EP2226490A1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
EP2226490A1
EP2226490A1 EP10151027A EP10151027A EP2226490A1 EP 2226490 A1 EP2226490 A1 EP 2226490A1 EP 10151027 A EP10151027 A EP 10151027A EP 10151027 A EP10151027 A EP 10151027A EP 2226490 A1 EP2226490 A1 EP 2226490A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injector
sleeve
coupler
injector according
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
EP10151027A
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German (de)
French (fr)
Other versions
EP2226490B1 (en
Inventor
Andreas Gruenberger
Martin Kiontke
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication date
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Publication of EP2226490A1 publication Critical patent/EP2226490A1/en
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Publication of EP2226490B1 publication Critical patent/EP2226490B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 having the features of 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 control valve of the proposed fuel injector on an extended valve pin with a lying outside the valve plate section forms a guided in a coupler sleeve valve piston of a hydraulic coupler unit.
  • the coupler sleeve and the setting piece together define a pressure chamber, which serves as a hydraulic coupler.
  • the hydraulic coupler unit of the fuel injector according to the invention has only one piston, which is also still formed by a portion of an extended valve pin.
  • a second piston By dispensing with a second piston, a significant reduction in length of the hydraulic coupler unit and thus the total length of the fuel injector can be effected.
  • the translation takes place here in the ratio 1: 1, that is, there is no gain of Aktorhubes instead.
  • the fuel injector according to the invention therefore preferably has a pressure-compensated control valve whose actuation essentially takes place independently of the system pressure and thus requires a lower pressure force.
  • the control valve can be pressure-balanced, for example, in that the valve pin of the control valve is guided on the side facing away from the valve seat in a sleeve, valve closure member and sleeve defining a pressure chamber which is always pressure-relieved.
  • 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.
  • 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.
  • a sufficient guidance of the valve piston is effected in the fuel injector according to the invention via the coupler sleeve.
  • a spring element for biasing the coupler sleeve relative to the adjusting piece is further provided.
  • the spring element is preferably a coil spring or a spring sleeve.
  • the spring force of the spring element ensures a sealing contact of the coupler sleeve on the adjusting piece and thus the sealing of the enclosed by the coupler sleeve, the adjusting piece and the valve piston pressure chamber.
  • the coupler sleeve on the upper side facing the spring element has an axially recessed shoulder for supporting the spring element.
  • the non-recessed region with a smaller diameter protrudes into the spring element, which thereby experiences a centering.
  • the coupler sleeve itself is centered over the valve piston.
  • the sealing piece on the adjusting surface of the coupler sleeve is provided with a biting edge.
  • the necessary surface pressure for sealing contact is effected by the voltage applied to the coupler sleeve spring element.
  • the distance between the radial shoulder and the biting edge of the coupler sleeve is the only degree of tolerance which has an influence on the spring force of the spring element, since the other end of the spring element is supported on the valve plate. Since the influence of this measure is minimal, the already mentioned in connection with the prior art shim for adjusting the spring force can be omitted. 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 further reduction in the length of the coupler unit and thus the total length of the fuel injector.
  • a guide gap is provided between the coupler sleeve and serving as a valve piston portion of the valve pin, which is less than 10 microns, preferably less than 5 microns. For one thing is thereby ensuring the sealing of the serving as a hydraulic coupler pressure chamber, on the other hand, a precise guidance of the valve piston in the region of the setting piece.
  • the coupler sleeve has on the inner circumference side on the top side facing the spring element a cone-shaped insertion opening for receiving the portion of the valve pin serving as the valve piston. Since the valve piston and the valve pin are integrally formed, the assembly has to be made from the valve seat side. That is, when inserting the valve pin serving as a valve piston portion is inserted through the valve plate and inserted into the coupler. In order to facilitate the insertion, the receiving bore of the coupler sleeve is formed on the valve seat side conical, so that the valve piston is automatically centered during insertion.
  • the serving as a valve piston portion of the valve pin in an area has at least one flattening.
  • this area is within the valve plate, more preferably in the vicinity of the valve seat.
  • the at least one flattening forms a return channel, via which high-pressure fuel can flow out when the control valve is open.
  • valve seat valve pin or portion of the valve pin has a spring collar on which a spring element is supported, by means of which the valve pin is biased relative to the valve seat.
  • the same spring element simultaneously serves to axially bias the section of the valve pin serving as the valve piston.
  • On a separate spring element for the valve piston can therefore be omitted.
  • valve pin is furthermore preferably guided at its end facing away from the valve seat in a sleeve, the valve pin, the sleeve and the valve plate defining a low-pressure space.
  • the actuation of the valve pin can thus take place essentially system pressure independent, that is, it requires a lower pressure force.
  • hydraulic coupler unit 3 comprises two guided in a coupler body 21 piston, a valve piston 8 with a first diameter D 1 and a coupler piston 22 with a second diameter D 2 , where 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 8, 22 coupler gap 23, which is filled with a hydraulic fluid.
  • the coupler body 21 serves to guide the two pistons 8, 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 5, in which a control valve 2 is received.
  • a pressure-balanced control valve 2 with a valve pin 6, the valve seat facing away end is guided in a sleeve 19 and limited together with the sleeve 19 and the valve plate 5, a low pressure space 20 so that the guided in the sleeve 19 portion of the valve pin 6 of the control valve 2 is not is acted upon by the system pressure.
  • a compressive force is required, which essentially corresponds to the spring force of a helical spring 17, by means of which the valve pin 6 is biased relative to the valve seat 18.
  • the coil spring 17 is supported on the one hand on the sleeve 19, on the other hand on a spring collar 16 of the valve pin 6.
  • the valve piston 8 is also biased by a coil spring 25 relative to the valve pin 6.
  • the helical spring 25 is supported on the valve piston 8 and on an inner peripheral side radially extending shoulder of the coupler body 21.
  • a second spring element in the form of a spring sleeve 10 is provided, by means of which coupler piston 22 is biased against an adjusting piece 4 and thus relative to the actuator unit 1.
  • the spring sleeve 10 is supported on the one hand on a radially extending collar surface of the coupler body 21, on the other hand on a shim 24, which in turn bears against a circumferential radial collar surface of the coupler piston 22.
  • the dial 24 is used to adjust the spring force, since the different collar heights of the coupler body 21 and the coupler piston 22 are subject to tolerances.
  • valve piston 8 which is also formed by a portion of an elongated valve pin 6. That is, the valve piston 8 and the valve pin 6 form a component.
  • valve piston 8 is guided only in a coupler sleeve 7, which is biased by a spring element 10 relative to the adjusting piece 4 and thus fixed in position.
  • the coupler sleeve 7, the valve piston 8 and the adjusting piece 4 define a pressure chamber 9, which serves as a hydraulic coupler.
  • the translation is done in the ratio 1: 1.
  • a reinforcement of the force of an actuator of an actuator unit 1 is not required because the control valve 2 is pressure balanced.
  • the valve pin 6 of the control valve 2 is guided in a sleeve 19, wherein the sleeve 19, the valve pin 6 and the valve plate 5 define a low-pressure space 20.
  • the coupler sleeve 7 is further provided with a biting edge 12, with which the coupler sleeve 7 bears sealingly against the adjusting piece 4.
  • the necessary surface pressure is effected by the spring element 10.
  • the spring element 10 is a helical spring which is supported on the one hand directly on the valve plate 5, on the other hand on the coupler sleeve 7.
  • the coupler sleeve 7 has for this purpose an axially recessed paragraph 11.
  • the distance between this paragraph 11 and the adjoining adjoining 4 B formulatekante 12 is the only tolerance-sensitive measure that has an influence on the spring force. Since this influence is minimal, in the case of the hydraulic coupler unit 3 according to the invention, a dial 24 for adjusting the spring force has also been dispensed with.
  • the valve pin 6 By a portion of the valve pin 6 at the same time forms the valve piston 8, a further spring element for the axial bias of the valve piston 8 is not required, because the axial position of the valve piston 8 is predetermined by the valve pin 6.
  • the structure of the hydraulic simplifies Coupler unit considerably.
  • the hydraulic coupler unit serving as a valve piston 8 portion of the valve pin 6 is inserted through the valve plate 5 and inserted into the central bore of the coupler sleeve 7.
  • this To facilitate insertion into the coupler sleeve 7, this is provided with a cone-shaped insertion opening 14, so that the valve piston is automatically centered during insertion. This is particularly advantageous because the coupler sleeve 7 serves as a guide for the valve piston 8 and the guide gap 13 has little play.
  • valve plate 5 The guided through the valve plate 5 and serving as a valve piston 8 portion of the valve pin 6 has in the example shown a flattening 15 in the region of the valve plate 5, which closely surrounds the valve piston 8 in this area. By the flattening 15, a return passage for fuel under high pressure is formed.

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

Abstract

The injector has an actuator unit (1) for actuating a control valve (2), and a hydraulic coupling unit (3) arranged between the actuator unit and the control valve. The coupling unit stands in connection with the actuator unit, and the control valve is formed in a valve plate (5). The control valve includes an elongated valve bolt (6) with a section resting outside of the valve plate. The section forms a coupling unit's valve bolt (8) that is guided into a coupling sleeve (7). The section with the coupling sleeve and an adjustment piece (4) limits a pressure chamber (9).

Description

Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit den Merkmalen des Oberbegriffes des Anspruchs 1.The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having the features of 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.

Erfindungsgemäß weist das Steuerventil des vorgeschlagenen Kraftstoffinjektors einen verlängerten Ventilbolzen mit einem außerhalb der Ventilplatte liegenden Abschnitt auf. Dieser Abschnitt bildet einen in einer Kopplerhülse geführten Ventilkolben einer hydraulischen Kopplereinheit aus. Zudem begrenzen der als Ventilkolben dienende Abschnitt des Ventilbolzens, die Kopplerhülse und das Einstellstück gemeinsam einen Druckraum, der als hydraulischer Koppler dient.According to the invention, the control valve of the proposed fuel injector on an extended valve pin with a lying outside the valve plate section. This section forms a guided in a coupler sleeve valve piston of a hydraulic coupler unit. In addition, serving as a valve piston portion of the valve pin, the coupler sleeve and the setting piece together define a pressure chamber, which serves as a hydraulic coupler.

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, der zudem noch von einem Abschnitt eines verlängerten Ventilbolzens gebildet wird. Durch den Verzicht auf einen zweiten Kolben kann eine deutliche Baulängenreduzierung der hydraulischen Kopplereinheit und damit der Gesamtlänge des Kraftstoffinjektors bewirkt werden. Die Übersetzung erfolgt vorliegend im Verhältnis 1:1, das heißt es findet keine Verstärkung des Aktorhubes statt.In contrast to the hydraulic coupler unit of the initially described and known from the prior art injector, the hydraulic coupler unit of the fuel injector according to the invention has only one piston, which is also still formed by a portion of an extended valve pin. By dispensing with a second piston, a significant reduction in length of the hydraulic coupler unit and thus the total length of the fuel injector can be effected. The translation takes place here in the ratio 1: 1, that is, there is no gain of Aktorhubes instead.

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 der Ventilbolzen des Steuerventils auf der dem Ventilsitz abgewandten Seite 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 fuel injector according to the invention therefore preferably has a pressure-compensated control valve whose actuation essentially takes place independently of the system pressure and thus requires a lower pressure force. The control valve can be pressure-balanced, for example, in that the valve pin of the control valve is guided on the side facing away from the valve seat in a sleeve, valve closure member and sleeve defining a pressure chamber which is always pressure-relieved. 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.

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. Eine ausreichende Führung des Ventilkolbens wird bei dem erfindungsgemäßen Kraftstoffinjektor über die Kopplerhülse bewirkt.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. A sufficient guidance of the valve piston is effected in the fuel injector according to the invention via the coupler sleeve.

Darüber hinaus kann bei dem erfindungsgemäßen Kraftstoffinjektor auf die Anordnung einer Einstellscheibe zur Einstellung der Federkraft eines Federelementes 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.In addition, can be dispensed with in the fuel injector according to the invention on the arrangement of a dial for adjusting the spring force of a spring element 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.

Ein Federelement zur Vorspannung der Kopplerhülse gegenüber dem Einstellstück ist weiterhin vorgesehen. Das Federelement ist vorzugsweise eine Schraubenfeder oder eine Federhülse. Die Federkraft des Federelementes stellt eine dichtende Anlage der Kopplerhülse am Einstellstück und damit die Abdichtung des von der Kopplerhülse, dem Einstellstück und dem Ventilkolben umschlossenen Druckraumes sicher.A spring element for biasing the coupler sleeve relative to the adjusting piece is further provided. The spring element is preferably a coil spring or a spring sleeve. The spring force of the spring element ensures a sealing contact of the coupler sleeve on the adjusting piece and thus the sealing of the enclosed by the coupler sleeve, the adjusting piece and the valve piston pressure chamber.

Vorzugsweise besitzt die Kopplerhülse auf der dem Federelement zugewandten Oberseite einen axial zurückspringenden Absatz zur Auflage des Federelementes. Der nicht zurückspringende Bereich mit einem geringeren Durchmesser ragt in das Federelement hinein, das dadurch eine Zentrierung erfährt. Die Kopplerhülse selbst ist über den Ventilkolben zentriert.Preferably, the coupler sleeve on the upper side facing the spring element has an axially recessed shoulder for supporting the spring element. The non-recessed region with a smaller diameter protrudes into the spring element, which thereby experiences a centering. The coupler sleeve itself is centered over the valve piston.

Weiterhin vorzugsweise ist die an dem Einstellstück dichtend anliegende Fläche der Kopplerhülse mit einer Beißkante versehen. Die notwenige Flächenpressung zur dichtenden Anlage wird durch das an der Kopplerhülse anliegende Federelement bewirkt. Der Abstand zwischen dem radialen Absatz und der Beißkante der Kopplerhülse stellt das einzige toleranzbehaftete Maß dar, das Einfluss auf die Federkraft des Federelementes hat, da das andere Ende des Federelementes an der Ventilplatte abgestützt ist. Da der Einfluss dieses Maßes 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 sealing piece on the adjusting surface of the coupler sleeve is provided with a biting edge. The necessary surface pressure for sealing contact is effected by the voltage applied to the coupler sleeve spring element. The distance between the radial shoulder and the biting edge of the coupler sleeve is the only degree of tolerance which has an influence on the spring force of the spring element, since the other end of the spring element is supported on the valve plate. Since the influence of this measure is minimal, the already mentioned in connection with the prior art shim for adjusting the spring force can be omitted. 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 further reduction in the length of the coupler unit and thus the total length of the fuel injector.

Nach einer bevorzugten Ausführungsform ist zwischen der Kopplerhülse und dem als Ventilkolben dienenden Abschnitt des Ventilbolzens ein Führungsspalt vorgesehen, der weniger als 10 µm, vorzugsweise weniger als 5 µm, beträgt. Zum Einen ist dadurch die Abdichtung des als hydraulischer Koppler dienenden Druckraumes, zum Anderen eine genaue Führung des Ventilkolbens im Bereich des Einstellstückes sichergestellt.According to a preferred embodiment, a guide gap is provided between the coupler sleeve and serving as a valve piston portion of the valve pin, which is less than 10 microns, preferably less than 5 microns. For one thing is thereby ensuring the sealing of the serving as a hydraulic coupler pressure chamber, on the other hand, a precise guidance of the valve piston in the region of the setting piece.

Vorteilhafterweise besitzt die Kopplerhülse innenumfangseitig auf der dem Federelement zugewandten Oberseite eine konusförmige Einführöffnung zur Aufnahme des als Ventilkolben dienenden Abschnitts des Ventilbolzens. Da der Ventilkolben und der Ventilbolzen einstückig ausgebildet sind, hat die Montage von der Ventilsitzseite zu erfolgen. Das heißt beim Einsetzen des Ventilbolzens wird der als Ventilkolben dienende Abschnitt durch die Ventilplatte hindurch gesteckt und in die Kopplerhülse eingeführt. Um das Einführen zu erleichtern, ist die Aufnahmebohrung der Kopplerhülse ventilsitzseitig konusförmig ausgebildet, so dass der Ventilkolben beim Einführen automatisch zentriert wird.Advantageously, the coupler sleeve has on the inner circumference side on the top side facing the spring element a cone-shaped insertion opening for receiving the portion of the valve pin serving as the valve piston. Since the valve piston and the valve pin are integrally formed, the assembly has to be made from the valve seat side. That is, when inserting the valve pin serving as a valve piston portion is inserted through the valve plate and inserted into the coupler. In order to facilitate the insertion, the receiving bore of the coupler sleeve is formed on the valve seat side conical, so that the valve piston is automatically centered during insertion.

Bevorzugt besitzt der als Ventilkolben dienende Abschnitt des Ventilbolzens in einem Bereich zumindest eine Abflachung. Vorzugsweise liegt dieser Bereich innerhalb der Ventilplatte, weiterhin vorzugsweise in der Nähe des Ventilsitzes. Die wenigstens eine Abflachung bildet einen Rücklaufkanal aus, über welchen bei geöffnetem Steuerventil unter hohem Druck stehender Kraftstoff abfließen kann.Preferably, the serving as a valve piston portion of the valve pin in an area has at least one flattening. Preferably, this area is within the valve plate, more preferably in the vicinity of the valve seat. The at least one flattening forms a return channel, via which high-pressure fuel can flow out when the control valve is open.

Der mit einem Ventilsitz zusammenwirkende Ventilbolzen bzw. Abschnitt des Ventilbolzens besitzt einen Federkragen, an dem ein Federelement abgestützt ist, mittels dessen der Ventilbolzen gegenüber dem Ventilsitz vorgespannt ist. Indem Ventilbolzen und Ventilkolben einstückig ausgebildet sind, dient dasselbe Federelement gleichzeitig dazu, den als Ventilkolben dienenden Abschnitt des Ventilbolzens axial vorzuspannen. Auf ein separates Federelement für den Ventilkolben kann daher verzichtet werden. Die reduzierte Anzahl an Bauteilen vereinfacht den Aufbau des erfindungsgemäßen Kraftstoffinjektors, so dass dieser einfach und kostengünstig herstellbar ist. Zudem verringert sich neben der Gesamtlänge auch das Gewicht des Injektors, was ebenfalls ein Vorteil ist.The cooperating with a valve seat valve pin or portion of the valve pin has a spring collar on which a spring element is supported, by means of which the valve pin is biased relative to the valve seat. By integrally forming the valve pin and the valve piston, the same spring element simultaneously serves to axially bias the section of the valve pin serving as the valve piston. On a separate spring element for the valve piston can therefore be omitted. The reduced number of components simplifies the structure of the invention Fuel injector, so that this is easy and inexpensive to produce. In addition, in addition to the overall length and the weight of the injector is reduced, which is also an advantage.

Zur Ausbildung eines druckausgeglichenen Steuerventils ist weiterhin bevorzugt der Ventilbolzen an seinem dem Ventilsitz abgewandten Ende in einer Hülse geführt, wobei der Ventilbolzen, die Hülse und die Ventilplatte einen Niederdruckraum begrenzen. Die Betätigung des Ventilbolzens kann somit im Wesentlichen systemdruckunabhängig erfolgen, das heißt, sie erfordert eine geringere Druckkraft.In order to form a pressure-balanced control valve, the valve pin is furthermore preferably guided at its end facing away from the valve seat in a sleeve, the valve pin, the sleeve and the valve plate defining a low-pressure space. The actuation of the valve pin can thus take place essentially system pressure independent, that is, it requires a lower pressure force.

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

  • Fig. leinen Längsschnitt durch die hydraulische Kopplereinheit eines aus dem Stand der Technik bekannten Kraftstoffinjektors und
  • Fig. 2 einen Längsschnitt durch die hydraulische Kopplereinheit eines erfindungsgemäßen Kraftstoffinjektors.
Preferred embodiments of the invention are explained below with reference to the drawings. Show it:
  • Fig. Leinen. Longitudinal section through the hydraulic coupler unit of a known from the prior art fuel injector and
  • Fig. 2 a longitudinal section through the hydraulic coupler unit of a fuel injector according to the invention.

Die in Fig. 1 dargestellte hydraulische Kopplereinheit 3 umfasst zwei in einem Kopplerkörper 21 geführte Kolben, einen Ventilkolben 8 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 8, 22 ausgebildeten Kopplerspalt 23 erfolgt, der mit einer Hydraulikflüssigkeit gefüllt ist. Der Kopplerkörper 21 dient der Führung der beiden Kolben 8, 22 und ist daher innenumfangseitig den jeweiligen Kolbendurchmessern angepasst. Mit einer radial verlaufenden Bundfläche liegt der Kopplerkörper an einer Ventilplatte 5 an, in der ein Steuerventil 2 aufgenommen ist. Vorliegend handelt es sich um ein druckausgeglichenes Steuerventil 2, mit einem Ventilbolzen 6, dessen ventilsitzabgewandtes Ende in einer Hülse 19 geführt ist und gemeinsam mit der Hülse 19 und der Ventilplatte 5 einen Niederdruckraum 20 begrenzt, so dass der in der Hülse 19 geführte Abschnitt des Ventilbolzens 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 17 entspricht, mittels derer der Ventilbolzen 6 gegenüber dem Ventilsitz 18 vorgespannt ist. Hierzu ist die Schraubenfeder 17 einerseits an der Hülse 19, andererseits an einem Federkragen 16 des Ventilbolzens 6 abgestützt. Der Ventilkolben 8 ist ebenfalls mittels einer Schraubenfeder 25 gegenüber dem Ventilbolzen 6 vorgespannt. Die Schraubenfeder 25 ist hierzu an dem Ventilkolben 8 und an einem innenumfangseitig radial verlaufenden Absatz des Kopplerkörpers 21 abgestützt. Neben der Schraubenfeder 25 als erstem Federelement ist ein zweites Federelement in Form einer Federhülse 10 vorgesehen, mittels derer Kopplerkolben 22 gegenüber einem Einstellstück 4 und damit gegenüber der Aktor-Einheit 1 vorgespannt ist. Die Federhülse 10 ist einerseits an einer radial verlaufenden Bundfläche des Kopplerkörpers 21, andererseits an einer Einstellscheibe 24 abgestützt, die wiederum an einer umlaufenden radialen Bundfläche des Kopplerkolbens 22 anliegt. Die Einstellscheibe 24 dient der Einstellung der Federkraft, da die verschiedenen Bundhöhen des Kopplerkörpers 21 und des Kopplerkolbens 22 toleranzbehaftet sind.In the Fig. 1 shown hydraulic coupler unit 3 comprises two guided in a coupler body 21 piston, a valve piston 8 with a first diameter D 1 and a coupler piston 22 with a second diameter D 2 , where 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 8, 22 coupler gap 23, which is filled with a hydraulic fluid. The coupler body 21 serves to guide the two pistons 8, 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 5, in which a control valve 2 is received. In the present case it concerns a pressure-balanced control valve 2, with a valve pin 6, the valve seat facing away end is guided in a sleeve 19 and limited together with the sleeve 19 and the valve plate 5, a low pressure space 20 so that the guided in the sleeve 19 portion of the valve pin 6 of the control valve 2 is not is 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 17, by means of which the valve pin 6 is biased relative to the valve seat 18. For this purpose, the coil spring 17 is supported on the one hand on the sleeve 19, on the other hand on a spring collar 16 of the valve pin 6. The valve piston 8 is also biased by a coil spring 25 relative to the valve pin 6. For this purpose, the helical spring 25 is supported on the valve piston 8 and on an inner peripheral side radially extending shoulder of the coupler body 21. In addition to the coil spring 25 as the first spring element, a second spring element in the form of a spring sleeve 10 is provided, by means of which coupler piston 22 is biased against an adjusting piece 4 and thus relative to the actuator unit 1. The spring sleeve 10 is supported on the one hand on a radially extending collar surface of the coupler body 21, on the other hand on a shim 24, which in turn bears against a circumferential radial collar surface of the coupler piston 22. The dial 24 is used to adjust the spring force, since the different collar heights of the coupler body 21 and the coupler piston 22 are subject to tolerances.

Im Unterschied zur der hydraulischen Kopplereinheit 3 der Fig. 1 weist die hydraulische Kopplereinheit 3 des erfindungsgemäßen Kraftstoffinjektors entsprechend der Fig. 2 nur einen Ventilkolben 8 auf, der zudem von einem Abschnitt eines verlängerten Ventilbolzens 6 ausgebildet wird. Das heißt, dass der Ventilkolben 8 und der Ventilbolzen 6 ein Bauteil bilden.In contrast to the hydraulic coupler unit 3 of Fig. 1 has the hydraulic coupler unit 3 of the fuel injector according to the invention according to the Fig. 2 only a valve piston 8, which is also formed by a portion of an elongated valve pin 6. That is, the valve piston 8 and the valve pin 6 form a component.

Darüber hinaus wurde bei der Anordnung der Fig. 2 auf einen Kopplerkörper 21 zur axialen Führung verzichtet. Der Ventilkolben 8 ist lediglich in einer Kopplerhülse 7 geführt, die mittels eines Federelementes 10 gegenüber dem Einstellstück 4 vorgespannt ist und somit in ihrer Lage fixiert ist. Die Kopplerhülse 7, der Ventilkolben 8 und das Einstellstück 4 begrenzen einen Druckraum 9, der als hydraulischer Koppler dient. Die Übersetzung erfolgt im Verhältnis 1:1. Eine Verstärkung der Kraft eines Aktors einer Aktor-Einheit 1 ist nicht erforderlich, da das Steuerventil 2 druckausgeglichen ist. Denn der Ventilbolzen 6 des Steuerventils 2 ist in einer Hülse 19 geführt, wobei die Hülse 19, der Ventilbolzen 6 und die Ventilplatte 5 einen Niederdruckraum 20 begrenzen.In addition, in the arrangement of the Fig. 2 dispensed with a coupler body 21 for axial guidance. The valve piston 8 is guided only in a coupler sleeve 7, which is biased by a spring element 10 relative to the adjusting piece 4 and thus fixed in position. The coupler sleeve 7, the valve piston 8 and the adjusting piece 4 define a pressure chamber 9, which serves as a hydraulic coupler. The translation is done in the ratio 1: 1. A reinforcement of the force of an actuator of an actuator unit 1 is not required because the control valve 2 is pressure balanced. For the valve pin 6 of the control valve 2 is guided in a sleeve 19, wherein the sleeve 19, the valve pin 6 and the valve plate 5 define a low-pressure space 20.

Die Kopplerhülse 7 ist ferner mit einer Beißkante 12 versehen, mit der die Kopplerhülse 7 dichtend an dem Einstellstück 4 anliegt. Die notwendige Flächenpressung wird durch das Federelement 10 bewirkt. Vorliegend ist das Federelement 10 eine Schraubenfeder, die einerseits direkt an der Ventilplatte 5, andererseits an der Kopplerhülse 7 abgestützt ist. Die Kopplerhülse 7 weist hierzu einen axial zurückspringenden Absatz 11 auf. Der Abstand zwischen diesem Absatz 11 und der am Einstellstück 4 anliegenden Beißkante 12 ist das einzige toleranzbehaftete Maß, das einen Einfluss auf die Federkraft hat. Da dieser Einfluss minimal ist wurde bei der hydraulischen Kopplereinheit 3 gemäß der Erfindung ferner auf eine Einstellscheibe 24 zur Einstellung der Federkraft verzichtet.The coupler sleeve 7 is further provided with a biting edge 12, with which the coupler sleeve 7 bears sealingly against the adjusting piece 4. The necessary surface pressure is effected by the spring element 10. In the present case, the spring element 10 is a helical spring which is supported on the one hand directly on the valve plate 5, on the other hand on the coupler sleeve 7. The coupler sleeve 7 has for this purpose an axially recessed paragraph 11. The distance between this paragraph 11 and the adjoining adjoining 4 Beißkante 12 is the only tolerance-sensitive measure that has an influence on the spring force. Since this influence is minimal, in the case of the hydraulic coupler unit 3 according to the invention, a dial 24 for adjusting the spring force has also been dispensed with.

Indem ein Abschnitt des Ventilbolzens 6 zugleich den Ventilkolben 8 bildet, ist ein weiteres Federelement zur axialen Vorspannung des Ventilkolbens 8 nicht erforderlich, denn die axiale Lage des Ventilkolbens 8 ist durch den Ventilbolzen 6 vorgegeben. Somit vereinfacht sich der Aufbau der hydraulischen Kopplereinheit erheblich. Bei der Montage der hydraulischen Kopplereinheit wird der als Ventilkolben 8 dienende Abschnitt des Ventilbolzens 6 durch die Ventilplatte 5 hindurch gesteckt und in die zentrale Bohrung der Kopplerhülse 7 eingeführt. Um das Einführen in die Kopplerhülse 7 zu erleichtern, ist diese mit einer konusförmigen Einführöffnung 14 versehen, so dass der Ventilkolben beim Einführen automatisch zentriert wird. Dies ist insbesondere von Vorteil, da die Kopplerhülse 7 als Führung für den Ventilkolben 8 dient und der Führungsspalt 13 nur wenig Spiel besitzt.By a portion of the valve pin 6 at the same time forms the valve piston 8, a further spring element for the axial bias of the valve piston 8 is not required, because the axial position of the valve piston 8 is predetermined by the valve pin 6. Thus, the structure of the hydraulic simplifies Coupler unit considerably. During assembly of the hydraulic coupler unit serving as a valve piston 8 portion of the valve pin 6 is inserted through the valve plate 5 and inserted into the central bore of the coupler sleeve 7. To facilitate insertion into the coupler sleeve 7, this is provided with a cone-shaped insertion opening 14, so that the valve piston is automatically centered during insertion. This is particularly advantageous because the coupler sleeve 7 serves as a guide for the valve piston 8 and the guide gap 13 has little play.

Der durch die Ventilplatte 5 hindurch geführte und als Ventilkolben 8 dienende Abschnitt des Ventilbolzens 6 weist in dem dargestellten Beispiel eine Abflachung 15 im Bereich der Ventilplatte 5 auf, die in diesem Bereich den Ventilkolben 8 eng umgibt. Durch die Abflachung 15 wird ein Rücklaufkanal für unter hohem Druck stehenden Kraftstoff ausgebildet.The guided through the valve plate 5 and serving as a valve piston 8 portion of the valve pin 6 has in the example shown a flattening 15 in the region of the valve plate 5, which closely surrounds the valve piston 8 in this area. By the flattening 15, a return passage for fuel under high pressure is formed.

Insbesondere im Vergleich mit einem aus dem Stand der Technik bekannten Injektor entsprechend Fig. 1 wird deutlich, dass der erfindungsgemäße Kraftstoffinjektor einfacher aufgebaut und damit leichter und kostengünstiger herstellbar ist. Der Verzicht auf eine Einstellscheibe 24, einen Kopplerkolben 22 und eine Kopplerkörper 21 führt zudem zu einer deutlichen Baulängenreduzierung und Verringerung des Gewichts. Der Kraftstoffinjektor ist somit in vielen Brennkraftmaschinen einsetzbar.In particular, in comparison with an injector known from the prior art accordingly Fig. 1 It is clear that the fuel injector according to the invention is simpler in construction and thus easier and less expensive to produce. The omission of a shim 24, a coupler piston 22 and a coupler body 21 also leads to a significant length reduction and weight reduction. The fuel injector is thus used in many internal combustion engines.

Claims (9)

Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit einer Aktor-Einheit (1) zur Betätigung eines Steuerventils (2) und mit einer zwischen Aktor-Einheit und Steuerventil angeordneten hydraulischen Kopplereinheit (3), die über ein Einstellstück (4) mit der Aktor-Einheit (1) in Verbindung steht, wobei das Steuerventil in einer Ventilplatte (5) ausgebildet ist,
dadurch gekennzeichnet,
dass das Steuerventil (2) einen verlängerten Ventilbolzen (6) mit einem außerhalb der Ventilplatte (5) liegenden Abschnitt aufweist, der einen in einer Kopplerhülse (7) geführten Ventilkolben (8) der hydraulischen Kopplereinheit (3) ausbildet und mit der Kopplerhülse (7) und dem Einstellstück (4) einen Druckraum (9) 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 an arranged between the actuator unit and control valve hydraulic coupler unit (3) via an adjusting piece (4) with the Actuator unit (1) is in communication, wherein the control valve is formed in a valve plate (5),
characterized,
that the control valve (2) comprises an elongated valve pin (6) with an outside of the valve plate (5) situated portion forms the guided one in a coupler sleeve (7) the valve piston (8) of the hydraulic coupler (3) and (with the coupler sleeve 7 ) and the adjusting piece (4) delimits a pressure chamber (9). Kraftstoffinjektor nach Anspruch 1, dadurch gekennzeichnet, dass die Kopplerhülse (7) mittels eines Federelementes (10), vorzugsweise einer Schraubenfeder oder einer Federhülse, gegen das Einstellstück (4) vorgespannt ist.Fuel injector according to claim 1, characterized in that the coupler sleeve (7) by means of a spring element (10), preferably a coil spring or a spring sleeve, is biased against the adjusting piece (4). Kraftstoffinjektor nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kopplerhülse (7) auf der dem Federelement (10) zugewandten Oberseite einen axial zurückspringenden Absatz (11) zur Auflage des Federelementes (10) besitzt.Fuel injector according to claim 1 or 2, characterized in that the coupler sleeve (7) on the spring element (10) facing upper side has an axially recessed paragraph (11) for supporting the spring element (10). Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die an dem Einstellstück (4) dichtend anliegende Fläche der Kopplerhülse (7) mit einer Beißkante (12) versehen ist.Fuel injector according to one of the preceding claims, characterized in that on the adjusting piece (4) sealingly fitting surface of the coupler sleeve (7) is provided with a biting edge (12). Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass zwischen der Kopplerhülse (7) und dem als Ventilkolben (8) dienenden Abschnitt des Ventilbolzens (6) ein Führungsspalt (13) vorgesehen ist, der weniger als 10 µm, vorzugsweise weniger als 5 µm beträgt.Fuel injector according to one of the preceding claims, characterized in that between the coupler sleeve (7) and serving as a valve piston (8) portion of the valve pin (6) a guide gap (13) is provided which is less than 10 microns, preferably less than 5 microns is. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kopplerhülse (7) innenumfangseitig auf der dem Federelement (10) zugewandten Oberseite eine konusförmige Einführöffnung (14) zur Aufnahme des als Ventilkolben (8) dienenden Abschnitts des Ventilbolzens (6) besitzt.Fuel injector according to one of the preceding claims, characterized in that the coupler sleeve (7) on the inner circumference side on the spring element (10) facing top has a cone-shaped insertion opening (14) for receiving the valve piston (8) serving as portion of the valve pin (6). Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der als Ventilkolben (8) dienende Abschnitt des Ventilbolzens (6) in einem Bereich zumindest eine Abflachung (15) besitzt.Fuel injector according to one of the preceding claims, characterized in that the valve piston (8) serving as the section of the valve pin (6) in an area at least one flattening (15) has. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ventilbolzen (6) einen Federkragen (16) besitzt und mittels eines Federelementes (17) gegenüber einem Ventilsitz (18) vorgespannt ist.Fuel injector according to one of the preceding claims, characterized in that the valve pin (6) has a spring collar (16) and is biased by a spring element (17) relative to a valve seat (18). Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ventilbolzen (6) an seinem dem Ventilsitz (18) abgewandten Ende in einer Hülse (19) geführt ist, wobei der Ventilbolzen (6), die Hülse (19) und die Ventilplatte (5) einen Niederdruckraum (20) begrenzen.Fuel injector according to one of the preceding claims, characterized in that the valve pin (6) is guided at its end remote from the valve seat (18) in a sleeve (19), wherein the valve pin (6), the sleeve (19) and the valve plate ( 5) limit a low-pressure space (20).
EP10151027A 2009-03-04 2010-01-19 Fuel injector Not-in-force EP2226490B1 (en)

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DE102009001322A DE102009001322A1 (en) 2009-03-04 2009-03-04 fuel injector

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EP2226490B1 EP2226490B1 (en) 2011-12-28

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DE102010043360A1 (en) 2010-11-04 2012-05-10 Robert Bosch Gmbh fuel injector

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004024282A1 (en) * 2004-05-15 2005-12-01 Robert Bosch Gmbh Pump-nozzle unit for internal combustion engine has control valve operated by hydraulic intensifier with first intensifying piston provided with blind hole in which is guided and sealed second intensifying piston
EP1900932A2 (en) * 2006-09-11 2008-03-19 Robert Bosch Gmbh Device for injecting fuel
DE102006062217A1 (en) * 2006-12-22 2008-06-26 Robert Bosch Gmbh Fuel injector operating method for e.g. diesel engine, involves separating pressure and/or flow forces such that switching forces from piezoactuator is reduced, where actuator has pulling and pushing operating phases during its operation
DE102007047426A1 (en) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Injector with piezo actuator

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004024282A1 (en) * 2004-05-15 2005-12-01 Robert Bosch Gmbh Pump-nozzle unit for internal combustion engine has control valve operated by hydraulic intensifier with first intensifying piston provided with blind hole in which is guided and sealed second intensifying piston
EP1900932A2 (en) * 2006-09-11 2008-03-19 Robert Bosch Gmbh Device for injecting fuel
DE102006042601A1 (en) 2006-09-11 2008-03-27 Robert Bosch Gmbh Injector for injecting fuel
DE102006062217A1 (en) * 2006-12-22 2008-06-26 Robert Bosch Gmbh Fuel injector operating method for e.g. diesel engine, involves separating pressure and/or flow forces such that switching forces from piezoactuator is reduced, where actuator has pulling and pushing operating phases during its operation
DE102007047426A1 (en) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Injector with piezo actuator

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