EP1319125B1 - Servo control valve for injectors - Google Patents

Servo control valve for injectors Download PDF

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Publication number
EP1319125B1
EP1319125B1 EP01967354A EP01967354A EP1319125B1 EP 1319125 B1 EP1319125 B1 EP 1319125B1 EP 01967354 A EP01967354 A EP 01967354A EP 01967354 A EP01967354 A EP 01967354A EP 1319125 B1 EP1319125 B1 EP 1319125B1
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EP
European Patent Office
Prior art keywords
valve body
control piston
piston
control
corresponding valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01967354A
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German (de)
French (fr)
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EP1319125A1 (en
Inventor
Wolfgang Scheibe
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LOrange GmbH
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LOrange GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/043—Fluid pressure acting on injection-valve in the period of non-injection to keep it closed
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/006—Springs assisting hydraulic closing force

Definitions

  • the invention relates to a servo valve combined with an actuating piston of an injection injector of internal combustion engines, in particular of internal combustion engines operating with accumulator pressure injection and operated with diesel or heavy oil
  • Such injection injectors are known from practice and usually comprise an injection nozzle, a control valve associated therewith, a servo control valve responsive to the control valve, and an axial actuator, usually in the form of a magnetic actuator. Due to such a structure is characterized in that on magnet master suitable size with direct application of the control valve hardly the required restoring forces can be applied, so that a servo control valve is interposed, which has quasi amplifier function and which operates with a stepped throttle system, wherein the spring-loaded armature the outflow throttle controls, so that the force must be applied by the magnet armature to its closed position loading spring, which are necessary depending on the control oil pressure and the cross section of the controlled via the armature drain valve to lock the outflow cross section at coverage by the armature.
  • a control valve combined with an injector which sequentially opens two outflow cross sections in order to relieve a pressure chamber connected to an actuating piston of the injector. So this is a control valve for three positions.
  • the control valve is formed by a valve disposed in a space, actuated by an axial control piston, which is surrounded by a sleeve-shaped, guided on the control piston valve member with the invention has in common that the control piston has a control edge, which cooperates with a sealing edge.
  • the corresponding sealing edge is
  • the invention formed in the region of one end of the valve member and the valve member is in one piece.
  • a control edge is formed, which cooperates with a sealing edge of the injector.
  • the sleeve-shaped valve member is axially entrained by the control piston, while compared to the inventive design, the valve member is only partially axially movable, wherein the movable part is not only supported on the control piston, but also on the control piston of the injection injector.
  • a drain channel is arranged in the control piston, which requires that a radial passage in the control piston is provided, in turn, by the inventive arrangement conditionally connected to the control and sealing edges in the middle of the two-part valve member, with corresponding switching position of the control valve with flow channels on the outer circumference of the valve member.
  • the invention has for its object to provide a servo control valve for injection injectors, which despite high restrictions on the axial plate, in particular a magnetic actuator applied adjusting forces high actuating speeds at the required, applied relatively high actuating forces.
  • a servo control valve for injection injectors by an embodiment according to claim 1, according to which a 3/2-way valve is used as servo control valve, which allows sufficiently large control cross sections and despite integration into the injection injector has a relatively simple structure. This is done with a valve guide insert, the injector housing is received and is tightly pressed in the injector to fix, by a transverse training at the same time but the best conditions for high precision, also allows for the fit into the injector. At the same time, high actuating speeds can be achieved.
  • the inventive design by the transverse division of the valve guide insert and the leadership of its serving as a counter-valve body on the control piston, also particularly favorable conditions to compensate for any tolerances in the Achs mecanic the valve parts and their assignment to the actuating piston, as well as the channel paths within the Servo confuseventiles and also to make the connections easy and with large cross sections.
  • the figures show a section of an injection injector 1, wherein 2 denotes a portion of a control valve 2, which is preceded by a servo control valve 3.
  • 2 denotes a portion of a control valve 2, which is preceded by a servo control valve 3.
  • a servo control valve 3 In the chain of action before it is an axial actuator in the form of a schematically indicated magnetic actuator 4 with a magnet armature 5 which is loaded in the direction of the servo control valve 3 via a spring 6. If the magnetic plate 4 is energized, the armature 5 is raised against the force of the spring 6.
  • the magnet armature 5 acts on a control piston 7, which is arranged in a valve guide insert 8, which is transversely divided relative to the common alignment axis 9 of magnetic actuator 4, servo control valve 3 and control valve 2 and its one part as a valve body 10 and the other part as a counter valve body 11 axially connect to each other and are supported against each other, wherein the valve body 10 is sealingly pressed axially into a receiving housing for the servo control valve 3.
  • the housing region enclosing the valve guide insert 8 is designated by 12 and may be formed by a housing part of the injection injector 1.
  • the dividing plane between the valve body 10 and the counter valve body 11 is located between the axially spaced sealing edges 14 and 15, of which the sealing edge 14 of the valve body 10 and the sealing edge 15 is associated with the counter valve body 11, which include the valve chamber 16 between them.
  • the valve chamber 16 is on the part of the control piston 7 associated with a collar 17, the control edges 18 and 19 which cooperate with relatively small radial overlap of the annular collar 17 to the valve chamber 16 with the sealing edges 14 and 15 of the valve chamber 16, if in accordance with the axial displacement of the control piston 7 one or the other comes in their investment position.
  • the control piston 7 On both sides of the annular collar 17, the control piston 7 in annular areas withdrawn annular areas as annular spaces 20 and 21, wherein the annular chamber 21 is limited in the region of the counter valve body 11 end of the control piston 7 by a guide collar 22, on which, as a centering collar, the counter valve body 11 is guided, wherein the counter-valve body 11 in cup-shaped configuration has a bottom zone 23 which engages under the control piston 7 and the support for a spring 24th forms, which is supported in an axial bore 25 of the control piston 7 lying against a shoulder 26 thereof.
  • the bottom zone 23 forms a support for a spring 27, which acts on a pressure chamber 28 bridging a control piston 29 which is axially displaceable associated with the control valve 2 and is supported against the control piston.
  • the annular space 20 is associated with a supply port 30 which is formed by a radial bore and passes through the valve body 10 and the subsequent housing portion.
  • the supply connection 30 is a high-pressure connection via which control oil is supplied. This occurs in the switching position of the servo control valve 3 shown, in which the magnet armature 5 via the spring 6, the control piston 7 in the direction of the counter valve body 11 loaded and in which the sealing edge 15 sealingly cooperates with the control edge 19, on the valve chamber 16 via, and passes
  • the radial Studentsströmquerête 31 are formed as annular gaps or the like, which are formed, for example, by the counter valve body 11 and the valve body 10 are spacer elements by axial projections on the valve body 10 and / or are formed on the counter-valve body 11.
  • an annular insert may be provided, the corresponding crossover cross sections 31 releases.
  • the countervalve body 11 can lie radially spaced from the wall of the receiving bore 37 for the valve body 10 via the guide collar 22 or corresponding guide surfaces, so that axial throughflow paths 32 to the pressure chamber 28 result from the overflow cross sections 31.
  • the actuating piston 29 is pressure-loaded in addition to the spring 27 via the high-pressure supply port 30 and its connection to the pressure chamber 28 and thus holds the control piston of the control valve, not shown, in a position corresponding to the closed position of the injection nozzle.
  • the control piston 7 is in the upper stop position, not shown, in which the sealing edge 14 cooperates with the control edge 18, reversed, with the result that the pressure chamber 28 is connected via the overflow cross-sections 31, the annular space 21 and an opening onto the axial bore 25 fürströmquerrough to the return line 36.
  • the addressed overflow cross section can, as shown in FIG. 2, be formed by radial bores 33 or else by the annular collar having axial passage openings 34 which allow the piston 7 to pass into the axial bore 25 at the end.
  • the axial bore 25 is, as indicated by the arrow 35, with the return passage 36 in connection.
  • control valve construction according to the invention is designed so that it is well manageable in terms of manufacturing technology, since the guide seat and stop surfaces for the Valve body 10 as well as for the counter valve body 11 could be ground in one clamping, so that close tolerances are possible.

Abstract

The invention relates to an embodiment of a servo control valve (3) for injectors in internal combustion engines in the form of a 3/2 directional control valve. A transversally divided valve guide insert (8) is used, one part thereof acting as a guide for the piston (7) and, another part (11) being guided on the piston, whereby said parts are axially supported against each other.

Description

Die Erfindung betrifft ein mit einem Stellkolben eines Einspritzinjektors von Brennkraftmaschinen kombiniertes Servoventil, insbesondere von mit Speicherdruckeinspritzung arbeitenden und mit Diesel oder Schweröl betriebenen BrennkraftmaschinenThe invention relates to a servo valve combined with an actuating piston of an injection injector of internal combustion engines, in particular of internal combustion engines operating with accumulator pressure injection and operated with diesel or heavy oil

Derartige Einspritzinjektoren sind aus der Praxis bekannt und umfassen üblicherweise eine Einspritzdüse, ein dieser zugeordnetes Steuerventil, ein das Steuerventil ansprechendes Servosteuerventil und einen Axialsteller, meist in Form eines Magnetstellers. Bedingt ist ein derartiger Aufbau dadurch, dass über Magnetsteller passender Größe bei direkter Beaufschlagung des Steuerventiles kaum die erforderlichen Stellkräfte aufgebracht werden können, so dass ein Servosteuerventil zwischengeschaltet wird, das quasi Verstärkerfunktion hat und das mit einem abgestuften Drosselsystem arbeitet, wobei der federbelastete Magnetanker den Abflussdrosselquerschnitt steuert, so dass durch die den Magnetanker auf seine Schließstellung belastende Stellfeder die Kräfte aufgebracht werden müssen, die abhängig vom Steueröldruck und dem Querschnitt der über den Magnetanker gesteuerten Abflussdrossel nötig sind, den Abflussquerschnitt bei Überdeckung durch den Magnetanker zu sperren. Hierdurch ergeben sich sowohl hinsichtlich der Arbeitsdrücke wie auch hinsichtlich des über den Magnetanker bei nicht bestromten Magneten abzudeckenden Querschnittes Beschränkungen, da die den Magnetanker im Hinblick auf die Sperrstellung belastende Feder schwächer sein muss als die vom Magneten bei Bestromung aufzubringende Hubkraft.Such injection injectors are known from practice and usually comprise an injection nozzle, a control valve associated therewith, a servo control valve responsive to the control valve, and an axial actuator, usually in the form of a magnetic actuator. Due to such a structure is characterized in that on magnet master suitable size with direct application of the control valve hardly the required restoring forces can be applied, so that a servo control valve is interposed, which has quasi amplifier function and which operates with a stepped throttle system, wherein the spring-loaded armature the outflow throttle controls, so that the force must be applied by the magnet armature to its closed position loading spring, which are necessary depending on the control oil pressure and the cross section of the controlled via the armature drain valve to lock the outflow cross section at coverage by the armature. This results in both in terms of working pressures as well as in terms of over the armature when not energized magnet cross-section restrictions, since the magnetic armature with regard to the locking position stressing spring must be weaker than the force applied by the magnet when energized lifting force.

Aus der US 6,085,719 A geht ein mit einem Injektor kombiniertes Steuerventil als bekannt hervor, das zur Entlastung eines mit einem Stellkolben des Injektors verbundenen Druckraums sequentiell nacheinander zwei Abflussquerschnitte aufsteuert. Es handelt sich hier also um ein Steuerventil für drei Schaltstellungen. Das Steuerventil wird von einem innerhalb eines Ventilraums gelegenen, von einem Axialsteller betätigten Steuerkolben gebildet, der von einem hülsenförmigen, auf dem Steuerkolben geführten Ventilglied umgeben ist Mit der Erfindung ist gemeinsam, dass der Steuerkolben eine Steuerkante besitzt, die mit einer Dichtkante zusammenwirkt. Die entsprechende Dichtkante ist jedoch im Gegensatz zur Erfindung im Bereich eines Endes des Ventilglieds ausgebildet und das Ventilglied ist einteilig. Am gegenüberliegenden, vom Druckraum abgewandten Ende des Ventilglieds ist eine Steuerkante ausgebildet, die mit einer Dichtkante des Injektorgehäuses zusammenwirkt. Zum Aufsteuern letzterer Dichtkante wird das hülsenförmige Ventilglied axial vom Steuerkolben mitgenommen, während im Vergleich zur erfindungsgemäßen Ausbildung das Ventilglied nur teilweise axial beweglich ist, wobei der bewegliche Teil zudem nicht nur am Steuerkolben, sondern auch am Stellkolben des Einspritzinjektors abgestützt ist. Der Abfluss von Steuerfluid erfolgt über Axialkanäle auf der Innen- und Außenseite des hülsenförmigen Ventilglieds, während beim erfindungsgemäßen Gegenstand nach Anspruch 1 ein Abflusskanal im Steuerkolben angeordnet ist, was bedingt, dass ein radialer Durchgang im Steuerkolben vorzusehen ist, der, wiederum durch die erfindungsgemäße Anordnung der Steuer- und Dichtkanten in der Mitte des zweigeteilten Ventilglieds bedingt, bei entsprechender Schaltstellung des Steuerventils mit Strömungskanälen auf dem Außenumfang des Ventilglieds in Verbindung steht.From US Pat. No. 6,085,719 A, a control valve combined with an injector is known, which sequentially opens two outflow cross sections in order to relieve a pressure chamber connected to an actuating piston of the injector. So this is a control valve for three positions. The control valve is formed by a valve disposed in a space, actuated by an axial control piston, which is surrounded by a sleeve-shaped, guided on the control piston valve member with the invention has in common that the control piston has a control edge, which cooperates with a sealing edge. The corresponding sealing edge is However, in contrast to the invention formed in the region of one end of the valve member and the valve member is in one piece. At the opposite, remote from the pressure chamber end of the valve member, a control edge is formed, which cooperates with a sealing edge of the injector. To open the latter sealing edge, the sleeve-shaped valve member is axially entrained by the control piston, while compared to the inventive design, the valve member is only partially axially movable, wherein the movable part is not only supported on the control piston, but also on the control piston of the injection injector. The outflow of control fluid via axial channels on the inside and outside of the sleeve-shaped valve member, while the article according to the invention according to claim 1, a drain channel is arranged in the control piston, which requires that a radial passage in the control piston is provided, in turn, by the inventive arrangement conditionally connected to the control and sealing edges in the middle of the two-part valve member, with corresponding switching position of the control valve with flow channels on the outer circumference of the valve member.

Der Erfindung liegt die Aufgabe zugrunde, ein Servosteuerventil für Einspritzinjektoren zu schaffen, das trotz vorgegebener Beschränkungen hinsichtlich der über den Axialsteller, insbesondere einen Magnetsteller aufgebrachten Stellkräfte hohe Stellgeschwindigkeiten bei den erforderlichen, aufzubringenden relativ hohen Stellkräfte ermöglicht.The invention has for its object to provide a servo control valve for injection injectors, which despite high restrictions on the axial plate, in particular a magnetic actuator applied adjusting forces high actuating speeds at the required, applied relatively high actuating forces.

Erreicht wird dies bei einem Servosteuerventil für Einspritzinjektoren durch eine Ausgestaltung gemäß dem Anspruch 1, demzufolge als Servosteuerventil ein 3/2-Wegeventil verwendet wird, das hinreichend große Steuerquerschnitte ermöglicht und trotz Integration in den Einspritzinjektor einen vergleichsweise einfachen Aufbau aufweist. Gearbeitet wird hierzu mit einem Ventilführungseinsatz, der vom lnjektorgehäuse aufgenommen wird und der im Injektorgehäuse dicht eingepresst zu fixieren ist, durch eine quergeteilte Ausbildung zugleich aber beste Voraussetzungen für hohe Präzision, auch hinsichtlich der Einpassung in den Injektor ermöglicht. Zugleich lassen sich hohe Stellgeschwindigkeiten erreichen. Insbesondere bietet die erfindungsgemäße Ausgestaltung, durch die Querteilung des Ventilführungseinsatzes und die Führung von dessen als Gegenventilkörper dienendem Teil auf dem Steuerkolben, auch besonders günstige Voraussetzungen etwaige Toleranzen in der Achsierung der Ventilteile und deren Zuordnung zum Stellkolben auszugleichen, sowie auch die Kanalwege innerhalb des Servosteuerventiles sowie auch zu den Anschlüssen einfach und mit großen Querschnitten zu gestalten.This is achieved in a servo control valve for injection injectors by an embodiment according to claim 1, according to which a 3/2-way valve is used as servo control valve, which allows sufficiently large control cross sections and despite integration into the injection injector has a relatively simple structure. This is done with a valve guide insert, the injector housing is received and is tightly pressed in the injector to fix, by a transverse training at the same time but the best conditions for high precision, also allows for the fit into the injector. At the same time, high actuating speeds can be achieved. In particular, the inventive design, by the transverse division of the valve guide insert and the leadership of its serving as a counter-valve body on the control piston, also particularly favorable conditions to compensate for any tolerances in the Achsierung the valve parts and their assignment to the actuating piston, as well as the channel paths within the Servosteuerventiles and also to make the connections easy and with large cross sections.

Abgesehen von der Anwendung in Einspritzinjektoren können Ventile der geschilderten Art mit quergeteiltem Ventilführungseinsatz auch anderweitig zweckmäßig sein, da durch die Aufteilung des Ventileinsatzes in einen für den Steuerkolben führenden Teil und in einen vom Steuerkolben geführten Teil nicht nur Vorteile hinsichtlich des Aufbaues als druckausgeglichenem Ventil, bei mit einem radial überstehenden Steuerbund ausgebildetem Steuerkolben, hinsichtlich Aufbau und Montage erreichbar sind, sondern gegebenenfalls auch für Servicezwecke der Zugriff auf die Innenteile des Ventiles erleichtert wird, ohne dass dessen Zentrierung gegenüber dem jeweils aufnehmenden Teil aufgegeben bzw. gelöst werden muss, da der Zugang über den auf dem Kolben geführten Teil des Ventileinführungseinsatzes möglich wird.Apart from the application in Einspritzmitjektoren valves of the kind described with transversely divided valve guide insert may also be useful elsewhere, as by the division of the valve insert in a leading part for the control piston and in a part guided by the control piston not only advantages in terms of design as a pressure balanced valve at with a radially projecting control collar trained control piston, in terms of design and installation can be achieved, but possibly also for service purposes, the access to the internal parts of the valve is facilitated without its centering against the respective receiving part must be abandoned or solved because the access via the guided on the piston part of the valve insertion insert is possible.

Weitere Einzelheiten und Merkmale der Erfindung ergeben sich aus den Ansprüchen. Ferner wird die Erfindung nachstehend anhand eines Ausführungsbeispieles näher erläutert. Es zeigen:

Figur 1
in stark schematisierter Darstellung einen Ausschnitt aus einem Einspritzinjektor, wobei dieser Ausschnitt im wesentlichen auf die Darstellung des Servosteuerventiles im Schnitt beschränkt ist, das über einen Axialsteller in Form eines Magnetstellers angesprochen wird und über das die Druckbeaufschlagung für einen Stellkolben, bevorzugt einen Stellkolben eines Steuerventiles gesteuert wird, und
Figur 2
eine Ausschnittsvergrößerung entsprechend A in Figur 1.
Further details and features of the invention will become apparent from the claims. Furthermore, the invention will be explained below with reference to an exemplary embodiment. Show it:
FIG. 1
in a highly schematic representation of a section of an injection injector, this section is essentially limited to the representation of the servo control valve in section, which is addressed via an axial adjuster in the form of a magnetic actuator and controlled by the pressurization of an actuating piston, preferably an actuating piston of a control valve will, and
FIG. 2
an enlarged detail corresponding to A in Figure 1.

Die Figuren zeigen einen Ausschnitt aus einem Einspritzinjektor 1, wobei mit 2 ein Teilbereich eines Steuerventiles 2 bezeichnet ist, dem ein Servosteuerventil 3 vorgelagert ist. In der Wirkkette davor liegt ein Axialsteller in Form eines schematisch angedeuteten Magnetstellers 4 mit einem Magnetanker 5 der in Richtung auf das Servosteuerventil 3 über eine Feder 6 belastet ist. Wird der Magnetsteller 4 bestromt, so wird der Magnetanker 5 gegen die Kraft der Feder 6 angehoben.The figures show a section of an injection injector 1, wherein 2 denotes a portion of a control valve 2, which is preceded by a servo control valve 3. In the chain of action before it is an axial actuator in the form of a schematically indicated magnetic actuator 4 with a magnet armature 5 which is loaded in the direction of the servo control valve 3 via a spring 6. If the magnetic plate 4 is energized, the armature 5 is raised against the force of the spring 6.

Der Magnetanker 5 wirkt auf einen Steuerkolben 7, der in einem Ventilführungseinsatz 8 angeordnet ist, welcher bezogen auf die gemeinsame Fluchtachse 9 von Magnetsteller 4, Servosteuerventil 3 und Steuerventil 2 quergeteilt ist und dessen einer Teil als Ventilkörper 10 und dessen anderer Teil als Gegenventilkörper 11 axial aneinander anschließen und gegeneinander abgestützt sind, wobei der Ventilkörper 10 in ein Aufnahmegehäuse für das Servosteuerventil 3 dichtend axial eingepresst ist. Der den Ventilführungseinsatz 8 umschließende Gehäusebereich ist mit 12 bezeichnet und kann durch einen Gehäuseteil des Einspritzinjektors 1 gebildet sein.The magnet armature 5 acts on a control piston 7, which is arranged in a valve guide insert 8, which is transversely divided relative to the common alignment axis 9 of magnetic actuator 4, servo control valve 3 and control valve 2 and its one part as a valve body 10 and the other part as a counter valve body 11 axially connect to each other and are supported against each other, wherein the valve body 10 is sealingly pressed axially into a receiving housing for the servo control valve 3. The housing region enclosing the valve guide insert 8 is designated by 12 and may be formed by a housing part of the injection injector 1.

Die Teilungsebene zwischen Ventilkörper 10 und Gegenventilkörper 11 liegt zwischen den axial beabstandeten Dichtkanten 14 und 15, von denen die Dichtkante 14 dem Ventilkörper 10 und die Dichtkante 15 dem Gegenventilkörper 11 zugeordnet ist, die zwischen sich die Ventilkammer 16 einschließen. Der Ventilkammer 16 ist seitens des Steuerkolbens 7 ein Ringbund 17 zugeordnet, der Steuerkanten 18 und 19 aufweist, welche bei verhältnismäßig geringer radialer Überdeckung des Ringbundes 17 zur Ventilkammer 16 mit den Dichtkanten 14 und 15 der Ventilkammer 16 zusammenwirken, wenn entsprechend dem axialen Verstellweg des Steuerkolbens 7 die eine oder die andere in ihrer Anlagestellung kommt.The dividing plane between the valve body 10 and the counter valve body 11 is located between the axially spaced sealing edges 14 and 15, of which the sealing edge 14 of the valve body 10 and the sealing edge 15 is associated with the counter valve body 11, which include the valve chamber 16 between them. The valve chamber 16 is on the part of the control piston 7 associated with a collar 17, the control edges 18 and 19 which cooperate with relatively small radial overlap of the annular collar 17 to the valve chamber 16 with the sealing edges 14 and 15 of the valve chamber 16, if in accordance with the axial displacement of the control piston 7 one or the other comes in their investment position.

Beiderseits des Ringbundes 17 weist der Steuerkolben 7 im Durchmesser zurückgenommene Ringbereiche als Ringräume 20 und 21 auf, wobei die Ringkammer 21 im Bereich des im Gegenventilkörper 11 liegenden Endes des Steuerkolbens 7 durch einen Führungsbund 22 begrenzt ist, auf dem, quasi als Zentrierbund, der Gegenventilkörper 11 geführt ist, wobei der Gegenventilkörper 11 bei napfförmiger Ausbildung eine Bodenzone 23 aufweist, die den Steuerkolben 7 untergreift und die die Abstützung für eine Feder 24 bildet, welche in einer Axialbohrung 25 des Steuerkolbens 7 liegend gegen eine Schulter 26 desselben abgestützt ist.On both sides of the annular collar 17, the control piston 7 in annular areas withdrawn annular areas as annular spaces 20 and 21, wherein the annular chamber 21 is limited in the region of the counter valve body 11 end of the control piston 7 by a guide collar 22, on which, as a centering collar, the counter valve body 11 is guided, wherein the counter-valve body 11 in cup-shaped configuration has a bottom zone 23 which engages under the control piston 7 and the support for a spring 24th forms, which is supported in an axial bore 25 of the control piston 7 lying against a shoulder 26 thereof.

In Gegenrichtung bildet die Bodenzone 23 eine Abstützung für eine Feder 27, die einen Druckraum 28 überbrückend einen Stellkolben 29 beaufschlagt, der axial verschieblich dem Steuerventil 2 zugeordnet ist und sich gegen dessen Steuerkolben abstützt.In the opposite direction, the bottom zone 23 forms a support for a spring 27, which acts on a pressure chamber 28 bridging a control piston 29 which is axially displaceable associated with the control valve 2 and is supported against the control piston.

Dem Ringraum 20 ist ein Versorgungsanschluss 30 zugeordnet, der durch eine Radialbohrung gebildet ist und den Ventilkörper 10 und den anschließenden Gehäusebereich durchsetzt. Im Ausführungsbeispiel ist der Versorgungsanschluss 30 ein Hochdruckanschluss, über den Steueröl zugeführt wird. Dieses tritt in der gezeigten Schaltstellung des Servosteuerventiles 3, in der der Magnetanker 5 über die Feder 6 den Steuerkolben 7 in Richtung auf den Gegenventilkörper 11 belastet und in der die Dichtkante 15 mit der Steuerkante 19 dichtend zusammenwirkt, auf die Ventilkammer 16 über, und gelangt von dort über radiale Überströmquerschnitte 31 in den Druckraum 28. Hierbei sind die radialen Überströmquerschnitte 31 als Ringspalte oder dergleichen ausgebildet, die beispielsweise dadurch gebildet sind, das zwischen dem Gegenventilkörper 11 und dem Ventilkörper 10 Distanzelemente liegen, die durch axiale Ansätze an dem Ventilkörper 10 und/oder an dem Gegenventilkörper 11 gebildet sind. Gegebenenfalls kann auch ein ringförmiger Einsatz vorgesehen sein, der entsprechende Übertrittsquerschnitte 31 freigibt.The annular space 20 is associated with a supply port 30 which is formed by a radial bore and passes through the valve body 10 and the subsequent housing portion. In the exemplary embodiment, the supply connection 30 is a high-pressure connection via which control oil is supplied. This occurs in the switching position of the servo control valve 3 shown, in which the magnet armature 5 via the spring 6, the control piston 7 in the direction of the counter valve body 11 loaded and in which the sealing edge 15 sealingly cooperates with the control edge 19, on the valve chamber 16 via, and passes Here, the radial Überströmquerschnitte 31 are formed as annular gaps or the like, which are formed, for example, by the counter valve body 11 and the valve body 10 are spacer elements by axial projections on the valve body 10 and / or are formed on the counter-valve body 11. Optionally, an annular insert may be provided, the corresponding crossover cross sections 31 releases.

Der Gegenventilkörper 11 kann aufgrund seiner Führung auf dem Steuerkolben 7 über den Führungsbund 22 oder entsprechende Führungsflächen, radial beabstandet zur Wandung der Aufnahmebohrung 37 für den Ventilkörper 10 liegen, so dass sich ausgehend von den Überströmquerschnitten 31 axiale Durchströmungswege 32 auf den Druckraum 28 ergeben. Damit ist der Stellkolben 29 über den Hochdruckversorgungsanschluss 30 und dessen Verbindung zum Druckraum 28 zusätzlich zur Feder 27 druckbelastet und hält damit den Steuerkolben des nicht dargestellten Steuerventiles in einer der Schließlage der Einspritzdüse entsprechenden Stellung.Due to its guidance on the control piston 7, the countervalve body 11 can lie radially spaced from the wall of the receiving bore 37 for the valve body 10 via the guide collar 22 or corresponding guide surfaces, so that axial throughflow paths 32 to the pressure chamber 28 result from the overflow cross sections 31. Thus, the actuating piston 29 is pressure-loaded in addition to the spring 27 via the high-pressure supply port 30 and its connection to the pressure chamber 28 and thus holds the control piston of the control valve, not shown, in a position corresponding to the closed position of the injection nozzle.

Wird der Magnet 5 bestromt, so wird der Steuerkolben 7 in die nicht dargestellte obere Anschlaglage, in der die Dichtkante 14 mit der Steuerkante 18 zusammenwirkt, umgesteuert, mit der Folge, dass der Druckraum 28 über die Überströmquerschnitte 31, den Ringraum 21 und einen auf die Axialbohrung 25 mündenden Überströmquerschnitt an den Rücklauf 36 angeschlossen ist. Der angesprochene Überströmquerschnitt kann, wie in Figur 2 gezeigt, durch Radialbohrungen 33 oder auch dadurch gebildet sein, dass der Ringbund axiale Durchlassöffnungen 34 aufweist, die zum Kolben 7 stirnseitig den Übertritt in die Axialbohrung 25 ermöglichen. Die Axialbohrung 25 steht, wie durch den Pfeil 35 angedeutet, mit dem Rücklaufkanal 36 in Verbindung.If the magnet 5 is energized, the control piston 7 is in the upper stop position, not shown, in which the sealing edge 14 cooperates with the control edge 18, reversed, with the result that the pressure chamber 28 is connected via the overflow cross-sections 31, the annular space 21 and an opening onto the axial bore 25 Überströmquerschnitt to the return line 36. The addressed overflow cross section can, as shown in FIG. 2, be formed by radial bores 33 or else by the annular collar having axial passage openings 34 which allow the piston 7 to pass into the axial bore 25 at the end. The axial bore 25 is, as indicated by the arrow 35, with the return passage 36 in connection.

Für Zu- und Ablauf lassen sich bei dieser Lösung verhältnismäßig große Querschnitte verwirklichen, so dass sich kurze Schaltzeiten ergeben. Ferner ist in der Übergangsphase zwischen den beiden Schaltstellungen des Steuerkolbens 7 ein Kurzschluss der Druckkammer 28 sowohl zum Zulauf - Anschluss 30 - wie auch zum Rücklauf - Anschluss 36 - gegeben. Wird das Einspritzventil geöffnet, so entspricht dies einer Bestromung des Magneten 4 und einer Absteuerung des zulaufseitigen Versorgungsanschlusses 30 durch Verschiebung des Steuerkolbens 7 an seine in der Zeichnung obere Dichtgrenze, gebildet durch die Steuerkante 18 und die Dichtkante 14. Im Zuge dieser Umsteuerung wird der zulaufseitige Anschluss (Versorgungsanschluss 30) zunehmend abgesteuert, bei gleichzeitiger Freigabe des rücklaufseitigen Anschlusses 36, so dass schon in der Übergangsphase der Druckabbau in der Druckkammer 28 beginnt, mit der Folge, das bei entsprechendem Öffnungsdruck auf die Druckschulter der Düsennadel der Einspritzdüse für diese eine schnelle Öffnung gewährleistet werden kann. Entsprechendes gilt in umgekehrter Richtung, wobei ungeachtet des herrschenden Druckes im Druckraum Stellkolben 29 und Gegenventilkörper 11 über die Feder 27 abgestützt sind, so dass der Gegenventilkörper 11 in seiner Anlagestellung zum Ventilkörper 10 gehalten wird. Wird der Magnetsteller 4 bestromt, so wird der Magnetanker 5 gegen die Feder 6 angehoben und der Steuerkolben 7 über die Feder 24 nachgeschoben, während in Gegenrichtung, bei abfallenden Magnetsteller 4, der Steuerkolben 7 über die Feder 6 entgegen der Kraft der Feder 24 verschoben wird. Die druckbeaufschlagten Flächen des Steuerkolbens 7 sind in der Umstellphase gleich groß, so dass mit vergleichsweise geringen Federkräften gearbeitet werden kann.For inflow and outflow relatively large cross sections can be realized in this solution, so that there are short switching times. Furthermore, in the transitional phase between the two switching positions of the control piston 7, a short circuit of the pressure chamber 28 to both the inlet - 30 - as well as the return port - given. If the injection valve is opened, this corresponds to energization of the magnet 4 and a shutdown of the supply side supply port 30 by displacement of the control piston 7 to its upper in the drawing sealing boundary formed by the control edge 18 and the sealing edge 14. In the course of this reversal of the inlet side Connection (supply port 30) increasingly diverted, with simultaneous release of the return side port 36, so that even in the transition phase of the pressure reduction in the pressure chamber 28 begins, with the result that at a corresponding opening pressure on the pressure shoulder of the nozzle needle of the injector for this a fast opening can be guaranteed. The same applies in the reverse direction, wherein regardless of the prevailing pressure in the pressure chamber actuator piston 29 and the counter valve body 11 are supported by the spring 27, so that the counter-valve body 11 is held in its contact position to the valve body 10. If the magnetic actuator 4 is energized, the armature 5 is raised against the spring 6 and the control piston 7 nachgeschoben via the spring 24, while in the opposite direction, with decreasing magnetic actuator 4, the control piston 7 is displaced against the spring 6 against the force of the spring 24 , The pressurized surfaces of the control piston 7 are the same size in the Umstellphase, so that you can work with comparatively low spring forces.

Konstruktiv ist die erfindungsgemäße Steuerventilkonstruktion so ausgelegt, dass sie auch fertigungstechnisch gut zu beherrschen ist, da Führungssitz und Anschlagflächen für den Ventilkörper 10 wie auch für den Gegenventilkörper 11 jeweils in einer Aufspannung geschliffen werden könnten, so dass enge Tolerierungen möglich sind. Entsprechendes gilt auch für den Steuerkolben bezüglich dessen Führungs- bzw. Zentrierflächen und Sitzflächen. Neben einer günstigen Fertigung ist somit auch eine hohe Präzision zu gewährleisten.Constructively, the control valve construction according to the invention is designed so that it is well manageable in terms of manufacturing technology, since the guide seat and stop surfaces for the Valve body 10 as well as for the counter valve body 11 could be ground in one clamping, so that close tolerances are possible. The same applies to the control piston with respect to its guiding or centering surfaces and seats. In addition to a low-cost production, therefore, a high precision is to be ensured.

Claims (23)

  1. Servocontrol valve which is combined with an actuating piston (29) of a fuel injector for internal combustion engines, in particular of diesel-operated or heavy-oil-operated internal combustion engines which operate with accumulator pressure injection, which servocontrol valve, as a pressure-equalized 3/2-way valve for a control piston (7) which is acted on via an axial actuating element (4), has a transversely divided valve guide insert (8) which is packaged in a housing and the dividing plane of which lies between the sealing edges (14, 15) of a radial valve chamber (16), with which control edges (18, 19) of the control piston (7) interact, and, of the parts (10, 11) of which, that part which is remote from the axial actuating element (4) is supported, as a corresponding valve body (11) which is guided on the control piston (7), with respect to the actuating piston (29) arranged behind it of the fuel injector (1) via a pressure space (28) which is supplied via the servovalve.
  2. Device according to Claim 1, characterized in that the control edges (18, 19) of the control piston (7) are assigned to an annular collar (17) of the control piston (7).
  3. Device according to Claim 2, characterized in that the annular collar (17) lies with its control edges (18, 19) in a radial overlap with respect to the sealing edges (14, 15) of the valve chamber (16), the sealing edge (14) of the said valve chamber (16) which lies opposite the corresponding valve body (11) being assigned, as a part of the valve guide insert (8), to the valve body (10) which forms the guide for the control piston (7).
  4. Device according to one of the preceding claims, characterized in that the corresponding valve body (11) and the valve body (10) are supported axially against one another.
  5. Device according to Claim 4, characterized in that the corresponding valve body (11) and the valve body (10) are supported axially against one another in the dividing plane.
  6. Device according to Claim 4 or 5, characterized in that the corresponding valve body (11) and the valve body (10) are supported against one another in a manner which forms a gap.
  7. Device according to one of Claims 4 to 6, characterized in that the corresponding valve body (11) and the valve body (10) are supported against one another via spacer elements.
  8. Device according to one of the preceding claims, characterized in that the annular collar (17) of the control piston (7) lies between radially drawn-in annular regions which form first (20) and second (21) annular spaces with respect to the valve guide insert.
  9. Device according to Claim 8, characterized in that, as a function of the position of the control piston (7), the first annular space (20) is connected to a connection which opens into the valve chamber (16).
  10. Device according to one of the preceding claims, characterized in that that end of the control piston (7) which dips into the corresponding valve body (11) is configured as a guide collar (22) for the corresponding valve body (11).
  11. Device according to Claim 10, characterized in that the guide collar (22) forms a boundary of the second annular space (21) with respect to the adjacent control edge (19) of the control piston (7).
  12. Device according to Claim 10 or 11, characterized in that the guide collar (22) is configured as a centring lip.
  13. Device according to one of Claims 8 to 12, characterized in that the first annular space (21) which is assigned to the corresponding valve body (11) is connected to an axial channel (25) which penetrates the control piston (7).
  14. Device according to Claim 13, characterized in that the connection to the axial channel (25) takes place via a radial channel (33).
  15. Device according to Claim 13, characterized in that the first annular space (21) is connected to the axial channel (25) via the end side of the control piston (7).
  16. Device according to one of the preceding claims, characterized in that the actuating piston (29) is supported in a sprung manner against the corresponding valve body (11), in a manner which bridges the pressure space.
  17. Device according to one of the preceding claims, characterized in that the control piston (7) is supported in a sprung manner against the corresponding valve body (11).
  18. Device according to one of the preceding claims, characterized in that the axial actuating element (4) is loaded in the direction of the control piston (7) in a sprung manner.
  19. Device according to one of the preceding claims, characterized in that the axial actuating element (4) is configured as a magnet actuating element, the armature (5) of which is spring-loaded in the direction of the control piston (7).
  20. Device according to Claim 19, characterized in that the actuating force of the spring support between the actuating piston (29) and the corresponding valve body (11) is greater than the spring force which acts on the magnet armature (5) .
  21. Device according to Claim 19 or 20, characterized in that the spring force of the spring (6) which loads the magnet armature (5) against the control piston (7) is greater than that of the spring arrangement (24) which is arranged between the corresponding valve body (11) and the control piston (7) and supports the control piston (7) in the opposite direction.
  22. Device according to one of Claims 16 to 21, characterized in that the springs (6; 24; 27) are arranged coaxially.
  23. Device according to one of Claims 16 to 22, characterized in that the springs (6; 24; 27) are configured as compression springs.
EP01967354A 2000-09-20 2001-09-19 Servo control valve for injectors Expired - Lifetime EP1319125B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10046823 2000-09-20
DE10046823A DE10046823B4 (en) 2000-09-20 2000-09-20 Servo control valve for injection injectors
PCT/EP2001/010817 WO2002027178A1 (en) 2000-09-20 2001-09-19 Servo control valve for injectors

Publications (2)

Publication Number Publication Date
EP1319125A1 EP1319125A1 (en) 2003-06-18
EP1319125B1 true EP1319125B1 (en) 2006-04-05

Family

ID=7657122

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01967354A Expired - Lifetime EP1319125B1 (en) 2000-09-20 2001-09-19 Servo control valve for injectors

Country Status (6)

Country Link
EP (1) EP1319125B1 (en)
JP (1) JP3768191B2 (en)
KR (1) KR100621270B1 (en)
AT (1) ATE322616T1 (en)
DE (2) DE10046823B4 (en)
WO (1) WO2002027178A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2604353A (en) * 2021-03-02 2022-09-07 Delphi Tech Ip Ltd Improved Injector

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19742073A1 (en) * 1997-09-24 1999-03-25 Bosch Gmbh Robert Fuel injection arrangement for internal combustion engines
DE19816316A1 (en) * 1998-04-11 1999-10-14 Bosch Gmbh Robert Fuel injection device for internal combustion engines
GB9823134D0 (en) * 1998-10-23 1998-12-16 Lucas Ind Plc Valve
DE19941709A1 (en) * 1999-09-02 2001-03-15 Bosch Gmbh Robert Built control valve for an injector of a fuel injection system for internal combustion engines

Also Published As

Publication number Publication date
WO2002027178A1 (en) 2002-04-04
DE50109450D1 (en) 2006-05-18
DE10046823B4 (en) 2004-07-15
ATE322616T1 (en) 2006-04-15
KR20030036808A (en) 2003-05-09
DE10046823A1 (en) 2002-04-04
JP2004510098A (en) 2004-04-02
KR100621270B1 (en) 2006-09-13
EP1319125A1 (en) 2003-06-18
JP3768191B2 (en) 2006-04-19

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