
DE50211740D1 (en) 2008-04-03
DE10131617A1 (en) 2003-01-23

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