WO2003004864A1 - 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
WO2003004864A1
WO2003004864A1 PCT/DE2002/002290 DE0202290W WO03004864A1 WO 2003004864 A1 WO2003004864 A1 WO 2003004864A1 DE 0202290 W DE0202290 W DE 0202290W WO 03004864 A1 WO03004864 A1 WO 03004864A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control chamber
chamber
fuel injector
anspmch
Prior art date
Application number
PCT/DE2002/002290
Other languages
German (de)
French (fr)
Inventor
Friedrich Boecking
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to DE50211740T priority Critical patent/DE50211740D1/en
Priority to EP02754253A priority patent/EP1404966B1/en
Publication of WO2003004864A1 publication Critical patent/WO2003004864A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-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
    • F02M47/027Electrically actuated valves draining the chamber to release the closing pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0014Valves characterised by the valve actuating means
    • F02M63/0015Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0014Valves characterised by the valve actuating means
    • F02M63/0015Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036Lift 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045Three-way valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0059Arrangements of valve actuators
    • F02M63/0068Actuators specially adapted for partial and full opening of the valves

Definitions

  • injection systems with high-pressure plenums are used today 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 injection process depends on the injection processes, among other things. on the speed at which the nozzle needle in the housing of the fuel injector opens or closes the injector.
  • the composition of the exhaust gas of the internal combustion engine for example with regard to HC emissions, is highly dependent on the course of the injection into the combustion chamber.
  • 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 furthermore has a piston-shaped extension over 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.
  • US 5,460,329 relates to a fuel injector with pressure-intensifying translation.
  • the fuel reaches the pressure booster in the injector via an electromagnetic control valve designed as a slide valve.
  • the electromagnetic pressure on the control valve puts the fuel from the pressure booster under high pressure at specified times or crankshaft angles.
  • the fuel under high pressure causes the injector valve needle to lift from its seat. This clears the way for the fuel to the injector injector.
  • DE 199 08 418 Cl relates to a control valve for use in a storage injection system for a diesel engine.
  • the control valve includes a housing with an input port, an output port. and a return connection.
  • a first seat valve with a first valve body and a second seat valve with a second valve body are provided.
  • the first poppet valve is located between the outlet port and the return port and is normally closed, the second poppet valve between the inlet port and the outlet port is normally open.
  • 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 a conical valve sealing surface on its combustion chamber end, with which it interacts with a conical valve seat surface on the valve body, which is formed on the inwardly projecting 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 circumferential sealing edge. This sealing edge formed when the injection valve is closed seals off a pressure space adjacent upstream of the sealing edge when the injection valve is closed. Downstream of this sealing edge, at least one injection opening, which opens into the combustion chamber of the internal combustion engine to be supplied, is provided in the wall of the valve body and leads away from the valve seat surface.
  • valve member The operating times of the valve member are too long for fast-switching injection valves due to the large hydraulic forces that occur. Furthermore, due to the large number of components lying axially one behind the other, this fuel injection valve is very large, which limits the usability on engines with little available space.
  • DE 197 44 518 AI 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 which is arranged in a valve body and 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. cut interacts.
  • the valve member is slidably guided by an internal guide on a pin of a stationary insert body.
  • 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 into several positions in the valve space surrounding it.
  • 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 takes place via the pressure relief line and the throttle element integrated into it.
  • the throttle assigned to the outlet from the control chamber of the nozzle needle acts as an outlet throttle when the control chamber is depressurized and as its inlet throttle when the control chamber is pressurized.
  • valve body If the valve body is spherical, it can be actuated, for example, using a piezo actuator and two opening speeds can be set. In addition to completely closing the inlet throttle in a lower seat, the valve body can be switched to a central position, in which the control chamber is also relieved of pressure, but there is simultaneous pressurization of the valve chamber of the switching valve, so that the pressure relief of the control chamber takes place at a lower speed.
  • the inlet from a high-pressure source such as, for example, a high-pressure collection space is still provided with an inlet throttle element, but according to this further embodiment variant of the solution according to the invention, the outlet throttle is in the outlet line from the valve chamber of the valve body of a 3/3 Directional control valve relocated.
  • a very rapid pressure relief of the control room can be achieved, since the inlet throttle can be completely closed.
  • the valve body of the 3/3-way control valve can be in one Move middle position, whereby the outflow of the control volume from the control room can also be slowed down.
  • Figure 1 is a control chamber of a nozzle needle associated switching valve with pressure and pressure relief line for the control room and
  • Figure 2 is a control valve assigned to the control chamber, the valve chamber inlet and valve chamber outlet contain throttle elements.
  • FIG. 1 shows a control chamber of a nozzle needle, to which a switching valve is assigned, the pressure relief and pressure relief line of the control chamber being provided with a throttle element.
  • a multi-way valve 3 is accommodated in a housing 2 of an injector body 1.
  • the multi-way valve 3 is preferably designed as a 3/3-way control valve, the valve body 4 of which is a spherical element in the exemplary embodiment shown.
  • the valve body 4 can be moved into several switching positions in the valve chamber 5 surrounding it in the housing 2 of the injector housing 1.
  • the actuation of the spherically configured valve body 4 of the multi-way valve 3 takes place via a transmission element 6, which can be actuated by an actuator, not shown here, be it a piezo actuator or a solenoid valve.
  • a mechanical / hydraulic translator can also be provided as the 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 leak oil drain 9 runs into 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 functions as an annular throttle element.
  • an inlet 13 from a high-pressure source not shown here, such as a high-pressure collecting chamber (common rail), opens into the valve chamber 5 in the housing 2 of the injector body 1.
  • an inlet throttle element 14 is integrated in the inlet 13 from the high-pressure source, which element is designed in an inlet throttle cross section 15.
  • the inlet 13 opens out on the side opposite the transmission element 6, with which the valve body 4 of the multi-way valve 3 can be actuated.
  • a control chamber duct 16 also opens into the valve chamber 5 of the multi-way valve 3.
  • the control chamber 20 and the valve chamber 5 of the multi-way valve 3 are connected via the control chamber duct 16.
  • the control chamber 20 of the fuel injector is delimited by a wall 21 of the housing 2.
  • a stop surface 22 is also received, which is opposite an upper end face 24 of a nozzle needle 23, the nozzle needle 23 in the housing 2 of the injector body 1 being movable up and down in the vertical direction according to the double arrow 25.
  • the control chamber 20 can be depressurized in the relief direction 17 from a control volume enclosed therein.
  • a throttle element 19 accommodated in the control chamber duct 16 functions as a discharge throttle in the pressure relief direction 17 with respect to the control chamber 20, whereas the throttle element 19 functions as an inlet throttle to the control chamber 20 when the control chamber duct 16 is acted upon in the opposite direction.
  • the valve body 4 of the multi-way valve 3 can be moved into 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.
  • fuel under high pressure passing through the throttle element 14 in the inlet 13 flows into the valve chamber 5 via the inlet 13 from the high-pressure source.
  • the fuel which is under high pressure, flows from the latter via the control chamber duct 16 in the load direction 18 the throttle element 19 passing into the control chamber 20.
  • pressure builds up 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 spherically configured valve body 4 of the multi-way valve 3 is in its second switching position 11.1, i.e. moved into its lower seat 11 in the valve chamber 5, the inlet 13 is sealed off from the high pressure source, not shown here.
  • the control chamber 20 can be relieved of pressure very rapidly via the control chamber duct 16 in the pressure relief direction 17 via the valve chamber 5, the annular gap into the leakage oil drain 9. The faster the pressure can be reduced in the control chamber 20, the faster the nozzle needle 23 can be opened from its nozzle needle-side seat, not shown here. This is an advantage in the embodiment variant according to FIG.
  • the spherically configured valve body 4 If, on the other hand, the spherically configured valve body 4 is moved into its central position 12, the outflow of the control chamber volume from the control chamber 20 can be slowed down, since in the central position 12 the inlet 13, which opens into the valve chamber 5, is open and thereby a counterpressure is related is generated on the flow direction of the control chamber volume from the control chamber 20. As a result, the control chamber 20 is in the housing
  • FIG. 2 shows a further embodiment variant of the concept on which the invention is based, in which a switching valve assigned to the control chamber comprises a valve chamber, the inlet and outlet of which are provided with throttle elements.
  • valve chamber of the multi-way valve 3 can be connected via an inlet 13 to a throttle element 14 with a high-pressure source, not shown here.
  • a control chamber duct 16 extends from the valve chamber 5 to a control chamber 20 in the housing 2 of the injector body 1, which is delimited on the one hand by a wall 21 of the housing 2 and on the other hand by an end face 24 of the nozzle needle 23 which can be moved in the direction of movement 25 in the housing 2 of the injector body 1.
  • a stop surface 22 is formed analogously to the illustration according to FIG.
  • control chamber channel 16 which connects the pressure-relieved control chamber 20 to the valve chamber 5, does not comprise a throttle element.
  • the control chamber duct 16 can only be acted upon in a pressure relief direction 17 with respect to the control chamber 20 and in a load direction 18 with a fluid, for example fuel.
  • the throttle element 19 accommodated in the control chamber duct 16 according to FIG. 1 is now integrated in the leak oil drain 9 branching off from the annular gap 8 between the transmission element 6 and the housing 2.
  • valve body 4 of the multi-way valve 3 On the valve chamber 5, which surrounds 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 an opposing lower seat 11 are formed, in which the valve body 4 of the multi-way valve 3 can be set to a second switching position 11.1 is.
  • the valve body 4 of the multi-way valve 3 In the state shown in Figure 2, the valve body 4 of the multi-way valve 3 is in a central position
  • the switch positions 10.1, 11.1 and 12 of the valve body 4 essentially correspond to the switch positions 10.1, 11.1 and 12, which have already been described in connection with the embodiment variant according to FIG.
  • a higher flow rate of the control chamber volume from the control chamber 20 into the valve chamber 5 of the multi-way valve 3 can be achieved by removing the throttle element 19 from the control chamber channel 16, which connects the control chamber 20 and the valve chamber 5.
  • a further increased flow velocity in the pressure relief of the control chamber 20 can be achieved compared to the illustration according to FIG. 1.
  • the multi-way valve 3 placed in its second switching position 11.1 closes the otherwise permanently acting inflow of fuel via the inflow 13 from a high-pressure source (not shown here) into the valve chamber 5 and from there via the control chamber duct 16 into the control chamber 20.
  • pressure relief of the control chamber 20 can take place at a first higher speed if in the control chamber duct 16 according to no throttle element 19 is included in the illustration in FIG. If the embodiment variant in FIG. 2, the valve body 4 is moved into its central position 12, a somewhat slower pressure relief speed in the pressure relief direction 17 in the control chamber channel 16 can be set in the valve chamber 5. This essentially also applies to the embodiment variant as shown in FIG. 1, the outflow speed of the control chamber volume from the control chamber 20 being reduced in comparison to the solution according to FIG.
  • a throttle element 19 is accommodated in the control chamber channel 16.
  • this is located in the leak oil drain 9 on the low pressure side behind the valve chamber 5 of the multi-way valve, which is preferably configured as a 3/3-way control valve.
  • the rapid opening of the nozzle needle 23 from its seat that can be achieved with the illustrated embodiment variants according to FIGS. 1 and 2 leads to the reduction of exhaust gas emissions of a self-igniting internal combustion engine operated in this way.
  • the central position 12 in which the Ventilgro ⁇ er 4 of the multi-way valve 3 can be adjusted, a slow opening of the nozzle needle 3 in the control chamber 20 and thus a slower release of the injection opening can be achieved.
  • This gives the possibility of shaping the course of the injection and adapting it to the progress of the combustion in the combustion chamber of the internal combustion engine.

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

Kraftstoffinjektor-Schaltventil zur Druckentlastung/Belastung eines SteuerraumesFuel injector switching valve for pressure relief / loading of a control room
Technisches GebietTechnical field
Bei Kraftstoffeinspritzsystemen für luftverdichtende Verbrennungskraftmaschinen werden heute Einspritzsysteme mit Hochdrucksammeiräumen (Common Rail) eingesetzt, um wäh- rend 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 Kraftstoffϊnjektors 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.In fuel injection systems for air-compressing internal combustion engines, injection systems with high-pressure plenums (common rail) are used today 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 injection process depends on the injection processes, among other things. on the speed at which the nozzle needle in the housing of the fuel injector opens or closes the injector. The composition of the exhaust gas of the internal combustion engine, for example with regard to HC emissions, is highly dependent on the course of the injection into the combustion chamber.
Stand der TechnikState of the art
DE 199 10 589 AI betrifft ein Einspritzventil für eine Brennkraftmaschine. Ein Servoventil weist ein bewegliches Ventilelement auf, an dem ein Drosselelement in Kraftstofffließ- richtung 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. 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 An- steuerung 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 Cl 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.DE 199 10 589 AI 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 furthermore has a piston-shaped extension over 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, a throttled connection to the injection nozzle of the injection system is to be established in the initial phase of the injection. In the further course of the injection process, when the servo valve opens further, bypassing the initially effective throttle, a direct connection to the injection nozzle is established. US 5,460,329 relates to a fuel injector with pressure-intensifying translation. The fuel reaches the pressure booster in the injector via an electromagnetic control valve designed as a slide valve. The electromagnetic pressure on the control valve puts the fuel from the pressure booster under high pressure at specified times or crankshaft angles. The fuel under high pressure causes the injector valve needle to lift from its seat. This clears the way for the fuel to the injector injector. DE 199 08 418 Cl relates to a control valve for use in a storage injection system for a diesel engine. The control valve includes a housing with an input port, an output port. and a return connection. Furthermore, a first seat valve with a first valve body and a second seat valve with a second valve body are provided. The first poppet valve is located between the outlet port and the return port and is normally closed, the second poppet valve between the inlet port and the outlet port is normally open. 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 Ventil- körper 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 hintereinanderliegen- den 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 a conical valve sealing surface on its combustion chamber end, with which it interacts with a conical valve seat surface on the valve body, which is formed on the inwardly projecting 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 circumferential sealing edge. This sealing edge formed when the injection valve is closed seals off a pressure space adjacent upstream of the sealing edge when the injection valve is closed. Downstream of this sealing edge, at least one injection opening, which opens into the combustion chamber of the internal combustion engine to be supplied, is provided in the wall of the valve body and leads away from the valve seat surface. The operating times of the valve member are too long for fast-switching injection valves due to the large hydraulic forces that occur. Furthermore, due to the large number of components lying axially one behind the other, this fuel injection valve is very large, which limits the usability on engines with little available space.
DE 197 44 518 AI zeigt ein Kraftstoffeinspritzventil für Brennkraftmaschinen. Es handelt sich um ein Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem in einem Ventil- körper 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 Einspritzquer- schnittes zusammenwirkt. Dabei ist das Ventilglied über eine Innenführung gleitverschieb- bar auf einem Zapfen eines ortsfesten Einsatzkörpers geführt.DE 197 44 518 AI 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 which is arranged in a valve body and 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. cut interacts. The valve member is slidably guided by an internal guide on a pin of a stationary insert body.
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 solution proposed 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 into several positions in the valve space surrounding it. In one of the switch 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 takes place via the pressure relief line and the throttle element integrated into it. By preventing the simultaneous inflow from the inflow throttle, there is only an outflow of the control volume from the control chamber, so that the nozzle needle opens more quickly because the simultaneous inflow of control volumes via the inflow throttle is blocked.
In dieser Ausführungsvariante fungiert die in den Ablauf vom Steuerraum der Düsennadel zugeordnete Drossel bei Druckentlastung des Steuerraumes als Ablauf- und bei Druckbe- aufschlagung des Steuerraumes als dessen Zulaufdrossel.In this embodiment variant, the throttle assigned to the outlet from the control chamber of the nozzle needle acts as an outlet throttle when the control chamber is depressurized and as its inlet throttle when the control chamber is pressurized.
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 spherical, it can be actuated, for example, using a piezo actuator and two opening speeds can be set. In addition to completely closing the inlet throttle in a lower seat, the valve body can be switched to a central position, in which the control chamber is also relieved of pressure, but there is simultaneous pressurization of the valve chamber of the switching valve, so that the pressure relief of the control chamber takes place at a lower speed.
In einer weiteren Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung ist der Zulauf von einer Hochdruckquelle wie zum Beispiel einem Hochdrucksammeiraum 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 Ausfuhrungsvariante 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 variant of the solution proposed according to the invention, the inlet from a high-pressure source such as, for example, a high-pressure collection space is still provided with an inlet throttle element, but according to this further embodiment variant of the solution according to the invention, the outlet throttle is in the outlet line from the valve chamber of the valve body of a 3/3 Directional control valve relocated. With this embodiment variant, a very rapid pressure relief of the control room can be achieved, since the inlet throttle can be completely closed. In this second embodiment variant, the valve body of the 3/3-way control valve can be in one Move middle position, whereby the outflow of the control volume from the control room 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 versions of the solution according to the invention have in common that the supply of fuel under high pressure, which is permanently effective in the case of solutions known from the prior art, can be completely blocked off from the high-pressure source into the control chamber. As a result, when the control chamber is relieved of pressure, rapid opening, i.e. achieve a quick opening of the nozzle needle in this.
Zeichnungdrawing
Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.The invention is described in more detail below with reference to the drawing.
Es zeigt:It shows:
Figur 1 ein einen Steuerraum einer Düsennadel zugeordnetes Schaltventil mit Druckbe- und Druckentlastungsleitung für den Steuerraum undFigure 1 is a control chamber of a nozzle needle associated switching valve with pressure and pressure relief line for the control room and
Figur 2 ein dem Steuerraum zugeordnetes Schaltventil, dessen Ventilraumzulauf bzw. Ventilraumablauf jeweils Drosselelemente enthalten.Figure 2 is a control valve assigned to the control chamber, the valve chamber inlet and valve chamber outlet 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 shows a control chamber of a nozzle needle, to which a switching valve is assigned, the pressure relief and pressure relief line of the control chamber being 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. 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 Betäti- gungselement 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 Hochdrucksammeiraumes (Com- mon Rail).It can be seen from this embodiment variant of the concept of the solution on which the invention is based that a multi-way valve 3 is accommodated in a housing 2 of an injector body 1. The multi-way valve 3 is preferably designed as a 3/3-way control valve, the valve body 4 of which is a spherical element in the exemplary embodiment shown. The valve body 4 can be moved into several switching positions in the valve chamber 5 surrounding it in the housing 2 of the injector housing 1. The actuation of the spherically configured valve body 4 of the multi-way valve 3 takes place via a transmission element 6, which can be actuated by an actuator, not shown here, be it a piezo actuator or a solenoid valve. Instead of the listed components, a mechanical / hydraulic translator can also be provided as the 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 leak oil drain 9 runs into 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 functions as an annular throttle element. In addition, an inlet 13 from a high-pressure source, not shown here, such as a high-pressure collecting chamber (common rail), opens into the valve chamber 5 in the housing 2 of the injector body 1.
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 Steuerraum- kanal 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 Steuer- raumkanals 16 in Belastungsrichtung 18 als Zulaufdrossel zum Steuerraum 20 fungiert.In the illustration according to FIG. 1, an inlet throttle element 14 is integrated in the inlet 13 from the high-pressure source, which element is designed in an inlet throttle cross section 15. The inlet 13 opens out on the side opposite the transmission element 6, with which the valve body 4 of the multi-way valve 3 can be actuated. A control chamber duct 16 also opens into the valve chamber 5 of the multi-way valve 3. The control chamber 20 and the valve chamber 5 of the multi-way valve 3 are connected via the control chamber duct 16. The control chamber 20 of the fuel injector is delimited by a wall 21 of the housing 2. In the wall 21 of the housing 2 of the injector body 1, a stop surface 22 is also received, which is opposite an upper end face 24 of a nozzle needle 23, the nozzle needle 23 in the housing 2 of the injector body 1 being movable up and down in the vertical direction according to the double arrow 25. Via the control chamber duct 16, the control chamber 20 can be depressurized in the relief direction 17 from a control volume enclosed therein. A throttle element 19 accommodated in the control chamber duct 16 functions as a discharge throttle in the pressure relief direction 17 with respect to the control chamber 20, whereas the throttle element 19 functions as an inlet throttle to the control chamber 20 when the control chamber duct 16 is acted upon in the opposite direction.
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 multi-way valve 3 can be moved into 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, fuel under high pressure, passing through the throttle element 14 in the inlet 13, flows into the valve chamber 5 via the inlet 13 from the high-pressure source. The fuel, which is under high pressure, flows from the latter via the control chamber duct 16 in the load direction 18 the throttle element 19 passing into the control chamber 20. As a result, pressure builds up 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 düsenna- delseitigen Sitz läßt sich erreichen. Von Vorteil bei der Ausführungsvariante gemäß FigurIf, on the other hand, the spherically configured valve body 4 of the multi-way valve 3 is in its second switching position 11.1, i.e. moved into 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 switch position, the control chamber 20 can be relieved of pressure very rapidly via the control chamber duct 16 in the pressure relief direction 17 via the valve chamber 5, the annular gap into the leakage oil drain 9. The faster the pressure can be reduced in the control chamber 20, the faster the nozzle needle 23 can be opened from its nozzle needle-side seat, not shown here. This is an advantage in the embodiment variant according to FIG
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.1 is the fact that an otherwise permanently acting inlet throttle 14 of an inlet 13 can be blocked by a high-pressure source from a control room volume, so that it is ensured that rapid pressure relief takes place in the control room 20.
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, offen- steht und dadurch ein Gegendruck in bezug auf die Strömungsrichtung des Steuerraumvolumens aus dem Steuerraum 20 erzeugt wird. Dadurch wird der Steuerraum 20 im GehäuseIf, on the other hand, the spherically configured valve body 4 is moved into its central position 12, the outflow of the control chamber volume from the control chamber 20 can be slowed down, since in the central position 12 the inlet 13, which opens into the valve chamber 5, is open and thereby a counterpressure is related is generated on the flow direction of the control chamber volume from the control chamber 20. As a result, the control chamber 20 is in the housing
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.2 of the injector body 1 relieved more slowly, i.e. the nozzle needle 23 moves more slowly towards the stop surface 22 formed on the wall 21, so that the injection openings correspondingly open more slowly at a second speed, which is lower than in the second switching position 11.2.
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 ver- sehen sind.The illustration according to FIG. 2 shows a further embodiment variant of the concept on which the invention is based, in which a switching valve assigned to the control chamber comprises a valve chamber, the inlet and outlet of which 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.Analogously to the illustration according to FIG. 1, the valve chamber of the multi-way valve 3, preferably designed as a 3/3-way control valve, can be connected via an inlet 13 to a throttle element 14 with a high-pressure source, not shown here. A control chamber duct 16 extends from the valve chamber 5 to a control chamber 20 in the housing 2 of the injector body 1, which is delimited on the one hand by a wall 21 of the housing 2 and on the other hand by an end face 24 of the nozzle needle 23 which can be moved in the direction of movement 25 in the housing 2 of the injector body 1. Also on the housing-side control room wall 21 of the control room 20, a stop surface 22 is formed analogously to the illustration according to FIG.
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 illustration according to FIG. 1, the control chamber channel 16, which connects the pressure-relieved control chamber 20 to the valve chamber 5, does not comprise a throttle element. The control chamber duct 16 can only be acted upon in a pressure relief direction 17 with respect to the control chamber 20 and in a load direction 18 with a fluid, for example fuel. In contrast to the illustration according to FIG. 1, the throttle element 19 accommodated in the control chamber duct 16 according to FIG. 1 is now integrated in the leak oil drain 9 branching off from the annular gap 8 between the transmission element 6 and the 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 Ventil- köφer 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 MittelstellungOn the valve chamber 5, which surrounds 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 an opposing lower seat 11 are formed, in which the valve body 4 of the multi-way valve 3 can be set to a second switching position 11.1 is. In the state shown in Figure 2, the valve body 4 of the multi-way valve 3 is in a central position
12 geschaltet.12 switched.
Die Schaltstellungen 10.1, 11.1 bzw. 12 des Ventilköφers 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 switch positions 10.1, 11.1 and 12 of the valve body 4 essentially correspond to the switch positions 10.1, 11.1 and 12, which have already been described in connection with the embodiment variant according to FIG.
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 illustration according to FIG. 1, a higher flow rate of the control chamber volume from the control chamber 20 into the valve chamber 5 of the multi-way valve 3 can be achieved by removing the throttle element 19 from the control chamber channel 16, which connects the control chamber 20 and the valve chamber 5. As a result, a further increased flow velocity in the pressure relief of the control chamber 20 can be achieved compared to the illustration according to FIG. 1.
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 ZulaufAlso according to the embodiment variant according to FIG. 2, the multi-way valve 3 placed in its second switching position 11.1 closes the otherwise permanently acting inflow of fuel via the inflow 13 from a high-pressure source (not shown here) into the valve chamber 5 and from there via the control chamber duct 16 into the control chamber 20. The inflow
13 wird in der zweiten Schaltstellung 11.1 des Ventilsköφers 4 des Mehrwegeventils 3 komplett abgeschaltet. Damit wird erreicht, daß sich kein Bypass während der Einspritzung einstellt; daneben ist in der Mittelstellung 12 des Ventilköφers 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 Ventilkör- per 4 seine Mittelstellung 12 gemäß der Darstellung in Figur 2 zwischen oberem Sitz 10 und unterem Sitz 11 ein.13 is completely switched off in the second switching position 11.1 of the valve body 4 of the multi-way valve 3. This ensures that no bypass occurs during the injection; In addition, 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, there is a possibility of variation, whereby quick and slow opening can be achieved. by 4 its middle position 12 as shown in FIG. 2 between the upper seat 10 and the lower seat 11.
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 Ausfüh- rungsvariante in Figur 2 der Ventilköφer 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.With a faster opening of the nozzle needle, i.e. with rapid pressure relief of the control chamber 20 and a related rapid opening of the nozzle needle 23 in the vertical direction according to the movement arrow 25 when the inlet 13 is completely shut off from the high-pressure source, pressure relief of the control chamber 20 can take place at a first higher speed if in the control chamber duct 16 according to no throttle element 19 is included in the illustration in FIG. If the embodiment variant in FIG. 2, the valve body 4 is moved into its central position 12, a somewhat slower pressure relief speed in the pressure relief direction 17 in the control chamber channel 16 can be set in the valve chamber 5. This essentially also applies to the embodiment variant as shown in FIG. 1, the outflow speed of the control chamber volume from the control chamber 20 being reduced in comparison to the solution according to FIG. 2 in that a throttle element 19 is accommodated in the control chamber channel 16. According to the solution according to FIG. 2, this is located in the leak oil drain 9 on the low pressure side behind the valve chamber 5 of the multi-way valve, which is preferably configured as a 3/3-way control 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 Ventilköφer 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 rapid opening of the nozzle needle 23 from its seat that can be achieved with the illustrated embodiment variants according to FIGS. 1 and 2 leads to the reduction of exhaust gas emissions of a self-igniting internal combustion engine operated in this way. By the central position 12, in which the Ventilköφer 4 of the multi-way valve 3 can be adjusted, a slow opening of the nozzle needle 3 in the control chamber 20 and thus a slower release of the injection opening can be achieved. This gives the possibility of shaping the course of the injection and adapting it to the progress of the combustion in the combustion chamber of the internal combustion engine.

Claims

Patentansprüche claims
1. Kraftstoffinjektor für Brennkraftmaschinen mit einem Injektorköφer (1), in dessen Gehäuse (2) eine Einspritzöffnungen freigebende oder diese verschließende Düsenna- del (23) aufgenommen ist, die über einen druckentlastbaren Steuerraum (20) betätigbar ist, der über einen Zulauf (13) von einer Hochdruckquelle mit unter hohem Druck stehenden Kraftstoff beaufschlagt wird und im Gehäuse (2) des Injektors (1) ein Ventilraum (5) eines Mehrwegeventils (3) ausgebildet ist, dadurch gekennzeichnet, daß der Steuerraum (20) mit dem Ventilraum (5) des Mehrwegeventils (3) über einen Steuer- raumkanal (16) verbunden ist, der in bezug auf den Steuerraum (20) sowohl in Entlastungsrichtung (17) als auch in Belastungsrichtung (18) beaufschlagbar ist.1. Fuel injector for internal combustion engines with an injector body (1), in the housing (2) of which an injection opening that opens or closes the injector needle (23) is accommodated, which can be actuated via a pressure-relieved control chamber (20), which can be actuated via an inlet (13 ) a high-pressure source is charged with fuel under high pressure and a valve chamber (5) of a multi-way valve (3) is formed in the housing (2) of the injector (1), characterized in that the control chamber (20) with the valve chamber (5 ) of the multi-way valve (3) is connected via a control chamber duct (16) which can be acted upon in relation to the control chamber (20) both in the relief direction (17) and in the loading direction (18).
2. Kraftstoffinjektor gemäß Anspmch 1, dadurch gekennzeichnet, daß das Mehrwegeventil (3) als ein 3/3 -Wege-Steuerventil ausgebildet ist, welches einen kugelförmigen Ventilkörper (4) umfaßt.2. Fuel injector according to Anspmch 1, characterized in that the multi-way valve (3) is designed as a 3/3-way control valve, which comprises a spherical valve body (4).
3. Kraftstoffinjektor gemäß Anspmch 1, dadurch gekennzeichnet, daß der Steuerraumkanal (16), ein Zulauf (13) von einer Hochdruckquelle und ein Ablauf (9) in den Ventilraum (5) des Mehrwegeventils (3) münden.3. Fuel injector according to Anspmch 1, characterized in that the control chamber channel (16), an inlet (13) from a high pressure source and an outlet (9) open into the valve chamber (5) of the multi-way valve (3).
4. Kraftstoffinjektor gemäß Anspruch 2, dadurch gekennzeichnet, daß der Ventilköφer (4) des Mehrwegeventils (3) mittels eines Übertragungselementes (6) betätigbar ist, welches den ablaufseitigen Bereich des Ventilraums (5) zugeordnet ist, der in einen Leckölablauf (9) übergeht.4. Fuel injector according to claim 2, characterized in that the Ventilköφer (4) of the multi-way valve (3) can be actuated by means of a transmission element (6) which is assigned to the outlet-side region of the valve chamber (5) which merges into a leak oil drain (9) ,
5. Kraftstoffinjektor gemäß Anspmch 4, dadurch gekennzeichnet, daß zwischen dem Übertragungselement (6) und dem Gehäuse (2) ein als Ringdrossel fungierender Ringspalt (8) ausgeführt ist.5. Fuel injector according to Anspmch 4, characterized in that between the transmission element (6) and the housing (2) an annular gap acting as an annular throttle (8) is executed.
6. Kraftstoffinjektor gemäß Anspmch 2, dadurch gekennzeichnet, daß der Ventilköφer (4) des Mehrwegeventils (3) im Ventilraum (5) in einer ersten Schaltstellung (10.1) in einen ersten Sitz (10), in einer zweiten Schaltstellung (11.1) in einen zweiten Sitz (11) und in eine Mittelstellung (12) stellbar ist.6. Fuel injector according to Anspmch 2, characterized in that the Ventilköφer (4) of the multi-way valve (3) in the valve chamber (5) in a first switching position (10.1) in a first seat (10), in a second switching position (11.1) in one second seat (11) and in a central position (12) is adjustable.
7. Kraftstoffinjektor gemäß Anspmch 3, dadurch gekennzeichnet, daß im Steuerraumkanal (16) ein Ablaufdrosselelement (19) aufgenommen ist. 7. Fuel injector according to Anspmch 3, characterized in that an outlet throttle element (19) is received in the control chamber channel (16).
8. Kraftstoffinjektor gemäß Anspmch 3, dadurch gekennzeichnet, daß im Leckölablauf (9) ein Ablaufdrosselelement (19) aufgenommen ist.8. Fuel injector according to Anspmch 3, characterized in that an outlet throttle element (19) is received in the leak oil drain (9).
9. Kraftstoffinjektor gemäß Anspmch 6, dadurch gekennzeichnet, daß in der zweiten Schaltstellung (11.1) des Ventilköφers (4) im Ventilraum (5) der Zulauf (13) von der9. Fuel injector according to Anspmch 6, characterized in that in the second switching position (11.1) of the Ventilköφers (4) in the valve chamber (5) of the inlet (13) from the
Hochdruckquelle verschlossen ist und eine Druckentlastung des Steuerraumes (20) in Entlastungsrichtung (17) durch den Steuerraumkanal (16) in einer ersten Geschwindigkeit erfolgt.High pressure source is closed and the control chamber (20) is depressurized in the relief direction (17) by the control chamber duct (16) at a first speed.
10. Kraftstoffinjektor gemäß Anspmch 6, dadurch gekennzeichnet, daß in der Mittelstellung (12) des Ventilköφers (4) im Ventilraum (5) eine Druckentlastung des Steuerraums (20) in Entlastungsrichtung (17) durch den Steuerraumkanal (16) in einer zweiten Geschwindigkeit erfolgt.10. Fuel injector according to Anspmch 6, characterized in that in the central position (12) of the Ventilköφers (4) in the valve chamber (5) a pressure relief of the control chamber (20) in the relief direction (17) through the control chamber channel (16) at a second speed ,
11. Kraftstoffinjektor gemäß Anspmch 6, dadurch gekennzeichnet, daß in der ersten Schaltstellung (10.1) des Ventilköφers (4) im Ventilraum (5) die Druckbeaufschlagung des Steuerraums (20) in Belastungsrichtung (18) über den Steuerraumkanal (16) erfolgt. 11. Fuel injector according to Anspmch 6, characterized in that in the first switching position (10.1) of the Ventilköφers (4) in the valve chamber (5) the pressurization of the control chamber (20) in the loading direction (18) via the control chamber channel (16).
PCT/DE2002/002290 2001-06-29 2002-06-21 Fuel injector switch valve for the compression/decompression of a control chamber WO2003004864A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE50211740T DE50211740D1 (en) 2001-06-29 2002-06-21 FUEL INJECTOR PILOT VALVE FOR PRESSURE RELIEF / LOADING OF A CONTROL ROOM
EP02754253A EP1404966B1 (en) 2001-06-29 2002-06-21 Fuel injector switch valve for the compression/decompression of a control chamber

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2001131617 DE10131617A1 (en) 2001-06-29 2001-06-29 Fuel injector switching valve for pressure relief / loading of a control room
DE10131617.8 2001-06-29

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DE (2) DE10131617A1 (en)
WO (1) WO2003004864A1 (en)

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EP1865190A1 (en) 2006-06-08 2007-12-12 Denso Corporation Fuel injection valve
EP1870594A1 (en) * 2006-06-21 2007-12-26 Denso Corporation Fuel injection valve
EP2136070A3 (en) * 2008-06-18 2010-02-17 Honda Motor Co., Ltd. Fuel injection device
WO2012107228A1 (en) * 2011-02-08 2012-08-16 Liebherr Machines Bulle Sa Injection device for a fluid

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DE10349639A1 (en) * 2003-10-24 2005-05-19 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102004024215A1 (en) * 2004-05-15 2005-12-08 L'orange Gmbh control valve
DE102010040989A1 (en) * 2010-09-17 2012-03-22 Continental Automotive Gmbh Control valve unit for a fuel injector
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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EP1870594A1 (en) * 2006-06-21 2007-12-26 Denso Corporation Fuel injection valve
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US8033269B2 (en) 2008-06-18 2011-10-11 Honda Motor Co., Ltd. Fuel injection device
WO2012107228A1 (en) * 2011-02-08 2012-08-16 Liebherr Machines Bulle Sa Injection device for a fluid

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DE10131617A1 (en) 2003-01-23
DE50211740D1 (en) 2008-04-03
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EP1404966B1 (en) 2008-02-20

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