EP2100026B1 - Fuel injector having a solenoid valve with a spherical seat - Google Patents

Fuel injector having a solenoid valve with a spherical seat Download PDF

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Publication number
EP2100026B1
EP2100026B1 EP07821236A EP07821236A EP2100026B1 EP 2100026 B1 EP2100026 B1 EP 2100026B1 EP 07821236 A EP07821236 A EP 07821236A EP 07821236 A EP07821236 A EP 07821236A EP 2100026 B1 EP2100026 B1 EP 2100026B1
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EP
European Patent Office
Prior art keywords
pressure
valve
valve member
fuel injector
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07821236A
Other languages
German (de)
French (fr)
Other versions
EP2100026A1 (en
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2100026A1 publication Critical patent/EP2100026A1/en
Application granted granted Critical
Publication of EP2100026B1 publication Critical patent/EP2100026B1/en
Not-in-force legal-status Critical Current
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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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • An injector for injecting fuel into a combustion chamber of an internal combustion engine in which an injection valve member is actuated via a solenoid-operated control valve, is off EP-A 1 612 403 known.
  • a flow restrictor from a control room in the fuel return can be closed or released.
  • the control chamber is bounded on one side by a control piston with which an injection valve member is actuated, which releases at least one injection opening into the combustion chamber of the internal combustion engine or closes it.
  • the outlet throttle is received in a body, which is on the side facing away from the control chamber with a tapered valve seat 29en.
  • a closing element is adjustable, which is connected to the armature of the solenoid valve.
  • an edge is formed on the closing element, which is provided against the conically shaped seat.
  • the closing element moves on an axial rod, which is integrally connected to the body in which the drainage throttle is formed.
  • a fuel injector which has a control valve with a movable piston, wherein the piston is mounted pressure balanced.
  • a control valve for a fuel injector with a force balanced control valve member is known, which cooperates with a flat or hemispherical valve seat.
  • z. B. on high-pressure accumulator injection systems used fuel injectors z. B. stroke-controlled injectors are used, which are operated by means of a solenoid valve to control the pressure in a control room.
  • the preferred needle-shaped injection valve member is z. B. controlled by a servo control room.
  • the solenoid valve is usually not pressure balanced and therefore requires high spring forces, high magnetic switching forces and due to the size of spring and magnet large space.
  • a disadvantage of such solenoid valves is the fact that there are severe restrictions on the sequence of multiple injections exist, so that very short successive injection intervals can not be realized.
  • Pressure compensated solenoid valves typically require much smaller spring forces, hence smaller magnetic forces to effect opening, as well as smaller valve strokes, thus allowing faster shift times.
  • a multiple injection capability can be improved.
  • these pressure-balanced designed valves require a high-pressure-tight guide and a linearly extending sealing edge, which correspond to the guide diameter of the valve member, which allows the pressure balance of the solenoid valve only.
  • a pressure-balanced solenoid valve wherein the preferably needle-shaped valve member has a self-adjusting mechanical wear due to material removal or deformation robust ball seat formed seat.
  • a valve seat of the present invention proposed solenoid valve with ball seat is formed on the valve sealing point, ie the seat of the valve member, a ball seat.
  • the ball seat can be z. B. represent by a hemispherical configuration of the seat of the valve member facing the end of the valve member.
  • the Z. B. hemispherical end of the valve member may be funnel-shaped, such. B. as a conical seat, trained seat in a valve piece.
  • the needle-shaped valve member is guided with an inner in an actuator housing loosely mounted pressure pin, whereby a pressure equalization can be achieved.
  • the solenoid valve is provided with a ball seat, so z. B. a balance of Parallelticiansohnem between the preferably needle-shaped valve member and a seat body, d. H. z. B. the valve piece, follow, so that thereby favorable multi-part valve design variants can be realized.
  • a further improvement is achieved by the connection of the ball seat proposed according to the invention with a small compression stage which is effective in the closing direction.
  • a hydraulic force acting on the valve member closing force is generated, whereby a bouncing is reduced in the valve closing, which in turn has beneficial effects on the self-adjusting wear, as occur during bouncing mechanical peak loads.
  • the damping behavior when closing the solenoid valve is improved by the effective pressure in the closing direction, since in the closed state of the seat of the preferably needle-shaped valve member, a hydraulic closing force builds up, which prevents reopening of the preferably needle-shaped valve member.
  • this allows optimized valve tuning and, on the other hand, improves the multiple injection capability of the fuel injector which is actuated by the solenoid valve having a ball seat proposed according to the invention.
  • a damping chamber can be provided in the high-pressure region of the fuel injector, whereby on the one hand the speed at which the preferably needle-shaped valve member moves and, on the other hand, the bouncing properties and bouncing stresses caused by the latter can advantageously be optimized with regard to the mechanical components. If the preferably needle-shaped injection valve member and an armature attracted by the solenoid valve armature formed integrally, a small moving mass can be achieved, and with optimized damping behavior can thus short intervals of individual injections realize, which favorably influences the Mehrfacheinspritzungswin.
  • the inventively proposed pressure balanced solenoid valve with ball seat can be used to control injection systems, in particular advantageously as a control valve for a servo-controlled Kraftstoffinjektor which is actuated by means of a solenoid valve.
  • the ball seat can be formed directly in the valve piece, in which a control chamber, in particular a servo control chamber, is located, and which closes a pressure chamber within the injector body of the fuel injector.
  • the sole FIGURE shows a section through the inventively proposed fuel injector, which is actuated by means of a solenoid valve which comprises a ball seat.
  • a fuel injector 10 is acted upon via a pressure accumulator 12, in which a system pressure p sys , with high-pressure fuel.
  • the system pressure p sys in pressure accumulator 12 is replaced by a not shown in the drawing high-pressure pumping unit, such.
  • the high-pressure line 14 opens within an injector 16 and acts on a reference numeral 34 designated pressure chamber with system pressure p sys stationary system pressure.
  • the fuel injector 10 further comprises a nozzle body 18, which is only indicated here, and an actuator housing 20, in which an actuator designed as a solenoid valve 22 is accommodated.
  • the actuator housing 20 is closed by a housing cover 24.
  • the housing cover 24 is provided with an external thread and can be screwed into a correspondingly formed internal thread of the actuator housing 20.
  • a magnetic core 26, an enclosed by this magnetic coil 28, a magnetic core 26 supporting supporting sleeve 30 are received and a part of a valve piece 32.
  • the partially housed in the actuator housing 20 valve piece 32 limits the aforementioned pressure chamber 34, in which the Pressure accumulator 12 outgoing high pressure line 14 opens.
  • a control chamber 36 is formed, which is filled via an inlet throttle 38 from under system pressure p sys pressure chamber 34 with fuel.
  • the control chamber 36 - formed in the drawing as a servo control room - is depressurized via an outlet throttle 40.
  • the outlet throttle 40 is also formed in the valve piece 32 and opens into a valve space identified by reference numeral 84.
  • the system pressure p sys applied via the inlet throttle 38 in the control chamber 36 acts on an end face 44 of a preferably needle-shaped injection valve member 42.
  • the injection valve member 42 comprises a support disk 46 against which a closing spring 48 is supported.
  • the support disk 46 opposite end of the closing spring 48 is supported on the valve piece 32 from.
  • annular space 52 extends through the injector housing 16. Via the annular space 52, fuel under system pressure p sys flows to a nozzle space designated by reference numeral 50, which is formed inside the nozzle body 18. From the annulus 52 passes under system pressure p sys standing fuel via at least one throttle point 56, the z. B. may be formed as at least one bevel on the circumference of the preferably needle-shaped injection valve member 42, in the nozzle chamber 50th
  • the injection valve member 42 comprises a pressure stage 54 in the region in which it is enclosed in the nozzle body 18 by the nozzle chamber 50.
  • injection ports 60 are closed at the combustion chamber end of the fuel injector 10 by the asked in his seat 58, preferably needle-shaped injection valve member 42.
  • At least one, preferably formed as a bevel throttle body 56 is at the periphery of the preferably needle-shaped injection valve member 42. About this at least one throttle point 56 of the system pressure p sys standing annular space 52 and the nozzle chamber 50 are hydraulically connected to each other.
  • the solenoid valve 22 accommodated in the actuator housing 20 comprises a valve spring 70, which encloses a pressure pin 66.
  • the valve spring 70 is supported on the underside of the housing cover 24.
  • the pressure pin 66 is loosely received in the actuator housing 20.
  • the valve spring 70 acts on an upper end side of a valve member designed as a valve member 62.
  • an anchor plate 64 is formed, which is disposed opposite to the solenoid coil 28 of the solenoid valve 22.
  • the pressure pin 66 is formed in a diameter that represents a guide diameter 68 for the valve member 62.
  • a lower end face of the pressure pin 66 bounded by the preferably needle-shaped valve member 62 a pressure compensation chamber 78.
  • the pressure relief chamber 66 and the valve member 62 limited pressure compensation chamber 78 communicates via a flow connection 74 with a valve chamber 84 in connection.
  • the valve space 84 is bounded by a conical surface 82 in the valve piece 32 on the one hand and on the other hand by a spherical surface 86 at the lower end of the valve member 62.
  • the spherical surface 86 which represents the ball seat, on the valve member 62 is executed.
  • spherical surface 86 at the valve piece 32 facing the end of the preferably needle-shaped valve member 62 can be achieved in an advantageous manner, a compensation of parallelism errors between the valve member 62 and the seat body performing valve member 32.
  • inventively proposed arrangement favorable, multi-part valve bodies can be realized by the inventively proposed arrangement favorable, multi-part valve bodies.
  • the conical surface 82 can also be formed on the valve member 62 and the spherical surface 86 on the valve piece 32 to be executed. Further, it is possible to realize both the valve member 62 and the valve piece 32 each spherical geometries.
  • the pressure balance of the solenoid valve 22 acts. It can be inventively proposed valve design realized by forming a spherical surface 86 ball seat in cooperation with a Conical surface 82 realize because the pressure pin 66 can be mounted independently of the valve seat 80 from the opposite side of the seating area.
  • a flow connection is identified, which connects the pressure equalization or damping chamber 78 with the valve space 84.
  • An embodiment of the fuel injector shown in the drawing is given by the fact that at the pressure pin 66, on which the preferably needle-shaped valve member 62 is guided, an effective compression in the closing direction is generated.
  • the effective in the closing direction of the preferably needle-shaped valve member 62 pressure stage can be achieved by increasing the guide diameter 68 of the loosely received in the actuator housing 20 pressure pin 66 with respect to the diameter of the given by the spherical surface 86 ball seat.
  • a hydraulic valve closing force is generated, whereby a bouncing of the Solenoid valve when closing the valve member 62 is reduced.
  • the damping behavior when closing the valve member 62 can be improved by the pressure acting in the closing direction, given by the enlargement of the guide diameter 68 with respect to the diameter of the given by the spherical surface 86 ball seat, since in the closed state of the ball seat builds up a hydraulic closing force which prevents reopening of the preferably needle-shaped valve member 62.
  • This in turn allows for optimized valve tuning and an improvement in the multiple injection capability of the fuel injector 10 proposed according to the invention.
  • the speed at which the valve member 62 opens can be optimized and the bouncing characteristics improved. If the preferably needle-shaped injection valve member 62 and the armature plate 64 designed as a component, so sets a small mass to be moved, which leads through a damper throttle 76, which is arranged in the flow connection 74 to an optimized damping behavior, resulting in very short distances be made possible with individual fuel injections in quick succession via the injection openings 30.
  • the ball seat realized by the spherical surface 86 is formed directly on the valve piece 32, which limits the control space 36 serving as a servo control room and separates from the pressure space 34 in the injector housing 16 under system pressure p sys .
  • the valve piece 32 is made in a sealing manner against the injector body 16 via the support sleeve 30, the magnetic core 26 resting thereon and the housing cover 24, with which the actuator housing 20 is closed.
  • the opening behavior of the preferably needle-shaped injection valve member 42 can be optimized by means of the throttle point 56, which is formed on the circumference thereof and has at least one preferably formed as a bevel.
  • the at least one throttle point 56 formed on the circumference of the preferably needle-shaped injection valve member 42 provides a hydraulic connection with the annular space 52 under system pressure p sys in the injector body 16 with the nozzle chamber 50 formed in the nozzle body 18 of the fuel injector 10.
  • the pressure compensated solenoid valve 22 is employed in fuel injection injection systems as a servo-controlled fuel injector control valve applicable to high-pressure common-rail injection systems.

Abstract

The fuel injector (10) has an injecting valve element (42) operated via pressure discharge of a control chamber (36), which is subjected with a system pressure. The pressure discharge of the control chamber is made by a pressure-compensating magnetic valve (22), whose valve element (62) opens or locks a valve seat (80). The valve element or a piece of valve exhibits a spherical surface (86). The valve element is guided at a pressure pin, and a pressure-compensating area (78) is limited with the valve element.

Description

Stand der TechnikState of the art

Ein Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine, bei welchem ein Einspritzventilglied über ein magnetbetriebenes Steuerventil angesteuert wird, ist aus EP-A 1 612 403 bekannt. Mit Hilfe des Steuerventils ist eine Ablaufdrossel aus einem Steuerraum in den Kraftstoffrücklauf verschließbar oder freigebbar. Der Steuerraum wird an einer Seite durch einen Steuerkolben begrenzt, mit welchem ein Einspritzventilglied angesteuert wird, welches mindestens eine Einspritzöffnung in den Brennraum der Verbrennungskraftmaschine freigibt oder diese verschließt. Die Ablaufdrossel ist in einem Körper aufgenommen, welcher auf der dem Steuerraum abgewandten Seite mit einem sich verjüngenden Ventilsitz verschen ist. In diesen Ventilsitz ist ein Schließelement stellbar, welches mit dem Anker des Magnetventils verbunden ist. Hierzu ist am Schließelement eine Kante ausgebildet, welche gegen den konisch ausgeformten Sitz gestellt wird. Das Schließelement bewegt sich auf einer axialen Stange, welche mit dem Körper, in dem die Ablaufdrossel ausgebildet ist, einstückig verbunden ist. Damit das Ventil flüssigkeitsdicht schließt, ist es notwendig, hochpräzise Oberflächen herzustellen und eine hochgenaue Passung des Schließelementes auf der axialen Stange vorzusehen, um zu vermeiden, dass das Schließelement taumelt und hierdurch verkanten kann, wodurch der Sitz nicht vollständig geschossen wird.An injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member is actuated via a solenoid-operated control valve, is off EP-A 1 612 403 known. With the help of the control valve, a flow restrictor from a control room in the fuel return can be closed or released. The control chamber is bounded on one side by a control piston with which an injection valve member is actuated, which releases at least one injection opening into the combustion chamber of the internal combustion engine or closes it. The outlet throttle is received in a body, which is on the side facing away from the control chamber with a tapered valve seat verschen. In this valve seat, a closing element is adjustable, which is connected to the armature of the solenoid valve. For this purpose, an edge is formed on the closing element, which is provided against the conically shaped seat. The closing element moves on an axial rod, which is integrally connected to the body in which the drainage throttle is formed. In order for the valve to close in a liquid-tight manner, it is necessary to produce high-precision surfaces and to provide a highly accurate fit of the closure member on the axial rod to prevent the closure member from tumbling and canting thereby not fully shooting the seat.

Aus der DE 199 52 511 A1 ist ein Kraftstoffinjektor bekannt, der ein Steuerventil mit einem beweglichen Kolben aufweist, wobei der Kolben druckausgeglichen gelagert ist.From the DE 199 52 511 A1 a fuel injector is known, which has a control valve with a movable piston, wherein the piston is mounted pressure balanced.

Aus der nachveröffentlichten WO 2008/055724 A1 ist darüber hinaus ein Steuerventil für einen Kraftstoffinjektor mit einem kraftausgeglichenen Steuerventilglied bekannt, das mit einem flachen oder halbkugelförmigen Ventilsitz zusammenwirkt.From the post-published WO 2008/055724 A1 In addition, a control valve for a fuel injector with a force balanced control valve member is known, which cooperates with a flat or hemispherical valve seat.

Bei z. B. an Hochdruckspeichereinspritzsystemen (Common-Rail) eingesetzten Kraftstoffinjektoren können z. B. hubgesteuerte Injektoren eingesetzt werden, die mittels eines Magnetventils zur Steuerung des Druckes in einem Steuerraum betrieben werden. Das bevorzugt nadelförmig ausgebildete Einspritzventilglied wird z. B. über einen Servosteuerraum gesteuert. Das Magnetventil ist in der Regel nicht druckausgeglichen und benötigt daher hohe Federkräfte, hohe Magnetschaltkräfte und einen aufgrund der Dimensionierung von Feder und Magneten großen Bauraum. Von Nachteil bei derartigen Magnetventilen ist der Umstand, dass starke Einschränkungen hinsichtlich der Abfolge von Mehrfacheinspritzun-gen bestehen, so dass sehr kurz aufeinander folgende Einspritzabstände nicht realisiert werden können.At z. B. on high-pressure accumulator injection systems (common rail) used fuel injectors z. B. stroke-controlled injectors are used, which are operated by means of a solenoid valve to control the pressure in a control room. The preferred needle-shaped injection valve member is z. B. controlled by a servo control room. The solenoid valve is usually not pressure balanced and therefore requires high spring forces, high magnetic switching forces and due to the size of spring and magnet large space. A disadvantage of such solenoid valves is the fact that there are severe restrictions on the sequence of multiple injections exist, so that very short successive injection intervals can not be realized.

Druckausgeglichene Magnetventile erfordern in der Regel wesentlich kleinere Federkräfte, demzufolge kleinere Magnetkräfte, um ein Öffnen zu bewirken, sowie kleinere Ventilhübe und erlauben somit schnellere Schaltzeiten. Mittels dieser Bauart von Magnetventilen lässt sich eine Mehrfacheinspritzfähigkeit verbessern. Allerdings benötigen diese druckausgeglichen ausgestalteten Ventile eine hochdruckdichte Führung sowie eine linienförmig verlaufende Dichtkante, die dem Führungsdurchmesser des Ventilgliedes entsprechen, was die Druckausgeglichenheit des Magnetventiles erst ermöglicht.Pressure compensated solenoid valves typically require much smaller spring forces, hence smaller magnetic forces to effect opening, as well as smaller valve strokes, thus allowing faster shift times. By means of this type of solenoid valves, a multiple injection capability can be improved. However, these pressure-balanced designed valves require a high-pressure-tight guide and a linearly extending sealing edge, which correspond to the guide diameter of the valve member, which allows the pressure balance of the solenoid valve only.

Kritisch ist bei den druckausgeglichenen Magnetventilen jedoch der Umstand, dass sich im Laufe von deren Betriebszeit ein Verschleiß an einer Dichtkante einstellt, da die mechanische Belastung einer linienförmig verlaufenden Sitzkante beim Schließen des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes sehr groß ist. Des Weiteren wird der Verschleiß dadurch unterstützt, dass Verunreinigungen in verstärktem Maße direkt an die Sitzkante gelangen. Dies führt über die Betriebszeit des Magnetventils gesehen zu Verschleiß, der die Funktion eines derartig ausgebildeten Magnetventiles nicht unerheblich beeinträchtigt.Critical is the pressure balanced solenoid valves, however, the circumstance that sets in the course of their operating time wear on a sealing edge, since the mechanical load of a linear extending seat edge when closing the preferably needle-shaped injection valve member is very large. Furthermore, the wear is supported by the fact that impurities come to a greater extent directly to the seat edge. This leads over the operating time of the solenoid valve to wear, which affects the function of such a trained solenoid valve not insignificant.

Offenbarung der ErfindungDisclosure of the invention

Bei der erfindungsgemäßen Lösung wird ein druckausgeglichenes Magnetventil vorgeschlagen, wobei das bevorzugt nadelförmig ausgebildete Ventilglied einen gegenüber sich einstellendem mechanischen Verschleiß durch Materialabtrag oder Deformation robusten Kugelsitz ausgebildeten Sitz aufweist. Als Ventilsitz des erfindungsgemäß vorgeschlagenen Magnetventils mit Kugelsitz ist an der Ventildichtstelle, d. h. dem Sitz des Ventilgliedes, ein Kugelsitz ausgebildet. Der Kugelsitz lässt sich z. B. durch eine halbkugelförmige Konfiguration des dem Sitz des Ventilgliedes zuweisenden Ende des Ventilgliedes darstellen. Das z. B. halbkugelförmig ausgebildete Ende des Ventilgliedes kann mit einem trichterförmig, so z. B. als Kegelsitz, ausgebildeten Sitz in einem Ventilstück zusammenwirken. Darüber hinaus besteht auch die Möglichkeit, anstelle der Kegelfläche im Ventilstück, diese Kegelfläche am Ende des Ventilgliedes auszubilden und den am Ventilstück ausgebildeten, mit dem Ventilglied zusammenwirkenden Sitz halbkugelförmig auszubilden. Beide Gestaltungen eines Kugelsitzes sind möglich.In the solution according to the invention, a pressure-balanced solenoid valve is proposed, wherein the preferably needle-shaped valve member has a self-adjusting mechanical wear due to material removal or deformation robust ball seat formed seat. As a valve seat of the present invention proposed solenoid valve with ball seat is formed on the valve sealing point, ie the seat of the valve member, a ball seat. The ball seat can be z. B. represent by a hemispherical configuration of the seat of the valve member facing the end of the valve member. The Z. B. hemispherical end of the valve member may be funnel-shaped, such. B. as a conical seat, trained seat in a valve piece. In addition, it is also possible, instead of the conical surface in the valve piece to form this conical surface at the end of the valve member and form the valve piece formed, cooperating with the valve member hemispherical. Both designs of a ball seat are possible.

Bevorzugt ist das nadelförmig ausgebildete Ventilglied mit einem innenliegenden in einem Aktorgehäuse lose gelagerten Druckstift geführt, wodurch sich ein Druckausgleich erzielen lässt.Preferably, the needle-shaped valve member is guided with an inner in an actuator housing loosely mounted pressure pin, whereby a pressure equalization can be achieved.

Wird das Magnetventil mit einem Kugelsitz versehen, so kann z. B. ein Ausgleich von Parallelitätsfehlem zwischen dem bevorzugt nadelförmig ausgebildeten Ventilglied und einem Sitzkörper, d. h. z. B. dem Ventilstück, folgen, so dass dadurch günstige mehrteilige Ventilaufbauvarianten realisiert werden können.If the solenoid valve is provided with a ball seat, so z. B. a balance of Parallelitätsfehlem between the preferably needle-shaped valve member and a seat body, d. H. z. B. the valve piece, follow, so that thereby favorable multi-part valve design variants can be realized.

Eine weitere Verbesserung wird durch die Verbindung des erfindungsgemäß vorgeschlagenen Kugelsitzes mit einer kleinen, in Schließrichtung wirksamen Druckstufe erreicht. Durch die in Schließrichtung wirksame Druckstufe wird eine hydraulische auf das Ventilglied wirkende Schließkraft erzeugt, wodurch ein Prellen beim Ventilschließen verringert wird, was wiederum günstige Auswirkungen auf den sich einstellenden Verschleiß hat, da beim Prellen mechanische Spitzenbelastungen auftreten. Das Dämpfungsverhalten beim Schließen des Magnetventils wird durch die in Schließrichtung wirksame Druckstufe verbessert, da sich im geschlossenen Zustand des Sitzes des bevorzugt nadelförmig ausgebildeten Ventilgliedes eine hydraulische Schließkraft aufbaut, die ein Wiederöffnen des bevorzugt nadelförmig ausgebildeten Ventilglieds verhindert. Dies erlaubt einerseits eine optimierte Ventilabstimmung und verbessert andererseits die Mehrfacheinspritzfähigkeit des Kraftstoffinjektors, der mit dem erfindungsgemäß vorgeschlagenen, einen Kugelsitz aufweisenden Magnetventil betätigt wird.A further improvement is achieved by the connection of the ball seat proposed according to the invention with a small compression stage which is effective in the closing direction. By acting in the closing direction pressure stage, a hydraulic force acting on the valve member closing force is generated, whereby a bouncing is reduced in the valve closing, which in turn has beneficial effects on the self-adjusting wear, as occur during bouncing mechanical peak loads. The damping behavior when closing the solenoid valve is improved by the effective pressure in the closing direction, since in the closed state of the seat of the preferably needle-shaped valve member, a hydraulic closing force builds up, which prevents reopening of the preferably needle-shaped valve member. On the one hand, this allows optimized valve tuning and, on the other hand, improves the multiple injection capability of the fuel injector which is actuated by the solenoid valve having a ball seat proposed according to the invention.

Darüber hinaus kann im Hochdruckbereich des Kraftstoffinjektors ein Dämpfungsraum vorgesehen sein, wodurch sich einerseits die Geschwindigkeit, mit der sich das bevorzugt nadelförmig ausgebildete Ventilglied bewegt, und andererseits die durch dieses verursachten Prelleigenschaften und Prellbeanspruchungen hinsichtlich der mechanischen Bauteile vorteilhaft optimieren lassen. Werden das bevorzugt nadelförmig ausgebildete Einspritzventilglied und ein durch die Magnetspule des Magnetventiles angezogener Anker einteilig ausgebildet, lässt sich eine kleine bewegte Masse erreichen, und bei optimiertem Dämpfungsverhalten lassen sich demzufolge kurze Abstände einzelner Einspritzvorgänge realisieren, was die Mehrfacheinspritzungsfähigkeit günstig beeinflusst.In addition, a damping chamber can be provided in the high-pressure region of the fuel injector, whereby on the one hand the speed at which the preferably needle-shaped valve member moves and, on the other hand, the bouncing properties and bouncing stresses caused by the latter can advantageously be optimized with regard to the mechanical components. If the preferably needle-shaped injection valve member and an armature attracted by the solenoid valve armature formed integrally, a small moving mass can be achieved, and with optimized damping behavior can thus short intervals of individual injections realize, which favorably influences the Mehrfacheinspritzungsfähigkeit.

Das erfindungsgemäß vorgeschlagene druckausgeglichene Magnetventil mit Kugelsitz lässt sich zur Steuerung von Einspritzsystemen einsetzen, insbesondere in vorteilhafter Weise als Steuerventil für einen servogesteuerten Kraftstoffinjektor, der mittels eines Magnetventils betätigt wird.The inventively proposed pressure balanced solenoid valve with ball seat can be used to control injection systems, in particular advantageously as a control valve for a servo-controlled Kraftstoffinjektor which is actuated by means of a solenoid valve.

In besonders vorteilhafter Weise kann der Kugelsitz direkt im Ventilstück ausgebildet werden, in welchem sich ein Steuerraum, insbesondere ein Servosteuerraum, befindet, und welches einen Druckraum innerhalb des Injektorkörpers des Kraftstoffinjektors verschließt. Dies erlaubt einen einfachen und kostengünstigen Aufbau eines insbesondere für Hochdruckspeichereinspritzsysteme (Common-Rail) geeigneten Kraftstoffinjektors.In a particularly advantageous manner, the ball seat can be formed directly in the valve piece, in which a control chamber, in particular a servo control chamber, is located, and which closes a pressure chamber within the injector body of the fuel injector. This allows a simple and inexpensive construction of a fuel injector suitable in particular for high-pressure accumulator injection systems (common rail).

Kurze Beschreibung der ZeichnungShort description of the drawing

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben. Die einzige Figur zeigt einen Schnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor, welcher mittels eines Magnetventils betätigt wird, der einen Kugelsitz umfasst.With reference to the drawing, the invention will be described below in more detail. The sole FIGURE shows a section through the inventively proposed fuel injector, which is actuated by means of a solenoid valve which comprises a ball seat.

Ausführungsformenembodiments

Aus der Zeichnung geht hervor, dass ein Kraftstoffinjektor 10 über einen Druckspeicher 12, in welchem ein Systemdruck psys herrscht, mit unter hohem Druck stehenden Kraftstoff beaufschlagt ist. Der Systemdruck psys im Druckspeicher 12 wird durch ein in der Zeichnung nicht dargestelltes Hochdruckförderaggregat, wie z. B. eine Hochdruckpumpe, erzeugt und gelangt vom Druckspeicher 12 über eine Hochdruckleitung 14 zum Kraftstoffinjektor 10. Die Hochdruckleitung 14 mündet innerhalb eines Injektorgehäuses 16 und beaufschlagt einen mit Bezugszeichen 34 bezeichneten Druckraum mit unter Systemdruck psys stehendem Systemdruck.From the drawing shows that a fuel injector 10 is acted upon via a pressure accumulator 12, in which a system pressure p sys , with high-pressure fuel. The system pressure p sys in pressure accumulator 12 is replaced by a not shown in the drawing high-pressure pumping unit, such. As a high-pressure pump, generated and passes from the pressure accumulator 12 via a high-pressure line 14 to the fuel injector 10. The high-pressure line 14 opens within an injector 16 and acts on a reference numeral 34 designated pressure chamber with system pressure p sys stationary system pressure.

Der Kraftstoffinjektor 10 gemäß der Zeichnung umfasst neben dem Injektorgehäuse 16 des Weiteren einen hier nur angedeuteten Düsenkörper 18 sowie ein Aktorgehäuse 20, in welchem ein als Magnetventil 22 ausgebildeter Aktor untergebracht ist. Das Aktorgehäuse 20 ist über einen Gehäusedeckel 24 verschlossen. In der Zeichnung ist der Gehäusedeckel 24 mit einem Außengewinde versehen und lässt sich in ein korrespondierend ausgebildetes Innengewinde des Aktorgehäuses 20 einschrauben. Innerhalb des Aktorgehäuses 20 sind ein Magnetkern 26, eine von diesem umschlossene Magnetspule 28, eine den Magnetkern 26 abstützende Stützhülse 30 aufgenommen sowie ein Teil eines Ventilstückes 32. Das teilweise im Aktorgehäuse 20 aufgenommene Ventilstück 32 begrenzt den eingangs erwähnten Druckraum 34, in welchen die vom Druckspeicher 12 ausgehende Hochdruckleitung 14 mündet.In addition to the injector housing 16, the fuel injector 10 further comprises a nozzle body 18, which is only indicated here, and an actuator housing 20, in which an actuator designed as a solenoid valve 22 is accommodated. The actuator housing 20 is closed by a housing cover 24. In the drawing, the housing cover 24 is provided with an external thread and can be screwed into a correspondingly formed internal thread of the actuator housing 20. Within the actuator housing 20, a magnetic core 26, an enclosed by this magnetic coil 28, a magnetic core 26 supporting supporting sleeve 30 are received and a part of a valve piece 32. The partially housed in the actuator housing 20 valve piece 32 limits the aforementioned pressure chamber 34, in which the Pressure accumulator 12 outgoing high pressure line 14 opens.

Im Ventilstück 32 ist ein Steuerraum 36 ausgebildet, der über eine Zulaufdrossel 38 vom unter Systemdruck psys stehenden Druckraum 34 mit Kraftstoff befüllt wird. Der Steuerraum 36 - in der Zeichnung als Servosteuerraum ausgebildet - ist über eine Ablaufdrossel 40 druckentlastbar. Die Ablaufdrossel 40 ist ebenfalls im Ventilstück 32 ausgebildet und mündet in einen mit Bezugszeichen 84 identifizierten Ventilraum.In the valve piece 32, a control chamber 36 is formed, which is filled via an inlet throttle 38 from under system pressure p sys pressure chamber 34 with fuel. The control chamber 36 - formed in the drawing as a servo control room - is depressurized via an outlet throttle 40. The outlet throttle 40 is also formed in the valve piece 32 and opens into a valve space identified by reference numeral 84.

Der über die Zulaufdrossel 38 im Steuerraum 36 anstehende Systemdruck psys beaufschlagt eine Stirnseite 44 eines bevorzugt nadelförmig ausgebildeten Einspritzventilglieds 42. Das Einspritzventilglied 42 umfasst eine Stützscheibe 46, an der sich eine Schließfeder 48 abstützt. Das der Stützscheibe 46 gegenüberliegende Ende der Schließfeder 48 stützt sich am Ventilstück 32 ab.The system pressure p sys applied via the inlet throttle 38 in the control chamber 36 acts on an end face 44 of a preferably needle-shaped injection valve member 42. The injection valve member 42 comprises a support disk 46 against which a closing spring 48 is supported. The support disk 46 opposite end of the closing spring 48 is supported on the valve piece 32 from.

Vom mit Systemdruck psys beaufschlagten Druckraum 34 erstreckt sich ein Ringraum 52 durch das Injektorgehäuse 16. Über den Ringraum 52 strömt unter Systemdruck psys stehender Kraftstoff einem mit Bezugszeichen 50 bezeichneten Düsenraum zu, der innerhalb des Düsenkörpers 18 ausgebildet ist. Vom Ringraum 52 gelangt der unter Systemdruck psys stehende Kraftstoff über mindestens eine Drosselstelle 56, die z. B. als mindestens ein Anschliff am Umfang des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 42 ausgebildet sein kann, in den Düsenraum 50.From the pressurized space 34 acted upon by system pressure p sys , an annular space 52 extends through the injector housing 16. Via the annular space 52, fuel under system pressure p sys flows to a nozzle space designated by reference numeral 50, which is formed inside the nozzle body 18. From the annulus 52 passes under system pressure p sys standing fuel via at least one throttle point 56, the z. B. may be formed as at least one bevel on the circumference of the preferably needle-shaped injection valve member 42, in the nozzle chamber 50th

Das Einspritzventilglied 42 umfasst in dem Bereich, in dem es im Düsenkörper 18 vom Düsenraum 50 umschlossen ist, eine Druckstufe 54.The injection valve member 42 comprises a pressure stage 54 in the region in which it is enclosed in the nozzle body 18 by the nozzle chamber 50.

Vom Düsenraum 50 strömt der unter Systemdruck psys stehende Kraftstoff über einen Ringspalt einem Sitz 58 des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 42 zu. In der Darstellung gemäß der Zeichnung sind Einspritzöffnungen 60 am brennraumseitigen Ende des Kraftstoffinjektors 10 durch das in seinen Sitz 58 gestellte, bevorzugt nadelförmig ausgebildete Einspritzventilglied 42 verschlossen.From the nozzle chamber 50, the fuel under system pressure p sys flows via an annular gap to a seat 58 of the preferably needle-shaped injection valve member 42. In the illustration according to the drawing injection ports 60 are closed at the combustion chamber end of the fuel injector 10 by the asked in his seat 58, preferably needle-shaped injection valve member 42.

Am Umfang des bevorzugt nadelförmig ausgebildeten Einspritzventilglieds 42 befindet sich mindestens eine, bevorzugt als Anschliff ausgebildete Drosselstelle 56. Über diese mindestens eine Drosselstelle 56 sind der unter Systemdruck psys stehende Ringraum 52 und der Düsenraum 50 hydraulisch miteinander verbunden.At least one, preferably formed as a bevel throttle body 56 is at the periphery of the preferably needle-shaped injection valve member 42. About this at least one throttle point 56 of the system pressure p sys standing annular space 52 and the nozzle chamber 50 are hydraulically connected to each other.

Das im Aktorgehäuse 20 untergebrachte Magnetventil 22 umfasst eine Ventilfeder 70, die einen Druckstift 66 umschließt. Die Ventilfeder 70 stützt sich an der Unterseite des Gehäusedeckels 24 ab. Bevorzugt ist der Druckstift 66 lose im Aktorgehäuse 20 aufgenommen. Die Ventilfeder 70 beaufschlagt eine obere Stirnseite eines als Ventilnadel ausgebildeten Ventilglieds 62. An diesem ist eine Ankerplatte 64 ausgebildet, die der Magnetspule 28 des Magnetventils 22 gegenüberliegend angeordnet ist. Der Druckstift 66 ist in einem Durchmesser ausgebildet, der einen Führungsdurchmesser 68 für das Ventilglied 62 darstellt. Eine untere Stirnseite des Druckstiftes 66 begrenzt mit dem bevorzugt nadelförmig ausgebildeten Ventilglied 62 einen Druckausgleichsraum 78. Der vom Druckstift 66 und vom Ventilglied 62 begrenzte Druckausgleichsraum 78 steht über eine Strömungsverbindung 74 mit einem Ventilraum 84 in Verbindung. Gemäß der in der Zeichnung dargestellten Ausführungsform des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors 10 wird der Ventilraum 84 durch eine Kegelfläche 82 im Ventilstück 32 einerseits und andererseits durch eine kugelförmige Fläche 86 am unteren Ende des Ventilglieds 62 begrenzt. In der in der Zeichnung dargestellten Ausführungsform ist die kugelförmige Fläche 86, welche den Kugelsitz darstellt, am Ventilglied 62 ausgeführt. Durch die den Kugelsitz darstellende, kugelförmige Fläche 86 an dem dem Ventilstück 32 zuweisenden Ende des bevorzugt nadelförmig ausgebildeten Ventilglieds 62 kann in vorteilhafter Weise ein Ausgleich von Parallelitätsfehlern zwischen dem Ventilglied 62 und dem den Sitzkörper darstellenden Ventilstück 32 erreicht werden. Zudem lassen sich durch die erfindungsgemäß vorgeschlagene Anordnung günstige, mehrteilige Ventilaufbauten realisieren.The solenoid valve 22 accommodated in the actuator housing 20 comprises a valve spring 70, which encloses a pressure pin 66. The valve spring 70 is supported on the underside of the housing cover 24. Preferably, the pressure pin 66 is loosely received in the actuator housing 20. The valve spring 70 acts on an upper end side of a valve member designed as a valve member 62. At this an anchor plate 64 is formed, which is disposed opposite to the solenoid coil 28 of the solenoid valve 22. The pressure pin 66 is formed in a diameter that represents a guide diameter 68 for the valve member 62. A lower end face of the pressure pin 66 bounded by the preferably needle-shaped valve member 62 a pressure compensation chamber 78. The pressure relief chamber 66 and the valve member 62 limited pressure compensation chamber 78 communicates via a flow connection 74 with a valve chamber 84 in connection. According to the embodiment of the inventively proposed fuel injector 10 shown in the drawing, the valve space 84 is bounded by a conical surface 82 in the valve piece 32 on the one hand and on the other hand by a spherical surface 86 at the lower end of the valve member 62. In the embodiment shown in the drawing, the spherical surface 86, which represents the ball seat, on the valve member 62 is executed. By the ball seat performing, spherical surface 86 at the valve piece 32 facing the end of the preferably needle-shaped valve member 62 can be achieved in an advantageous manner, a compensation of parallelism errors between the valve member 62 and the seat body performing valve member 32. In addition, can be realized by the inventively proposed arrangement favorable, multi-part valve bodies.

In Umkehr des in der Zeichnung dargestellten Kugelsitzes, gebildet durch die am Ventilglied 62 ausgebildete Kugelfläche 86 und die im Ventilstück 32 vorgesehene Kegelfläche 82, kann die Kegelfläche 82 auch am Ventilglied 62 ausgebildet werden und die kugelförmige Fläche 86 am Ventilstück 32 ausgeführt sein. Ferner ist es möglich, sowohl am Ventilglied 62 als auch am Ventilstück 32 jeweils kugelförmige Geometrien zu verwirklichen.Inversion of the ball seat shown in the drawing, formed by the ball member 86 formed on the valve member 62 and provided in the valve member 32 conical surface 82, the conical surface 82 can also be formed on the valve member 62 and the spherical surface 86 on the valve piece 32 to be executed. Further, it is possible to realize both the valve member 62 and the valve piece 32 each spherical geometries.

Aufgrund des Umstandes, dass der Führungsdurchmesser 68 im Wesentlichen dem Durchmesser des durch die kugelförmige Fläche 86 gebildeten Kugelsitzes entspricht, wirkt die Druckausgeglichenheit des Magnetventils 22. Es lässt sich bei der erfindungsgemäß vorgeschlagenen Ventilbauform ein durch Ausbildung einer kugelförmigen Fläche 86 realisierter Kugelsitz im Zusammenwirken mit einer Kegelfläche 82 verwirklichen, da der Druckstift 66 unabhängig vom Ventilsitz 80 von der Gegenseite des Sitzbereiches aus montiert werden kann. Durch Bezugszeichen 74 ist eine Strömungsverbindung kenntlich gemacht, die den Druckausgleichs- oder Dämpfungsraum 78 mit dem Ventilraum 84 verbindet.Due to the fact that the guide diameter 68 substantially corresponds to the diameter of the ball seat formed by the spherical surface 86, the pressure balance of the solenoid valve 22 acts. It can be inventively proposed valve design realized by forming a spherical surface 86 ball seat in cooperation with a Conical surface 82 realize because the pressure pin 66 can be mounted independently of the valve seat 80 from the opposite side of the seating area. By reference numeral 74, a flow connection is identified, which connects the pressure equalization or damping chamber 78 with the valve space 84.

Eine Ausführungsform des in der Zeichnung dargestellten Kraftstoffinjektors ist dadurch gegeben, dass am Druckstift 66, an dem das bevorzugt nadelförmig ausgebildete Ventilglied 62 geführt ist, eine in Schließrichtung wirksame Druckstufe erzeugt wird. Die in Schließrichtung des bevorzugt nadelförmig ausgebildeten Ventilglieds 62 wirksame Druckstufe kann durch eine Vergrößerung des Führungsdurchmessers 68 des lose im Aktorgehäuse 20 aufgenommenen Druckstiftes 66 in Bezug auf den Durchmesser des durch die kugelförmige Fläche 86 gegebenen Kugelsitzes erreicht werden. Durch die in Schließrichtung wirksame Druckstufe wird eine hydraulische Ventilschließkraft erzeugt, wodurch ein Prellen des Magnetventils beim Schließen des Ventilgliedes 62 verringert wird. Das Dämpfungsverhalten beim Schließen des Ventilgliedes 62 kann durch die in Schließrichtung wirksame Druckstufe, gegeben durch die Vergrößerung des Führungsdurchmessers 68 in Bezug auf den Durchmesser des durch die kugelförmige Fläche 86 gegebenen Kugelsitzes, verbessert werden, da sich im geschlossenen Zustand des Kugelsitzes eine hydraulische Schließkraft aufbaut, die ein Wiederöffnen des bevorzugt nadelförmig ausgebildeten Ventilgliedes 62 verhindert. Dies wiederum erlaubt eine optimierte Ventilabstimmung und eine Verbesserung der Mehrfacheinspritzfähigkeit des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors 10.An embodiment of the fuel injector shown in the drawing is given by the fact that at the pressure pin 66, on which the preferably needle-shaped valve member 62 is guided, an effective compression in the closing direction is generated. The effective in the closing direction of the preferably needle-shaped valve member 62 pressure stage can be achieved by increasing the guide diameter 68 of the loosely received in the actuator housing 20 pressure pin 66 with respect to the diameter of the given by the spherical surface 86 ball seat. By acting in the closing direction pressure stage, a hydraulic valve closing force is generated, whereby a bouncing of the Solenoid valve when closing the valve member 62 is reduced. The damping behavior when closing the valve member 62 can be improved by the pressure acting in the closing direction, given by the enlargement of the guide diameter 68 with respect to the diameter of the given by the spherical surface 86 ball seat, since in the closed state of the ball seat builds up a hydraulic closing force which prevents reopening of the preferably needle-shaped valve member 62. This in turn allows for optimized valve tuning and an improvement in the multiple injection capability of the fuel injector 10 proposed according to the invention.

Durch den Druckausgleichs- oder Dämpfungsraum 78, der über die Strömungsverbindung 74 mit dem Ventilraum 84 in Verbindung steht, können die Geschwindigkeit, mit der das Ventilglied 62 öffnet, optimiert werden und die Prelleigenschaften verbessert werden. Werden das bevorzugt nadelförmig ausgebildete Einspritzventilglied 62 und die Ankerplatte 64 als ein Bauteil ausgelegt, so stellt sich eine kleine zu bewegende Masse ein, was durch eine Dämpferdrossel 76, die in der Strömungsverbindung 74 angeordnet ist, zu einem optimierten Dämpfungsverhalten führt, wodurch sehr kurze Abstände bei einzelnen kurz hintereinander folgenden Kraftstoffeinspritzungen über die Einspritzöffnungen 30 ermöglicht werden.By the pressure equalization or damping chamber 78 communicating with the valve space 84 via the flow connection 74, the speed at which the valve member 62 opens can be optimized and the bouncing characteristics improved. If the preferably needle-shaped injection valve member 62 and the armature plate 64 designed as a component, so sets a small mass to be moved, which leads through a damper throttle 76, which is arranged in the flow connection 74 to an optimized damping behavior, resulting in very short distances be made possible with individual fuel injections in quick succession via the injection openings 30.

In vorteilhafter Weise ist der durch die kugelförmige Fläche 86 realisierte Kugelsitz direkt an dem Ventilstück 32 ausgebildet, das den als Servosteuerraum dienenden Steuerraum 36 begrenzt und von dem unter Systemdruck psys stehenden Druckraum 34 im Injektorgehäuse 16 trennt. Das Ventilstück 32 ist über die Stützhülse 30, den sich darauf abstützenden Magnetkern 26 und den Gehäusedeckel 24, mit dem das Aktorgehäuse 20 verschlossen wird, dichtend an den Injektorkörper 16 angestellt.Advantageously, the ball seat realized by the spherical surface 86 is formed directly on the valve piece 32, which limits the control space 36 serving as a servo control room and separates from the pressure space 34 in the injector housing 16 under system pressure p sys . The valve piece 32 is made in a sealing manner against the injector body 16 via the support sleeve 30, the magnetic core 26 resting thereon and the housing cover 24, with which the actuator housing 20 is closed.

Die bei Bestromung des Magnetventils 22 erfolgende, in vertikale Richtung nach oben gerichtete Öffnungsbewegung des bevorzugt nadelförmig ausgebildeten Ventilgliedes 62 bewirkt eine Druckentlastung des Steuerraums 36. Die beim Öffnen des durch die kugelförmige Fläche 86 gegebenen Kugelsitzes aus dem Steuerraum 36 abströmende Steuermenge strömt in das Aktorgehäuse 20 ein und wird über einen niederdruckseitigen Rücklauf 72 in den Niederdruckbereich des Kraftstoffeinspritzsystems abgeleitet. Bei der Druckentlastung des bevorzugt als Servosteuerraum dienenden Steuerraums 36 des Kraftstoffinjektors 10 gemäß der in der Zeichnung dargestellten Ausführungsform erfolgt ein Einfahren der Stirnfläche 44 des nadelförmig ausgebildeten Einspritzventilglieds 42 in den Steuerraum 36. Dadurch strömt über den geöffneten Sitz 58 des Einspritzventilglieds 42 über die mindestens eine am brennraumseitigen Ende des Kraftstoffinjektors 10 ausgebildete Öffnung 60 unter Systemdruck psys stehender Kraftstoff in den Brennraum der Verbrennungskraftmaschine.The taking place during energization of the solenoid valve 22, in vertical upward upward opening movement of the preferably needle-shaped valve member 62 causes a pressure relief of the control chamber 36. The opening when the given by the spherical surface 86 ball seat from the control chamber 36 flowing outflow quantity flows into the actuator housing 20th and is discharged via a low-pressure side return 72 in the low pressure region of the fuel injection system. In the pressure relief of serving preferably as a servo control chamber control chamber 36 of the fuel injector 10 according to the embodiment shown in the drawing, retraction of the end face 44 of the needle-shaped injection valve member 42 into the control chamber 36. This flows through the open seat 58 of the injection valve member 42 via the at least a formed at the combustion chamber end of the fuel injector 10 opening 60 under system pressure p sys standing fuel into the combustion chamber of the internal combustion engine.

Das Öffnungsverhalten des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 42 lässt sich über die an dessen Umfang ausgebildete, mindestens eine bevorzugt als Anschliff ausgebildete Drosselstelle 56 optimieren. Die mindestens eine am Umfang des bevorzugt nadelförmig ausgebildeten Einspritzventilglieds 42 ausgebildete Drosselstelle 56 stellt eine hydraulische Verbindung mit dem unter Systemdruck psys stehenden Ringraum 52 im Injektorkörper 16 mit dem Düsenraum 50, der im Düsenkörper 18 des Kraftstoffinjektors 10 ausgebildet ist, dar.The opening behavior of the preferably needle-shaped injection valve member 42 can be optimized by means of the throttle point 56, which is formed on the circumference thereof and has at least one preferably formed as a bevel. The at least one throttle point 56 formed on the circumference of the preferably needle-shaped injection valve member 42 provides a hydraulic connection with the annular space 52 under system pressure p sys in the injector body 16 with the nozzle chamber 50 formed in the nozzle body 18 of the fuel injector 10.

Das druckausgeglichene Magnetventil 22 wird in Einspritzsystemen zum Einspritzen von Kraftstoff eingesetzt, als Steuerventil für einen servogesteuerten Kraftstoffinjektor, der bei Hochdruckspeichereinspritzsystemen (Common-Rail) einsetzbar ist.The pressure compensated solenoid valve 22 is employed in fuel injection injection systems as a servo-controlled fuel injector control valve applicable to high-pressure common-rail injection systems.

Claims (6)

  1. Fuel injector (10) for injecting fuel into the combustion chamber of an internal combustion engine, with an injection valve member (42) being actuated by means of a release of pressure from a control chamber (36) which is charged with a system pressure psys, and with the release of pressure from the control chamber (36) taking place via a pressure-balanced solenoid valve (22) whose valve member (62) opens or closes off a valve seat (80), characterized
    - in that a spherical surface (86) is formed on the valve member (62), which spherical surface forms a valve seat (80) with a conical surface (82) in a valve piece (32).
  2. Fuel injector (10) according to Claim 1, characterized in that the valve member (62) is guided on a pressure pin (66) and, with the latter, delimits a pressure compensation chamber (78).
  3. Fuel injector (10) according to Claim 2, characterized in that the valve member (62) has a flow connection (74) between the pressure compensation chamber or damper chamber (78) and the valve seat (80).
  4. Fuel injector (10) according to Claim 3, characterized in that a throttle point (76) is formed in the flow connection (74).
  5. Fuel injector (10) according to Claim 1, characterized in that the valve member (62) is guided on a pressure pin (66) whose guide diameter (68) corresponds to an inner diameter of the valve member (62).
  6. Fuel injector (10) according to Claim 1, characterized in that the valve seat (80) is formed on a valve piece (32) which delimits the control chamber (36) and which closes off a pressure chamber (34) in the injector body (16) with respect to a low-pressure region.
EP07821236A 2006-12-04 2007-10-12 Fuel injector having a solenoid valve with a spherical seat Not-in-force EP2100026B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057025A DE102006057025A1 (en) 2006-12-04 2006-12-04 Fuel injector for injecting fuel into combustion chamber of internal combustion engine, has pressure-compensating magnetic valve with valve element that opens or locks valve seat, where valve element or piece of valve has spherical surface
PCT/EP2007/060869 WO2008068093A1 (en) 2006-12-04 2007-10-12 Fuel injector having a solenoid valve with a spherical seat

Publications (2)

Publication Number Publication Date
EP2100026A1 EP2100026A1 (en) 2009-09-16
EP2100026B1 true EP2100026B1 (en) 2010-12-22

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Application Number Title Priority Date Filing Date
EP07821236A Not-in-force EP2100026B1 (en) 2006-12-04 2007-10-12 Fuel injector having a solenoid valve with a spherical seat

Country Status (5)

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EP (1) EP2100026B1 (en)
CN (1) CN101548092B (en)
AT (1) ATE492719T1 (en)
DE (2) DE102006057025A1 (en)
WO (1) WO2008068093A1 (en)

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DE102007011685A1 (en) * 2007-03-09 2008-09-11 Robert Bosch Gmbh Fuel injector with improved control valve
DE102007035698A1 (en) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Fuel injection valve with improved tightness at the sealing seat of a pressure-balanced control valve
DE102008001600A1 (en) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Fuel injector with a pressure valve having a control valve
DE102009046563A1 (en) * 2009-11-10 2011-05-12 Robert Bosch Gmbh fuel injector
DE102009060029A1 (en) * 2009-12-21 2011-06-22 Robert Bosch GmbH, 70469 Electromagnetically switchable valve for installation in a built-in block
CN102213165B (en) * 2010-04-08 2013-02-13 北京亚新科天纬油泵油嘴股份有限公司 High pressure common rail electronic control fuel injector
DE102013206383A1 (en) * 2013-04-11 2014-10-16 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102018109206A1 (en) * 2018-04-18 2019-10-24 Liebherr-Components Deggendorf Gmbh Injector for injecting fuel

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DE29807601U1 (en) * 1998-04-27 1998-08-20 Fev Motorentech Gmbh & Co Kg Hydraulic slide valve
DE19952511B4 (en) * 1999-10-30 2004-09-30 Robert Bosch Gmbh Common rail injector
ES2277229T3 (en) * 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE.
AT500889B8 (en) * 2004-08-06 2007-02-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
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DE102005062549A1 (en) * 2005-12-27 2007-07-05 Robert Bosch Gmbh Fuel injector for internal combustion engine has control valve fully integrated into fuel injector, high pressure fuel storage device connected to control chamber and integrated into fuel injector

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Also Published As

Publication number Publication date
ATE492719T1 (en) 2011-01-15
EP2100026A1 (en) 2009-09-16
DE502007006059D1 (en) 2011-02-03
CN101548092A (en) 2009-09-30
WO2008068093A1 (en) 2008-06-12
DE102006057025A1 (en) 2008-06-05
CN101548092B (en) 2012-12-19

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