EP2218906A1 - Fuel injector - Google Patents

Fuel injector Download PDF

Info

Publication number
EP2218906A1
EP2218906A1 EP09180310A EP09180310A EP2218906A1 EP 2218906 A1 EP2218906 A1 EP 2218906A1 EP 09180310 A EP09180310 A EP 09180310A EP 09180310 A EP09180310 A EP 09180310A EP 2218906 A1 EP2218906 A1 EP 2218906A1
Authority
EP
European Patent Office
Prior art keywords
sleeve
coupler
fuel injector
spring element
valve piston
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.)
Granted
Application number
EP09180310A
Other languages
German (de)
French (fr)
Other versions
EP2218906B1 (en
Inventor
Andreas Gruenberger
Martin Kiontke
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2218906A1 publication Critical patent/EP2218906A1/en
Application granted granted Critical
Publication of EP2218906B1 publication Critical patent/EP2218906B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • Such fuel injectors are known from the prior art.
  • the publication DE 10 2006 042 601 A1 discloses an injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member for releasing or closing at least one injection port is driven by an actuator-operated control valve.
  • a hydraulic coupler unit is arranged, which in the example known from the prior art comprises a first piston operatively connected to the actuator with a first diameter and a second piston with a second, smaller diameter, so that corresponding to the diameter ratio the two pistons of the stroke of the actuator for controlling the control valve is translated hydraulically.
  • Both pistons are guided in a coupler body, which in turn is surrounded by a spring sleeve for axially biasing the first piston relative to the actuator.
  • the second piston is biased axially relative to the control valve via a coil spring which is supported on the coupler body.
  • a arranged between the actuator and the first piston shim serves to compensate for production-related length tolerances.
  • a fuel injector of the type described above has a certain overall construction length due to its complex structure. He may therefore not be used in all internal combustion engines. There is therefore a general interest in reducing the overall construction length of a fuel injector.
  • Object of the present invention is to provide such a length-optimized fuel injector with a hydraulic coupler unit, which is also easy and inexpensive to manufacture.
  • the proposed fuel injector comprises an actuator unit and a hydraulic coupler unit, which communicates via an adjusting piece with the actuator unit.
  • the hydraulic coupler unit comprises an axially displaceably guided and biased by a first spring element valve piston and according to the invention further comprises a coupler sleeve which is biased by a second spring element against the setting piece and limited together with the valve piston and the adjusting piece a pressure chamber.
  • the hydraulic coupler unit of the fuel injector according to the invention has only one piston. In the absence of a second piston and a coupler gap formed between the pistons, the pressure space formed between the valve piston, the adjusting piece and the coupler sleeve serves as a hydraulic coupler.
  • the fuel injector according to the invention therefore preferably has one pressure balanced control valve, whose operation is essentially independent of system pressure and thus requires a lower pressure force.
  • the control valve may, for example, be pressure balanced in that the valve closure member of the control valve is guided in a sleeve, wherein valve closure member and sleeve define a pressure chamber, which is always depressurized.
  • a pressure balanced control valve is the subject of another application of the same applicant and should therefore not be further explored in the context of this application.
  • the overall length of the hydraulic coupler unit and thus the total length of the fuel injector according to the invention can be significantly reduced.
  • an extension of the valve piston may be required to compensate for the omitted second piston, but even then length reductions of the coupler unit to about 6.5 mm are possible.
  • a highly accurate guide for example in the form of a coupler body, is dispensed with. This contributes to the simplification of the hydraulic coupler unit and thus to the cost-effective production of the fuel injector.
  • the fuel injector according to the invention can be dispensed with the arrangement of a shim for adjusting the spring force of the spring sleeve and thus to compensate for length tolerances, since on the one hand, the incoming in the spring force tolerances are reduced, on the other hand, the spring force is no longer dependent on tolerances collar heights , As a result, the structure of a fuel injector according to the invention is further simplified and the costs optimized.
  • the coupler gap that is, the pressure space between the coupler sleeve, the adjusting piece and the valve piston, which is provided on the adjusting piece sealingly fitting surface of the coupler sleeve with a biting edge.
  • the required surface pressure is effected by the second spring element, which acts on the coupler sleeve in the axial direction with a compressive force and thus holds in sealing contact with the setting piece.
  • the coupler sleeve on the inner peripheral side has a circumferential radial shoulder, with which the coupler sleeve bears sealingly on the adjusting piece.
  • the radial shoulder is provided with a biting edge.
  • the adjoining the radial shoulder region preferably has an inner diameter which is slightly larger than the outer diameter of the adjusting piece, so that the guided over the adjusting coupler sleeve undergoes a centering.
  • the coupler sleeve has a radially outwardly guided collar for supporting the second spring element, wherein the second spring element is preferably a spring sleeve. While one end of the second spring element is supported on the collar of the coupler sleeve, the other end is preferably located on a valve plate receiving the control valve.
  • the distance between the collar surface and the biting edge of the coupler sleeve is the only measure influencing the spring force of the second spring element. Since the influence is minimal, the adjusting disk already mentioned in connection with the prior art can be omitted for adjusting the spring force. Thus, the complex adjustment process itself is unnecessary. By this measure, not only simplifies the construction of the hydraulic coupler unit, but allows by dispensing with a dial another Reduction in the length of the coupler unit and thus the total length of the fuel injector.
  • the guide gap between coupler sleeve and valve piston is less than 10 microns, preferably less than 5 microns. This ensures a highly accurate guidance of the valve piston via the coupler sleeve. Since the coupler sleeve is preferably designed such that it comprises only a portion of the valve piston, namely the end facing the adjusting piece, further measures can be taken to guide the other, the control valve facing the end of the valve piston.
  • the control valve receiving valve plate may be formed with a serving as a guide collar. However, the formation of the valve plate with a collar requires a higher manufacturing effort. Subsequently, alternative measures are shown.
  • valve piston for example, by the spring force acting in the axial direction of the first spring element, by means of which the valve piston is biased against the closing element of the control valve.
  • first spring element is supported on the one hand on the coupler sleeve, on the other hand on the valve piston.
  • the valve piston is equipped with a collar sleeve, on the radially extending collar surface, the coil spring is supported.
  • the first spring element is a helical spring.
  • the hydraulic coupler unit may comprise a centering sleeve for centering the coupler sleeve and / or the valve piston. If the valve piston experiences centering via the centering sleeve, it also experiences a guide, since the valve piston is preferably arranged to be axially movable relative to the centering sleeve.
  • the centering sleeve can be arranged for example instead of a collar on the upper side of the valve plate.
  • the valve plate can for receiving and fixing the position of the centering, at least in the radial direction, further have a concentric bore into which the centering sleeve is inserted.
  • the centering sleeve extends from the valve plate to the coupler sleeve or beyond, so that primarily the coupler sleeve and indirectly via the coupler sleeve of the valve piston undergoes a centering or guiding.
  • the centering sleeve preferably has on the inner peripheral side a circumferential radial shoulder on which the first spring element is supported. To form such a shoulder, the centering sleeve may for example have sections with different inner diameters.
  • the centering sleeve On the outer circumference side, the centering sleeve preferably has a cylindrical lateral surface.
  • hydraulic coupler unit 3 comprises two guided in a coupler body 20 piston, a valve piston 7 having a first diameter D 1 and a Coupler piston 22 having a second diameter D 2 , wherein D 1 ⁇ D 2 , so that according to the diameter ratio, a translation of the force and the stroke of an actuator 1 via a formed between the two pistons 7, 22 coupler gap 23, which is provided with a hydraulic fluid is filled.
  • the coupler body 20 serves to guide the two pistons 7, 22 and is therefore adapted to the inner circumference of the respective piston diameters. With a radially extending collar surface of the coupler body rests against a valve plate 16, in which a control valve 2 is received.
  • the valve seat facing away end is guided in a sleeve 19 and limited together with the sleeve 19 and the valve plate 16, a low-pressure space 24, so that guided in the sleeve 19 portion of the closing element 6 of the control valve 2 is not acted upon by the system pressure.
  • a compressive force is required, which essentially corresponds to the spring force of a helical spring 18, by means of which the closing element 6 is biased relative to the valve seat 25.
  • the coil spring 18 is supported on the one hand on the sleeve 19, on the other hand on a spring collar 17 of the closing element 6.
  • the valve piston 7 is also biased by a coil spring against the closing element 6.
  • the helical spring is for this purpose supported on the valve piston 7 and on an inner peripheral side radially extending shoulder of the coupler body.
  • a second spring element 9 is provided in the form of a spring sleeve, by means of which the coupler piston 22 is biased against an adjusting piece 4 and thus relative to the actuator unit 1.
  • the spring sleeve is supported on the one hand on a radially extending collar surface of the coupler body 20, on the other hand on a shim 21, which in turn rests against a circumferential radial collar surface of the coupler piston 22.
  • the shim 21 serves to adjust the spring force since the different collar heights of the coupler body 20 and the coupler piston 22 are subject to tolerances.
  • the hydraulic coupler unit 3 of a fuel injector according to the invention has only one valve piston 7 (see FIG Fig. 2 and 3 ).
  • the arrangement of a second piston 22 and a coupler body 20 according to the example described above is deliberately omitted.
  • the translation is thus in the ratio 1: 1.
  • the control valve 2 is in turn pressure balanced, because the closing member 6 of the control valve 2 is guided in a sleeve 19, which define a low pressure space 24 together with the valve plate 16, an amplification of the actuator force or deshubes is not required.
  • a coupler gap 23 is now formed between a valve piston 7 and 4 setting piece pressure chamber 10 which is bounded radially by a coupler sleeve 8.
  • the valve piston 7 is movably guided.
  • the guide gap 13 is designed with only a small clearance and in the present example is about 4 ⁇ m.
  • the coupler sleeve 8 is further provided with a biting edge with which the coupler sleeve 8 rests sealingly on the adjusting piece 4.
  • the necessary surface pressure is effected by a second spring element 9, by means of which the coupler sleeve 8 is biased against the adjusting piece 4.
  • the second spring element 9 is also in this example a spring sleeve which is supported on the one hand directly to the valve plate 16, on the other hand to the coupler sleeve 8.
  • the coupler sleeve 8 has for this purpose a collar 12 with a radially extending collar surface. The distance between this collar surface and the adjoining adjoining 4 biting edge is the only tolerant degree that affects the spring force. Since the influence is minimal, a dial 21 has also been dispensed with in the case of the hydraulic coupler unit 3 according to the invention. By waiving one Second piston 22 and a shim 21, the length of the coupler unit 3 according to the embodiment of Fig. 2 by 4.5 mm compared to the known design accordingly Fig. 1 be shortened.
  • the hydraulic coupler unit 3 of the Fig. 2 a centering sleeve 14 for centering the coupler sleeve 8 and thus indirectly for centering and guiding the valve piston 7.
  • the hydraulic coupler unit 3 of the Fig. 1 also has the centering sleeve 14 of the hydraulic coupler unit 3 of Fig. 2 an inner peripheral side radially extending shoulder 15, on which one end of the first spring element 5 is supported, by means of which the valve piston 7 is biased against the closing element 6 of the control valve 2.
  • a further centering of the coupler sleeve 8 and thus indirectly also of the valve piston 7 takes place in that the adjusting piece 4 is at least partially embedded in an inner peripheral side recess of the coupler sleeve so that it rests against an inner peripheral side radially extending shoulder 11 of the coupler sleeve 8.
  • the centering sleeve can also be reduced to an annular body, which surrounds only the valve piston 7 in the region of the valve plate 16 and this centered as a result or leads.
  • the first spring element 5 has an axial position, so that it is supported on one side on the coupler sleeve 8.
  • the embodiment differs Fig. 3 not from the Fig. 2 , However, the reduction of the centering sleeve 14 allows an applied to the valve piston 7 annular body a reduction in length of the coupler unit 3 of up to 6.5 mm.
  • valve plate 16 can also be equipped with a collar or shoulder which allows axial guidance of the valve piston 7.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The injector has an actuator unit (1) for operating a control valve (2), and a hydraulic coupler unit (3) connected with the actuator unit by a setting piece (4). A valve piston (7) is pre-stressed against a closing element (6) of the control valve by a spring element (5). The hydraulic coupler unit comprises a coupler sleeve (8) that is pre-stressed against the setting piece by another spring element (9). The coupler sleeve limits a pressure chamber (10) with the valve piston and the setting piece, where the former spring element is designed as a coil spring.

Description

Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.

Derartige Kraftstoffinjektoren sind aus dem Stand der Technik bekannt. Die Druckschrift DE 10 2006 042 601 A1 beispielsweise offenbart einen Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine, bei dem ein Einspritzventilglied zum Freigeben oder Verschließen wenigstens einer Einspritzöffnung durch ein aktorbetätigtes Steuerventil angesteuert wird. Zwischen Aktor und Steuerventil ist eine hydraulische Kopplereinheit angeordnet, die bei dem aus dem Stand der Technik bekannten Beispiel einen mit dem Aktor in Wirkverbindung stehenden ersten Kolben mit einem ersten Durchmesser und einen zweiten Kolben mit einem zweiten, geringeren Durchmesser umfasst, so dass entsprechend dem Durchmesserverhältnis der beiden Kolben der Hub des Aktors zur Steuerung des Steuerventils hydraulisch übersetzt wird. Beide Kolben sind in einem Kopplerkörper geführt, der wiederum von einer Federhülse zur axialen Vorspannung des ersten Kolbens gegenüber dem Aktor umgeben ist. Der zweite Kolben wird über eine Schraubenfeder, die am Kopplerkörper abgestützt ist, gegenüber dem Steuerventil axial vorgespannt. Eine zwischen dem Aktor und dem erstem Kolben angeordnete Einstellscheibe dient dem Ausgleich von fertigungsbedingten Längentoleranzen.Such fuel injectors are known from the prior art. The publication DE 10 2006 042 601 A1 For example, discloses an injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member for releasing or closing at least one injection port is driven by an actuator-operated control valve. Between the actuator and the control valve, a hydraulic coupler unit is arranged, which in the example known from the prior art comprises a first piston operatively connected to the actuator with a first diameter and a second piston with a second, smaller diameter, so that corresponding to the diameter ratio the two pistons of the stroke of the actuator for controlling the control valve is translated hydraulically. Both pistons are guided in a coupler body, which in turn is surrounded by a spring sleeve for axially biasing the first piston relative to the actuator. The second piston is biased axially relative to the control valve via a coil spring which is supported on the coupler body. A arranged between the actuator and the first piston shim serves to compensate for production-related length tolerances.

Ein Kraftstoffinjektor der vorstehend beschriebenen Art besitzt aufgrund seines komplexen Aufbaus eine bestimmte Gesamtbaulänge. Er ist damit gegebenenfalls nicht in allen Brennkraftmaschinen einsetzbar. Es besteht daher ein allgemeines Interesse, die Gesamtbaulänge eines Kraftstoffinjektors zu reduzieren.A fuel injector of the type described above has a certain overall construction length due to its complex structure. He may therefore not be used in all internal combustion engines. There is therefore a general interest in reducing the overall construction length of a fuel injector.

Aufgabe der vorliegenden Erfindung ist es, einen solchen längenoptimierten Kraftstoffinjektor mit einer hydraulischen Kopplereinheit anzugeben, der zugleich einfach und kostengünstig herzustellen ist.Object of the present invention is to provide such a length-optimized fuel injector with a hydraulic coupler unit, which is also easy and inexpensive to manufacture.

Zur Lösung der Aufgabe wird ein Kraftstoffinjektor mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Erfindungen sind in den Unteransprüchen angegeben.To solve the problem, a fuel injector with the features of claim 1 is proposed. Advantageous developments of the inventions are specified in the subclaims.

Der vorgeschlagene Kraftstoffinjektor umfasst eine Aktor-Einheit und eine hydraulische Kopplereinheit, die über ein Einstellstück mit der Aktor-Einheit in Verbindung steht. Die hydraulische Kopplereinheit umfasst einen axial verschiebbar geführten und mittels eines ersten Federelementes vorgespannten Ventilkolben und erfindungsgemäß ferner eine Kopplerhülse, die mittels eines zweiten Federelementes gegen das Einstellstück vorgespannt ist und gemeinsam mit dem Ventilkolben und dem Einstellstück einen Druckraum begrenzt. Im Unterschied zur hydraulischen Kopplereinheit des eingangs beschriebenen und aus dem Stand der Technik bekannten Injektors weist die hydraulische Kopplereinheit des erfindungsgemäßen Kraftstoffinjektors lediglich einen Kolben auf. In Ermangelung eines zweiten Kolbens und eines zwischen den Kolben ausgebildeten Kopplerspaltes dient der zwischen Ventilkolben, Einstellstück und Kopplerhülse ausgebildete Druckraum als hydraulischer Koppler. Die Übersetzung erfolgt im Verhältnis 1:1, das heißt es findet keine Verstärkung des Aktorhubes statt. Bevorzugt weist der erfindungsgemäße Kraftstoffinjektor daher ein druckausgeglichenes Steuerventil auf, dessen Betätigung im Wesentlichen systemdruckunabhängig erfolgt und somit eine geringere Druckkraft erfordert. Das Steuerventil kann beispielsweise dadurch druckausgeglichen sein, dass das Ventilschließglied des Steuerventils in einer Hülse geführt ist, wobei Ventilschließglied und Hülse einen Druckraum begrenzen, der stets druckentlastet ist. Ein druckausgeglichenes Steuerventil ist Gegenstand einer anderen Anmeldung derselben Anmelderin und soll daher im Rahmen dieser Anmeldung nicht weiter vertieft werden.The proposed fuel injector comprises an actuator unit and a hydraulic coupler unit, which communicates via an adjusting piece with the actuator unit. The hydraulic coupler unit comprises an axially displaceably guided and biased by a first spring element valve piston and according to the invention further comprises a coupler sleeve which is biased by a second spring element against the setting piece and limited together with the valve piston and the adjusting piece a pressure chamber. In contrast to the hydraulic coupler unit of the injector described above and known from the prior art, the hydraulic coupler unit of the fuel injector according to the invention has only one piston. In the absence of a second piston and a coupler gap formed between the pistons, the pressure space formed between the valve piston, the adjusting piece and the coupler sleeve serves as a hydraulic coupler. The translation takes place in a ratio of 1: 1, that is, there is no reinforcement of Aktorhubes instead. The fuel injector according to the invention therefore preferably has one pressure balanced control valve, whose operation is essentially independent of system pressure and thus requires a lower pressure force. The control valve may, for example, be pressure balanced in that the valve closure member of the control valve is guided in a sleeve, wherein valve closure member and sleeve define a pressure chamber, which is always depressurized. A pressure balanced control valve is the subject of another application of the same applicant and should therefore not be further explored in the context of this application.

Indem auf die Anordnung eines zweiten Kolbens verzichtet wird, kann die Baulänge der hydraulischen Kopplereinheit und damit die Gesamtlänge des erfindungsgemäßen Kraftstoffinjektors deutlich reduziert werden. Gegebenenfalls kann zur Kompensation des entfallenen zweiten Kolbens eine Verlängerung des Ventilkolbens erforderlich sein, doch selbst dann sind Längenreduzierungen der Kopplereinheit bis etwa 6,5 mm möglich.By dispensing with the arrangement of a second piston, the overall length of the hydraulic coupler unit and thus the total length of the fuel injector according to the invention can be significantly reduced. Optionally, an extension of the valve piston may be required to compensate for the omitted second piston, but even then length reductions of the coupler unit to about 6.5 mm are possible.

Des Weiteren wird bei dem erfindungsgemäßen Kraftstoffinjektor im Unterschied zu dem eingangs beschriebenen und aus dem Stand der Technik bekannten Injektor auf eine hochgenaue Führung, beispielsweise in Form eines Kopplerkörpers, verzichtet. Dies trägt zur Vereinfachung der hydraulischen Kopplereinheit und damit zur kostengünstigen Herstellung des Kraftstoffinjektors bei. Darüber hinaus kann bei dem erfindungsgemäßen Kraftstoffinjektor auf die Anordnung einer Einstellscheibe zur Einstellung der Federkraft der Federhülse und damit zum Ausgleich von Längentoleranzen verzichtet werden, da zum Einen die in die Federkrafttoleranzen eingehenden Maße reduziert werden, zum Anderen die Federkraft nicht mehr von toleranzbehafteten Bundhöhen abhängig ist. Dadurch wird der Aufbau eines erfindungsgemäßen Kraftstoffinjektors weiter vereinfacht und die Kosten optimiert.Furthermore, in the fuel injector according to the invention, in contrast to the injector described above and known from the prior art, a highly accurate guide, for example in the form of a coupler body, is dispensed with. This contributes to the simplification of the hydraulic coupler unit and thus to the cost-effective production of the fuel injector. In addition, in the fuel injector according to the invention can be dispensed with the arrangement of a shim for adjusting the spring force of the spring sleeve and thus to compensate for length tolerances, since on the one hand, the incoming in the spring force tolerances are reduced, on the other hand, the spring force is no longer dependent on tolerances collar heights , As a result, the structure of a fuel injector according to the invention is further simplified and the costs optimized.

Nach einer bevorzugten Ausführungsform ist zur Abdichtung des Kopplerspaltes, das heißt des Druckraumes zwischen der Kopplerhülse, dem Einstellstück und dem Ventilkolben, die an dem Einstellstück dichtend anliegende Fläche der Kopplerhülse mit einer Beißkante versehen. Die erforderliche Flächenpressung wird durch das zweite Federelement bewirkt, das die Kopplerhülse in Axialrichtung mit einer Druckkraft beaufschlagt und somit in dichtender Anlage mit dem Einstellstück hält.According to a preferred embodiment, for sealing the coupler gap, that is, the pressure space between the coupler sleeve, the adjusting piece and the valve piston, which is provided on the adjusting piece sealingly fitting surface of the coupler sleeve with a biting edge. The required surface pressure is effected by the second spring element, which acts on the coupler sleeve in the axial direction with a compressive force and thus holds in sealing contact with the setting piece.

Nach einer weiteren bevorzugten Ausführungsform besitzt die Kopplerhülse innenumfangsseitig einen umlaufenden radialen Absatz, mit dem die Kopplerhülse dichtend am Einstellstück anliegt. Bevorzugt ist daher der radiale Absatz mit einer Beißkante versehen. Der sich an den radialen Absatz anschließende Bereich weist vorzugsweise einen Innendurchmesser auf, der geringfügig größer als der Außendurchmesser des Einstellstückes ist, so dass die über das Einstellstück geführte Kopplerhülse eine Zentrierung erfährt.According to a further preferred embodiment, the coupler sleeve on the inner peripheral side has a circumferential radial shoulder, with which the coupler sleeve bears sealingly on the adjusting piece. Preferably, therefore, the radial shoulder is provided with a biting edge. The adjoining the radial shoulder region preferably has an inner diameter which is slightly larger than the outer diameter of the adjusting piece, so that the guided over the adjusting coupler sleeve undergoes a centering.

Weiterhin bevorzugt besitzt die Kopplerhülse einen nach radial außen geführten Bund zur Auflage des zweiten Federelementes, wobei das zweite Federelement vorzugsweise eine Federhülse ist. Während das eine Ende des zweiten Federelementes am Bund der Kopplerhülse abgestützt ist, liegt das andere Ende bevorzugt an einer das Steuerventil aufnehmenden Ventilplatte auf. Damit stellt der Abstand zwischen Bundfläche und Beißkante der Kopplerhülse das einzige die Federkraft des zweiten Federelementes beeinflussende Maß dar. Da der Einfluss minimal ist, kann die im Zusammenhang mit dem Stand der Technik bereits erwähnte Einstellscheibe zur Einstellung der Federkraft entfallen. Damit ist auch der aufwendige Einstellprozess selbst entbehrlich. Durch diese Maßnahme vereinfacht sich nicht nur der Aufbau der hydraulischen Kopplereinheit, sondern ermöglicht durch den Verzicht auf eine Einstellscheibe eine weitere Reduzierung der Baulänge der Kopplereinheit und damit der Gesamtlänge des Kraftstoffinjektors.Further preferably, the coupler sleeve has a radially outwardly guided collar for supporting the second spring element, wherein the second spring element is preferably a spring sleeve. While one end of the second spring element is supported on the collar of the coupler sleeve, the other end is preferably located on a valve plate receiving the control valve. Thus, the distance between the collar surface and the biting edge of the coupler sleeve is the only measure influencing the spring force of the second spring element. Since the influence is minimal, the adjusting disk already mentioned in connection with the prior art can be omitted for adjusting the spring force. Thus, the complex adjustment process itself is unnecessary. By this measure, not only simplifies the construction of the hydraulic coupler unit, but allows by dispensing with a dial another Reduction in the length of the coupler unit and thus the total length of the fuel injector.

Vorteilhafterweise beträgt der Führungsspalt zwischen Kopplerhülse und Ventilkolben weniger als 10 µm, vorzugsweise weniger als 5 µm. Dadurch ist eine hochgenaue Führung des Ventilkolbens über die Kopplerhülse sichergestellt. Da die Kopplerhülse vorzugsweise derart ausgebildet ist, dass sie lediglich einen Abschnitt des Ventilkolbens umfasst, und zwar das dem Einstellstück zugewandte Ende, können zur Führung des anderen, dem Steuerventil zugewandten Endes des Ventilkolbens weitere Maßnahmen getroffen werden. Beispielsweise kann die das Steuerventil aufnehmende Ventilplatte mit einem als Führung dienenden Kragen ausgebildet sein. Allerdings erfordert die Ausbildung der Ventilplatte mit einem Kragen einen höheren fertigungstechnischen Aufwand. Nachfolgend werden daher alternative Maßnahmen aufgezeigt.Advantageously, the guide gap between coupler sleeve and valve piston is less than 10 microns, preferably less than 5 microns. This ensures a highly accurate guidance of the valve piston via the coupler sleeve. Since the coupler sleeve is preferably designed such that it comprises only a portion of the valve piston, namely the end facing the adjusting piece, further measures can be taken to guide the other, the control valve facing the end of the valve piston. For example, the control valve receiving valve plate may be formed with a serving as a guide collar. However, the formation of the valve plate with a collar requires a higher manufacturing effort. Subsequently, alternative measures are shown.

Eine gewisse Führung erfährt der Ventilkolben beispielsweise durch die in Axialrichtung wirkende Federkraft des ersten Federelementes, mittels dessen der Ventilkolben gegenüber dem Schließelement des Steuerventils vorgespannt ist. Hierzu ist vorzugsweise das erste Federelement einerseits an der Kopplerhülse, andererseits am Ventilkolben abgestützt. Vorteilhafterweise ist der Ventilkolben mit einer Bundhülse ausgestattet, an deren radial verlaufenden Bundfläche die Schraubenfeder abgestützt ist. Weiterhin vorzugsweise ist das erste Federelement eine Schraubenfeder.A certain guidance experiences the valve piston, for example, by the spring force acting in the axial direction of the first spring element, by means of which the valve piston is biased against the closing element of the control valve. For this purpose, preferably the first spring element is supported on the one hand on the coupler sleeve, on the other hand on the valve piston. Advantageously, the valve piston is equipped with a collar sleeve, on the radially extending collar surface, the coil spring is supported. Further preferably, the first spring element is a helical spring.

Des Weiteren kann die hydraulische Kopplereinheit eine Zentrierhülse zur Zentrierung der Kopplerhülse und/oder des Ventilkolbens umfassen. Sofern der Ventilkolben über die Zentrierhülse eine Zentrierung erfährt, erfährt er auch eine Führung, da der Ventilkolben gegenüber der Zentrierhülse bevorzugt axial beweglich angeordnet ist. Die Zentrierhülse kann beispielsweise anstelle eines Kragens an der Oberseite der Ventilplatte angeordnet sein. Die Ventilplatte kann zur Aufnahme und Lagefixierung der Zentrierhülse, zumindest in radialer Richtung, ferner eine konzentrische Bohrung besitzen, in welche die Zentrierhülse eingesetzt ist.Furthermore, the hydraulic coupler unit may comprise a centering sleeve for centering the coupler sleeve and / or the valve piston. If the valve piston experiences centering via the centering sleeve, it also experiences a guide, since the valve piston is preferably arranged to be axially movable relative to the centering sleeve. The centering sleeve can be arranged for example instead of a collar on the upper side of the valve plate. The valve plate can for receiving and fixing the position of the centering, at least in the radial direction, further have a concentric bore into which the centering sleeve is inserted.

Nach einer ersten bevorzugten Ausführungsform erstreckt sich die Zentrierhülse von der Ventilplatte bis zur Kopplerhülse bzw. darüber hinaus, so dass vorrangig die Kopplerhülse und mittelbar über die Kopplerhülse der Ventilkolben eine Zentrierung bzw. Führung erfährt. Die Zentrierhülse besitzt vorzugsweise innenumfangseitig einen umlaufenden radialen Absatz, an dem das erste Federelement abgestützt ist. Zur Ausbildung eines solchen Absatzes kann die Zentrierhülse beispielsweise Abschnitte mit unterschiedlichen Innendurchmessern aufweisen. Außenumfangseitig weist die Zentrierhülse bevorzugt eine zylindrische Mantelfläche auf.According to a first preferred embodiment, the centering sleeve extends from the valve plate to the coupler sleeve or beyond, so that primarily the coupler sleeve and indirectly via the coupler sleeve of the valve piston undergoes a centering or guiding. The centering sleeve preferably has on the inner peripheral side a circumferential radial shoulder on which the first spring element is supported. To form such a shoulder, the centering sleeve may for example have sections with different inner diameters. On the outer circumference side, the centering sleeve preferably has a cylindrical lateral surface.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1 einen Längsschnitt durch die hydraulische Kopplereinheit eines aus dem Stand der Technik bekannten Kraftstoffinjektors,
  • Fig. 2 einen Längsschnitt durch die hydraulische Kopplereinheit einer ersten Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors und
  • Fig. 3 einen Längsschnitt durch die hydraulische Kopplereinheit einer zweiten Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors.
Preferred embodiments of the invention are explained below with reference to the drawings. Show it:
  • Fig. 1 a longitudinal section through the hydraulic coupler unit of a known from the prior art fuel injector,
  • Fig. 2 a longitudinal section through the hydraulic coupler unit of a first embodiment of a fuel injector according to the invention and
  • Fig. 3 a longitudinal section through the hydraulic coupler unit of a second embodiment of a fuel injector according to the invention.

Die in Fig. 1 dargestellte hydraulische Kopplereinheit 3 umfasst zwei in einem Kopplerkörper 20 geführte Kolben, einen Ventilkolben 7 mit einem ersten Durchmesser D1 und einen Kopplerkolben 22 mit einem zweiten Durchmesser D2, wobei D1 < D2 ist, so dass entsprechend dem Durchmesserverhältnis eine Übersetzung der Kraft und des Hubes eines Aktors 1 über einen zwischen den beiden Kolben 7, 22 ausgebildeten Kopplerspalt 23 erfolgt, der mit einer Hydraulikflüssigkeit gefüllt ist. Der Kopplerkörper 20 dient der Führung der beiden Kolben 7, 22 und ist daher innenumfangseitig den jeweiligen Kolbendurchmessern angepasst. Mit einer radial verlaufenden Bundfläche liegt der Kopplerkörper an einer Ventilplatte 16 an, in der ein Steuerventil 2 aufgenommen ist. Vorliegend handelt es sich um ein druckausgeglichenes Steuerventil 2, mit einem Schließelement 6, dessen ventilsitzabgewandtes Ende in einer Hülse 19 geführt ist und gemeinsam mit der Hülse 19 und der Ventilplatte 16 einen Niederdruckraum 24 begrenzt, so dass der in der Hülse 19 geführte Abschnitt des Schließelementes 6 des Steuerventils 2 nicht vom Systemdruck beaufschlagt wird. Zur Betätigung des Steuerventils 2 ist daher lediglich eine Druckkraft erforderlich, die im Wesentlichen der Federkraft einer Schraubenfeder 18 entspricht, mittels derer das Schließelement 6 gegenüber dem Ventilsitz 25 vorgespannt ist. Hierzu ist die Schraubenfeder 18 einerseits an der Hülse 19, andererseits an einem Federkragen 17 des Schließelementes 6 abgestützt. Der Ventilkolben 7 ist ebenfalls mittels einer Schraubenfeder gegenüber dem Schließelement 6 vorgespannt. Die Schraubenfeder ist hierzu an dem Ventilkolben 7 und an einem innenumfangseitig radial verlaufenden Absatz des Kopplerkörpers abgestützt. Neben der Schraubenfeder als erstem Federelement 5 ist ein zweites Federelement 9 in Form einer Federhülse vorgesehen, mittels derer Kopplerkolben 22 gegenüber einem Einstellstück 4 und damit gegenüber der Aktor-Einheit 1 vorgespannt ist. Die Federhülse ist einerseits an einer radial verlaufenden Bundfläche des Kopplerkörpers 20, andererseits an einer Einstellscheibe 21 abgestützt, die wiederum an einer umlaufenden radialen Bundfläche des Kopplerkolbens 22 anliegt. Die Einstellscheibe 21 dient der Einstellung der Federkraft, da die verschiedenen Bundhöhen des Kopplerkörpers 20 und des Kopplerkolbens 22 toleranzbehaftet sind.In the Fig. 1 shown hydraulic coupler unit 3 comprises two guided in a coupler body 20 piston, a valve piston 7 having a first diameter D 1 and a Coupler piston 22 having a second diameter D 2 , wherein D 1 <D 2 , so that according to the diameter ratio, a translation of the force and the stroke of an actuator 1 via a formed between the two pistons 7, 22 coupler gap 23, which is provided with a hydraulic fluid is filled. The coupler body 20 serves to guide the two pistons 7, 22 and is therefore adapted to the inner circumference of the respective piston diameters. With a radially extending collar surface of the coupler body rests against a valve plate 16, in which a control valve 2 is received. In the present case, it is a pressure-balanced control valve 2, with a closing element 6, the valve seat facing away end is guided in a sleeve 19 and limited together with the sleeve 19 and the valve plate 16, a low-pressure space 24, so that guided in the sleeve 19 portion of the closing element 6 of the control valve 2 is not acted upon by the system pressure. For actuation of the control valve 2, therefore, only a compressive force is required, which essentially corresponds to the spring force of a helical spring 18, by means of which the closing element 6 is biased relative to the valve seat 25. For this purpose, the coil spring 18 is supported on the one hand on the sleeve 19, on the other hand on a spring collar 17 of the closing element 6. The valve piston 7 is also biased by a coil spring against the closing element 6. The helical spring is for this purpose supported on the valve piston 7 and on an inner peripheral side radially extending shoulder of the coupler body. In addition to the coil spring as the first spring element 5, a second spring element 9 is provided in the form of a spring sleeve, by means of which the coupler piston 22 is biased against an adjusting piece 4 and thus relative to the actuator unit 1. The spring sleeve is supported on the one hand on a radially extending collar surface of the coupler body 20, on the other hand on a shim 21, which in turn rests against a circumferential radial collar surface of the coupler piston 22. The shim 21 serves to adjust the spring force since the different collar heights of the coupler body 20 and the coupler piston 22 are subject to tolerances.

Im Unterschied zur der hydraulischen Kopplereinheit 3 der Fig. 1 weist die hydraulische Kopplereinheit 3 eines erfindungsgemäßen Kraftstoffinjektors nur einen Ventilkolben 7 auf (siehe Fig. 2 und 3). Auf die Anordnung eines zweiten Kolbens 22 sowie eines Kopplerkörpers 20 entsprechend dem vorstehend beschriebenen Beispiel wird bewusst verzichtet. Die Übersetzung erfolgt somit im Verhältnis 1:1. Da vorliegend das Steuerventil 2 wiederum druckausgeglichen ist, denn das Schließglied 6 des Steuerventils 2 ist in einer Hülse 19 geführt, die gemeinsam mit der Ventilplatte 16 einen Niederdruckraum 24 begrenzen, ist eine Verstärkung der Aktorkraft bzw. des -hubes nicht erforderlich. Als Kopplerspalt 23 dient nunmehr ein zwischen Ventilkolben 7 und Einstellstück 4 ausgebildeten Druckraum 10, der radial von einer Kopplerhülse 8 begrenzt wird. In der Kopplerhülse 8 ist der Ventilkolben 7 beweglich geführt. Der Führungsspalt 13 ist mit nur geringem Spiel ausgeführt und beträgt bei dem vorliegenden Beispiel etwa 4 µm. Zur Abdichtung des Druckraumes 10 ist die Kopplerhülse 8 des Weiteren mit einer Beißkante versehen, mit der die Kopplerhülse 8 an dem Einstellstück 4 dichtend anliegt. Die notwendige Flächenpressung wird durch ein zweites Federelement 9 bewirkt, mittels derer die Kopplerhülse 8 gegenüber dem Einstellstück 4 vorgespannt ist. Das zweite Federelement 9 ist auch in diesem Beispiel eine Federhülse, die einerseits direkt an der Ventilplatte 16, andererseits an der Kopplerhülse 8 abgestützt ist. Die Kopplerhülse 8 weist hierzu einen Bund 12 mit einer radial verlaufenden Bundfläche auf. Der Abstand zwischen dieser Bundfläche und der am Einstellstück 4 anliegenden Beißkante ist das einzige toleranzbehaftete Maß, das die Federkraft beeinflusst. Da der Einfluss minimal ist wurde bei der hydraulischen Kopplereinheit 3 gemäß der Erfindung zudem auf eine Einstellscheibe 21 verzichtet. Durch Verzicht auf einen zweiten Kolben 22 und auf eine Einstellscheibe 21, kann die Baulänge der Kopplereinheit 3 entsprechend dem Ausführungsbeispiel der Fig. 2 um 4,5 mm gegenüber der bekannten Ausführung entsprechend Fig. 1 verkürzt werden.In contrast to the hydraulic coupler unit 3 of Fig. 1 For example, the hydraulic coupler unit 3 of a fuel injector according to the invention has only one valve piston 7 (see FIG Fig. 2 and 3 ). The arrangement of a second piston 22 and a coupler body 20 according to the example described above is deliberately omitted. The translation is thus in the ratio 1: 1. In the present case, the control valve 2 is in turn pressure balanced, because the closing member 6 of the control valve 2 is guided in a sleeve 19, which define a low pressure space 24 together with the valve plate 16, an amplification of the actuator force or deshubes is not required. As a coupler gap 23 is now formed between a valve piston 7 and 4 setting piece pressure chamber 10 which is bounded radially by a coupler sleeve 8. In the coupler sleeve 8, the valve piston 7 is movably guided. The guide gap 13 is designed with only a small clearance and in the present example is about 4 μm. For sealing the pressure chamber 10, the coupler sleeve 8 is further provided with a biting edge with which the coupler sleeve 8 rests sealingly on the adjusting piece 4. The necessary surface pressure is effected by a second spring element 9, by means of which the coupler sleeve 8 is biased against the adjusting piece 4. The second spring element 9 is also in this example a spring sleeve which is supported on the one hand directly to the valve plate 16, on the other hand to the coupler sleeve 8. The coupler sleeve 8 has for this purpose a collar 12 with a radially extending collar surface. The distance between this collar surface and the adjoining adjoining 4 biting edge is the only tolerant degree that affects the spring force. Since the influence is minimal, a dial 21 has also been dispensed with in the case of the hydraulic coupler unit 3 according to the invention. By waiving one Second piston 22 and a shim 21, the length of the coupler unit 3 according to the embodiment of Fig. 2 by 4.5 mm compared to the known design accordingly Fig. 1 be shortened.

Anstelle eines Kopplerkörpers 20 weist die hydraulische Kopplereinheit 3 der Fig. 2 eine Zentrierhülse 14 zur Zentrierung der Kopplerhülse 8 und damit mittelbar zur Zentrierung und Führung des Ventilkolbens 7 auf. Entsprechend der Ausbildung des Kopplerkörpers 20 aus Fig. 1 weist auch die Zentrierhülse 14 der hydraulischen Kopplereinheit 3 der Fig. 2 einen innenumfangseitig radial verlaufenden Absatz 15 auf, an dem ein Ende des ersten Federelementes 5 abgestützt ist, mittels dessen der Ventilkolben 7 gegenüber dem Schließelement 6 des Steuerventils 2 vorgespannt ist.Instead of a coupler body 20, the hydraulic coupler unit 3 of the Fig. 2 a centering sleeve 14 for centering the coupler sleeve 8 and thus indirectly for centering and guiding the valve piston 7. According to the formation of the coupler body 20 Fig. 1 also has the centering sleeve 14 of the hydraulic coupler unit 3 of Fig. 2 an inner peripheral side radially extending shoulder 15, on which one end of the first spring element 5 is supported, by means of which the valve piston 7 is biased against the closing element 6 of the control valve 2.

Eine weitere Zentrierung der Kopplerhülse 8 und damit mittelbar auch des Ventilkolbens 7 erfolgt dadurch, dass das Einstellstück 4 zumindest teilweise in eine innenumfangseitige Ausnehmung der Kopplerhülse eingelassen ist, so dass sie an einem innenumfangseitig radial verlaufenden Absatz 11 der Kopplerhülse 8 anliegt.A further centering of the coupler sleeve 8 and thus indirectly also of the valve piston 7 takes place in that the adjusting piece 4 is at least partially embedded in an inner peripheral side recess of the coupler sleeve so that it rests against an inner peripheral side radially extending shoulder 11 of the coupler sleeve 8.

Da eine Zentrierung der Kopplerhülse 8 über die Zentrierhülse 14 nicht unbedingt erforderlich ist, kann gemäß dem in Fig. 3 dargestellten Ausführungsbeispiels die Zentrierhülse auch auf einen Ringkörper reduziert werden, der nur noch den Ventilkolben 7 im Bereich der Ventilplatte 16 umgibt und diesen infolgedessen zentriert bzw. führt. Das erste Federelement 5 weist hierzu eine axiale Lage auf, so dass es einseitig an der Kopplerhülse 8 abgestützt ist. Darüber hinaus unterscheidet sich die Ausführungsform der Fig. 3 nicht von der der Fig. 2. Allerdings ermöglicht die Reduzierung der Zentrierhülse 14 auf einen am Ventilkolben 7 anliegenden Ringkörper eine Baulängenreduzierung der Kopplereinheit 3 von bis zu 6, 5 mm.Since a centering of the coupler sleeve 8 via the centering sleeve 14 is not absolutely necessary, according to the in Fig. 3 illustrated embodiment, the centering sleeve can also be reduced to an annular body, which surrounds only the valve piston 7 in the region of the valve plate 16 and this centered as a result or leads. For this purpose, the first spring element 5 has an axial position, so that it is supported on one side on the coupler sleeve 8. In addition, the embodiment differs Fig. 3 not from the Fig. 2 , However, the reduction of the centering sleeve 14 allows an applied to the valve piston 7 annular body a reduction in length of the coupler unit 3 of up to 6.5 mm.

Alternativ zur Anordnung einer als Ringkörper ausgebildeten Zentrierhülse 14 kann auch die Ventilplatte 16 mit einem Kragen oder Absatz ausgestattet sein, der eine axiale Führung des Ventilkolbens 7 ermöglicht.As an alternative to the arrangement of a centering sleeve 14 embodied as an annular body, the valve plate 16 can also be equipped with a collar or shoulder which allows axial guidance of the valve piston 7.

Claims (8)

Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit einer Aktor-Einheit (1) zur Betätigung eines Steuerventils (2) und mit einer hydraulischen Kopplereinheit (3), die über ein Einstellstück (4) mit der Aktor-Einheit (1) in Verbindung steht und einen axial verschiebbar geführten und mittels eines ersten Federelementes (5) gegen ein Schließelement (6) des Steuerventils (2) vorgespannten Ventilkolben (7) umfasst,
dadurch gekennzeichnet,
dass die hydraulische Kopplereinheit (3) ferner eine Kopplerhülse (8) umfasst, die mittels eines zweiten Federelementes (9) gegen das Einstellstück (4) vorgespannt ist und gemeinsam mit dem Ventilkolben (7) und dem Einstellstück (4) einen Druckraum (10) begrenzt.Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with an actuator unit (1) for actuating a control valve (2) and with a hydraulic coupler unit (3) via an adjusting piece (4) with the actuator unit (1) in Connection stands and an axially displaceably guided and by means of a first spring element (5) against a closing element (6) of the control valve (2) biased valve piston (7),
characterized,
in that the hydraulic coupler unit (3) furthermore comprises a coupler sleeve (8) which is prestressed against the adjusting piece (4) by means of a second spring element (9) and together with the valve piston (7) and the adjusting piece (4) has a pressure chamber (10). limited. Kraftstoffinjektor nach Anspruch 1, dadurch gekennzeichnet, dass die an dem Einstellstück (4) dichtend anliegende Fläche der Kopplerhülse (8) mit einer Beißkante versehen ist.Fuel injector according to claim 1, characterized in that on the adjusting piece (4) sealingly fitting surface of the coupler sleeve (8) is provided with a biting edge. Kraftstoffinjektor nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kopplerhülse (8) zur teilweisen Aufnahme des Einstellstücks (4) innenumfangsseitig einen umlaufenden radialen Absatz (11) besitzt, mit dem die Kopplerhülse am Einstellstück anliegt.Fuel injector according to claim 1 or 2, characterized in that the coupler sleeve (8) for receiving part of the adjusting piece (4) on the inner peripheral side has a circumferential radial shoulder (11), with which the coupler sleeve rests on the adjusting piece. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kopplerhülse (8) einen nach radial außen geführten Bund (12) zur Auflage des zweiten Federelementes (9) besitzt, wobei das zweite Federelement vorzugsweise eine Federhülse ist.Fuel injector according to one of the preceding claims, characterized in that the coupler sleeve (8) has a radially outwardly guided collar (12) for supporting the second Spring element (9) has, wherein the second spring element is preferably a spring sleeve. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Führungsspalt (13) zwischen Kopplerhülse (8) und Ventilkolben (7) weniger als 10 µm, vorzugsweise weniger als 5 µm beträgt.Fuel injector according to one of the preceding claims, characterized in that the guide gap (13) between coupler sleeve (8) and valve piston (7) is less than 10 microns, preferably less than 5 microns. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das erste Federelement (5) einerseits an der Kopplerhülse (8), andererseits am Ventilkolben (7) abgestützt ist, wobei das erste Federelement vorzugsweise eine Schraubenfeder ist.Fuel injector according to one of the preceding claims, characterized in that the first spring element (5) on the one hand on the coupler sleeve (8), on the other hand on the valve piston (7) is supported, wherein the first spring element is preferably a helical spring. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die hydraulische Kopplereinheit (3) zur Zentrierung der Kopplerhülse (8) und/oder des Ventilkolbens (7) ferner eine Zentrierhülse (14) umfasst.Fuel injector according to one of the preceding claims, characterized in that the hydraulic coupler unit (3) for centering the coupler sleeve (8) and / or the valve piston (7) further comprises a centering sleeve (14). Kraftstoffinjektor nach Anspruch 7, dadurch gekennzeichnet, dass die Zentrierhülse (14) innenumfangseitig einen umlaufenden radialen Absatz (15) besitzt, an dem das erste Federelement (5) abgestützt ist, wobei das erste Federelement vorzugsweise eine Schraubenfeder ist.Fuel injector according to claim 7, characterized in that the centering sleeve (14) on the inner peripheral side has a circumferential radial shoulder (15) on which the first spring element (5) is supported, wherein the first spring element is preferably a helical spring.
EP20090180310 2009-02-16 2009-12-22 Fuel injector Not-in-force EP2218906B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910000875 DE102009000875A1 (en) 2009-02-16 2009-02-16 fuel injector

Publications (2)

Publication Number Publication Date
EP2218906A1 true EP2218906A1 (en) 2010-08-18
EP2218906B1 EP2218906B1 (en) 2013-02-20

Family

ID=41718754

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090180310 Not-in-force EP2218906B1 (en) 2009-02-16 2009-12-22 Fuel injector

Country Status (2)

Country Link
EP (1) EP2218906B1 (en)
DE (1) DE102009000875A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012059265A1 (en) * 2010-11-04 2012-05-10 Robert Bosch Gmbh Fuel injector
EP3035520A1 (en) * 2014-12-19 2016-06-22 Robert Bosch Gmbh Hydraulic coupler unit for controlling a valve

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004044812A1 (en) * 2004-09-16 2006-03-23 Robert Bosch Gmbh Control valve of an injection nozzle for an internal combustion engine
DE102006042601A1 (en) 2006-09-11 2008-03-27 Robert Bosch Gmbh Injector for injecting fuel
EP1916410A2 (en) * 2006-10-20 2008-04-30 Robert Bosch Gmbh Pilot valve for an injector and injector

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004044812A1 (en) * 2004-09-16 2006-03-23 Robert Bosch Gmbh Control valve of an injection nozzle for an internal combustion engine
DE102006042601A1 (en) 2006-09-11 2008-03-27 Robert Bosch Gmbh Injector for injecting fuel
EP1916410A2 (en) * 2006-10-20 2008-04-30 Robert Bosch Gmbh Pilot valve for an injector and injector

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012059265A1 (en) * 2010-11-04 2012-05-10 Robert Bosch Gmbh Fuel injector
CN103189635A (en) * 2010-11-04 2013-07-03 罗伯特·博世有限公司 Fuel injector
CN103189635B (en) * 2010-11-04 2016-08-31 罗伯特·博世有限公司 Fuel injector
EP3035520A1 (en) * 2014-12-19 2016-06-22 Robert Bosch Gmbh Hydraulic coupler unit for controlling a valve

Also Published As

Publication number Publication date
DE102009000875A1 (en) 2010-08-19
EP2218906B1 (en) 2013-02-20

Similar Documents

Publication Publication Date Title
EP1989436B1 (en) Fuel injection device for an internal combustion engine
EP1477666B1 (en) Supply pump, in particular high pressure fuel pump for internal combustion engines
EP2715103B1 (en) Nozzle assembly for a fuel injector, and fuel injector
WO2011023467A1 (en) Fuel injection valve
EP2218906B1 (en) Fuel injector
WO2011042296A1 (en) Fuel injection valve and production thereof
EP2226490B1 (en) Fuel injector
EP3060789B1 (en) Fuel injector
EP1873393A1 (en) Injector
EP2957760B1 (en) Nozzle assembly for a fuel injector and fuel injector
EP2905458B1 (en) Nozzle assembly for a fuel injector and fuel injector
WO2005017323A1 (en) Hydraulic support element
WO2011160900A1 (en) Fuel injection device comprising a hydraulic coupler
EP2955366B1 (en) Nozzle assembly for a fuel injector and fuel injector
EP3035520B1 (en) Hydraulic coupler unit for controlling a valve
EP3303817B1 (en) Common-rail-injector
EP2884088B1 (en) Fuel injector
EP2366887B1 (en) Fuel injector
DE102014209997A1 (en) Common rail injector
WO2009013069A1 (en) Fuel injector having a non-guided nozzle needle
EP3358178A1 (en) Hydraulic coupler for a piezo injector, piezo injector
DE102017204644A1 (en) Hydraulic coupler unit and fuel injector
WO2013000635A1 (en) Fuel injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

17P Request for examination filed

Effective date: 20110218

RIC1 Information provided on ipc code assigned before grant

Ipc: F02M 63/00 20060101AFI20120809BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 597674

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502009006276

Country of ref document: DE

Effective date: 20130418

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130220

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130531

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130520

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130620

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130520

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130521

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130620

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

26N No opposition filed

Effective date: 20131121

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502009006276

Country of ref document: DE

Effective date: 20131121

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20131231

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20131222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131222

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131222

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131231

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131231

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20091222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130220

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 597674

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141222

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20181218

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190221

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502009006276

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200701

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191231