EP2201240B1 - Injector - Google Patents

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Publication number
EP2201240B1
EP2201240B1 EP08803438A EP08803438A EP2201240B1 EP 2201240 B1 EP2201240 B1 EP 2201240B1 EP 08803438 A EP08803438 A EP 08803438A EP 08803438 A EP08803438 A EP 08803438A EP 2201240 B1 EP2201240 B1 EP 2201240B1
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EP
European Patent Office
Prior art keywords
control
valve element
control valve
injector
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.)
Active
Application number
EP08803438A
Other languages
German (de)
French (fr)
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EP2201240A1 (en
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication of EP2201240A1 publication Critical patent/EP2201240A1/en
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Publication of EP2201240B1 publication Critical patent/EP2201240B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced 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
    • F02M63/0077—Valve seat details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • the EP 1 612 403 A1 is a common rail injector with a pressure balanced in the axial direction control valve known.
  • the control valve By means of the control valve, the fuel pressure can be influenced within a limited by an injection valve element control chamber.
  • the injection valve element By varying the fuel pressure within the control chamber, the injection valve element is adjusted between an open position and a closed position, wherein the injection valve element releases the fuel flow into the combustion chamber of an internal combustion engine in its open position.
  • the control valve has an axially adjustable by means of an electromagnetic actuator, sleeve-shaped control valve member which cooperates with a control valve seat.
  • the control valve seat is formed on a plate member from which extends integrally formed therewith a guide pin in the axial direction and passes through the sleeve-shaped control valve element.
  • a disadvantage of the known injector is that the arranged at the foot of the guide pin control valve seat is difficult to produce due to its poor accessibility.
  • the invention has for its object to provide an injector with a control valve, the control valve seat is easily manufacturable, and avoided in the strength problems, even at low control valve seat diameters.
  • the invention is based on the idea within the sleeve-shaped control valve element to arrange a pressure pin for receiving the fuel pressure acting in the axial direction and to form this pressure pin as a separate component of the equipped with the control valve seat component.
  • the pressure pin serves as a guide element for the sleeve-shaped control valve element or that additionally or alternatively an outer guide for guiding the sleeve-shaped control valve element is provided on its outer periphery.
  • control valve seat formed in this way, angular errors can be compensated similarly to a spherical control valve seat, but an outer cone as a control valve seat can be manufactured comparatively easily and can be detected well by measurement. Due to the separate formation of pressure pin and the component with control valve seat, the control valve seat is easily accessible, so that the control valve seat is easily manufacturable. In addition, the control valve seat and the guide for the sleeve-shaped control valve element can be processed separately due to the arrangement of different components. By combining a designed as an outer cone control valve seat with a separate pressure pin so easy to be manufactured injector is created, which can be formed in a simple manner pressure balanced in the axial direction.
  • the sleeve-shaped Control valve element advantageously has a high radial rigidity in its end facing the seating area.
  • the control valve seat formed as an outer cone generates centering forces by which the control valve element can be optimally centered to the control valve seat.
  • control valve more precisely the control valve element, as in its closed position in the axial direction pressure compensated component is formed.
  • the sleeve-shaped control valve element is seated with its inner circumference on the control valve designed as an outer cone, so that a linear sealing surface is obtained without pressure step.
  • the outer cone of the control valve seat has an outer cone angle of a value range between about 60 ° and about 80 °.
  • outer cone angle is understood to mean the angle of the outer cone surface to the longitudinal central axis of the control valve seat (outer cone).
  • the outer cone angle is selected from a range between about 70 ° and about 75 °.
  • an inner cone is provided on the cooperating with the designed as an outer cone control valve seat, adjustable in the axial direction, sleeve-shaped control valve element.
  • the inner cone angle ie the angle of the inner conical surface and the longitudinal center axis of the inner cone, is greater than the outer cone angle.
  • control valve seat of the preferably pressure-balanced control valve is inevitably subject to wear over its service life, it is advantageous to limit the actual seating area on the sleeve-shaped control valve element in the radial direction. This is surprisingly very easy to implement in a designed as an outer cone control valve seat.
  • the maximum extent of the sealing surface which increases due to wear can be limited to a maximum by limiting the end face of the control valve element facing the control valve seat by an annular, perpendicular to the longitudinal extent of the valve sleeve, ie in the radial direction, extending end face.
  • the axial distance between the annular, formed by the inner cone seat line (sealing surface) and extending in the radial direction end surface of the control valve element less than 400 .mu.m, preferably less than 300 .mu.m, more preferably less than 200 microns , is.
  • the maximum end-side, radial extension of the seat line can be limited by wear to a minimum, which even in a long-time in operation injector still a high surface pressure in the investment area the sleeve-shaped control valve element leads to the control valve seat.
  • the pressure pin is designed as an inner guide element for the control valve element, that is, the control valve element is guided with its cylindrical inner circumference on the outer circumference of the pressure pin.
  • the pressure pin is fixed to, for example, a positive fit on a component which is axially spaced apart from the component having the control valve seat, or is integral therewith.
  • this component is a plate on which an electromagnet arrangement of an electromagnetic actuator is supported in the axial direction.
  • the pressure pin passes through this electromagnet arrangement in the axial direction.
  • an embodiment of the injector can be realized in which an external guide for the control valve element is provided, the control valve element is thus guided on its outer circumference.
  • the pressure pin is formed as an independent component, which in switched off the internal combustion engine to the the control valve seat having component rests and is supported when pressurized on an axially disposed of this component component.
  • the injector with pressure pin and outer conical control valve seat is an injector with an electromagnetic actuator for actuating the control valve.
  • Fig. 1 a designed as a common-rail injector injector 1 for injecting fuel in a combustion chamber of an internal combustion engine of a motor vehicle is shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored.
  • the injector 1 is connected via other, not shown, injectors via a supply line 5.
  • a return line 8 a low-pressure region 9 of the injector 1 is connected to the storage container 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 to flow.
  • an injector body 10 Within an injector body 10 is a control rod 11 of an existing in this embodiment of the control rod 11 and a nozzle needle 12 injection valve element 13 is arranged.
  • the control rod 11 of the injection valve element 13 is guided longitudinally displaceably in a lower portion of the sleeve-shaped component 14.
  • the control rod 11 In a lying on low pressure chamber 15, which is arranged in the plane of the drawing axially below the pressure chamber 6 and sealed with a sealing element 16 with respect to this, the control rod 11 is located with its lower end face on an upper end side of the nozzle needle 12 which is axially displaceable within a Nozzle body 18 is guided.
  • the nozzle body 18 is screwed by means of a union nut, not shown, with the injector body 10.
  • the low-pressure chamber 15 is connected via a channel 19 with connected to the low pressure region 9 of the injector.
  • the injection valve element 13 has a diameter stage 42 (low pressure stage), whereby a fast closing behavior of the injector 1 is ensured.
  • the nozzle needle 12 has at its tip 20 a closing surface 21, with which the nozzle needle 12, so the injection valve element 13, in close contact with an injection valve member seat 22 formed within the nozzle body 18 can be brought.
  • a control chamber 26 is limited, via a radially in the sleeve-shaped portion of Component 14 extending inlet throttle 27 is supplied with high-pressure fuel from the pressure chamber 6.
  • the control chamber 26 is above, in the upper, plate-shaped portion of the component 14 arranged drain channel 28 with outlet throttle 29 connected to a valve chamber 30 which is bounded radially outwardly by a sleeve-shaped control valve element 31 of a control valve 32 (servo valve).
  • fuel can flow into the low-pressure region 9 of the injector 1 when the control valve element 31 which can be actuated by an electromagnetic actuator 33 is lifted off its control valve seat 34, which is designed as an outer cone and arranged on the plate-shaped section of the component 14, ie the control valve 32 is open.
  • the flow cross sections of the inlet throttle 27 and the outlet throttle 28 are matched to one another such that when the control valve 32 is open, a net outflow of fuel (control quantity) from the control chamber 26 via the valve chamber 30 into the low pressure region 9 of the injector 1 and from there via the return line 8 takes place in the reservoir 3.
  • the control valve 32 is designed as a pressure balanced in the axial direction in the closed state valve, wherein the control valve member 31 in its upper plane in the plane of the drawing in one piece with an anchor plate 35 which cooperates with an electromagnet assembly 36 of the actuator 33 is formed.
  • a control closing spring 40 which is supported on a component 41 designed as an injector cover, moves the sleeve-shaped control valve element 31 back onto its outer conical control valve seat 34 on the upper side of the component 14 in the drawing plane.
  • the fuel flowing in through the inlet throttle 27 increases the pressure in the cylinder Control chamber 26 rapidly, whereby the control rod 11 and subsequently the nozzle needle 12, supported by the spring force of a closing spring 38, which is supported on a circumferential collar 39 of the control rod 11, is moved in the direction of the injection valve member seat 22, whereby the fuel flow from the nozzle hole arrangement 23 is interrupted in the combustion chamber.
  • a pressure pin 43 is received, which receives the pressure forces acting in the axial direction within the valve chamber 30 and the valve chamber 30 seals in the axial direction in the plane of the drawing upwards.
  • the pressure pin 43 is supported on the component 41 arranged by the component 14, for which purpose the pressure pin 43 passes through the electromagnet arrangement 36 of the actuator 33 in the axial direction.
  • the pressure pin 43 drops and lies on the top of the outer conical control valve seat 34 until the pressure builds up again.
  • a guide plate 44 (outer guide) is provided, which is the Control valve element 31 leads at its outer periphery.
  • the loose pressure pin 43 designed as a separate component has no guiding function, but serves only to absorb pressure forces acting in the axial direction.
  • an axial passage 45 is provided to the fuel flow within the low pressure region to an armature space 46 and from there via a central, penetrated by the pressure pin 43 opening 51, in which the control closing spring 40 is arranged to ensure the return line 8 ,
  • the control valve member 31 has a radially inner cone 47 located inside. From this, a seat line 48 (sealing line) is formed on the inner circumference, by means of which the control valve element 31 cooperates with the control valve seat 34. How out Fig. 2 it can be seen, an inner cone angle ⁇ of the inner cone 47 is greater than an outer cone angle ⁇ of the outer cone-shaped control valve seat 34th
  • Radially to the inner cone 47 includes an end face 49 of the control valve element 31 on the front side.
  • the distance A between the seat line 48 and the annular end surface 50 is less than 200 microns in the embodiment shown.
  • the perpendicular to the longitudinal central axis L of the control valve seat 34 extending end surface 49 limits the wear-increasing, maximum extension of the seat line 48, whereby a sufficiently high surface pressure is ensured even after a long period of operation.
  • control closing spring 40 is supported on the one hand on the control valve element 31 and on the other an annular shoulder 50 of the pressure pin 43 and presses it against the serving as a lid member 41st
  • Fig. 2 includes radially outward of the flat, extending in the radial direction end surface 49 of the control valve member 31, a radially outer chamfer portion 17 at.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, insbesondere einen Common-Rail-Injektor, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.

Aus der EP 1 612 403 A1 ist ein Common-Rail-Injektor mit einem in axialer Richtung druckausgeglichenen Steuerventil bekannt. Mittels des Steuerventils kann der Kraftstoffdruck innerhalb einer von einem Einspritzventilelement begrenzten Steuerkammer beeinflusst werden. Durch die Variation des Kraftstoffdrucks innerhalb der Steuerkammer wird das Einspritzventilelement zwischen einer Öffnungsstellung und einer Schließstellung verstellt, wobei das Einspritzventilelement in seiner Öffnungsstellung den Kraftstofffluss in den Brennraum einer Brennkraftmaschine freigibt. Das Steuerventil weist ein in axialer Richtung mittels eines elektromagnetischen Aktuators verstellbares, hülsenförmiges Steuerventilelement auf, das mit einem Steuerventilsitz zusammenwirkt. Der Steuerventilsitz ist an einem Plattenelement angeformt, von dem aus sich ein einstückig mit diesem ausgebildeter Führungsstift in axialer Richtung erstreckt und das hülsenförmige Steuerventilelement durchsetzt. Nachteilig bei dem bekannten Injektor ist es, dass der am Fuß des Führungsstiftes angeordnete Steuerventilsitz aufgrund seiner schlechten Zugänglichkeit schwer fertigbar ist. Zudem kann es aufgrund des hohen Kraftstoffdrucks in der Kraftstoffdurchführung im Führungsstift zu Festigkeitsproblemen kommen, so dass ein vergleichsweise großer Mindestdurchmesser des Führungsstiftes nicht unterschritten werden kann, was sich wiederum negativ auf die Größe des benötigten Bauraums auswirkt.From the EP 1 612 403 A1 is a common rail injector with a pressure balanced in the axial direction control valve known. By means of the control valve, the fuel pressure can be influenced within a limited by an injection valve element control chamber. By varying the fuel pressure within the control chamber, the injection valve element is adjusted between an open position and a closed position, wherein the injection valve element releases the fuel flow into the combustion chamber of an internal combustion engine in its open position. The control valve has an axially adjustable by means of an electromagnetic actuator, sleeve-shaped control valve member which cooperates with a control valve seat. The control valve seat is formed on a plate member from which extends integrally formed therewith a guide pin in the axial direction and passes through the sleeve-shaped control valve element. A disadvantage of the known injector is that the arranged at the foot of the guide pin control valve seat is difficult to produce due to its poor accessibility. In addition, due to the high fuel pressure in The fuel passage in the guide pin to strength problems come, so that a comparatively large minimum diameter of the guide pin can not be exceeded, which in turn has a negative effect on the size of the required space.

Offenbarung der ErfindungDisclosure of the invention Technische AufgabeTechnical task

Der Erfindung liegt die Aufgabe zugrunde, einen Injektor mit einem Steuerventil vorzuschlagen, dessen Steuerventilsitz einfach fertigbar ist, und bei dem Festigkeitsprobleme, auch bei geringen Steuerventilsitzdurchmessern vermieden werden.The invention has for its object to provide an injector with a control valve, the control valve seat is easily manufacturable, and avoided in the strength problems, even at low control valve seat diameters.

Technische LösungTechnical solution

Diese Aufgabe wird mit einem Injektor mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen auch sämtliche Kombinationen aus zumindest zwei von in der Beschreibung, den Ansprüchen und/oder den Figuren offenbarten Merkmalen.This object is achieved with an injector having the features of claim 1. Advantageous developments of the invention are specified in the subclaims. All combinations of at least two features disclosed in the description, the claims and / or the figures also fall within the scope of the invention.

Der Erfindung liegt der Gedanke zugrunde, innerhalb des hülsenförmigen Steuerventilelementes einen Druckstift zur Aufnahme des in axialer Richtung wirkenden Kraftstoffdruckes anzuordnen und diesen Druckstift als von dem mit dem Steuerventilsitz ausgestatteten Bauelement separates Bauteil auszubilden. Je nach gewählter, später noch zu erläuternder Ausführungsform ist es dabei denkbar, dass der Druckstift als Führungselement für das hülsenförmige Steuerventilelement dient oder dass zusätzlich oder alternativ eine Außenführung zur Führung des hülsenförmigen Steuerventilelementes an seinem Außenumfang vorgesehen ist. Insbesondere dann, wenn der Führungsstift als frei verstellbares Bauteil ausgebildet ist, ist bei einem nach dem Konzept der Erfindung ausgebildeten Injektor durch eine Verschiebung des Führungsstiftes bei der Montage ein Ausgleich von Winkelfehlern sowie ein Ausgleich eines Axialversatzes des hülsenförmigen Steuerventilelementes möglich. Theoretisch ist es denkbar, den Steuerventilsitz kugelförmig auszubilden, um eine zusätzliche Möglichkeit zu schaffen, Winkelfehler zwischen dem Steuerventilelement und dem den Ventilsitz aufweisenden Bauelement auszugleichen. Es hat sich jedoch herausgestellt, dass die Fertigung eines teilkugelförmigen Steuerventilsitzes aufwendig ist, da diese Form schwierig zu schleifen und messtechnisch zu erfassen ist. Gemäß der Erfindung ist daher vorgesehen, den separaten Druckstift mit einem als Außenkonus ausgebildeten Steuerventilsitz zu kombinieren. Mit einem derart ausgeformten Steuerventilsitz lassen sich ähnlich wie bei einem kugelförmigen Steuerventilsitz Winkelfehler ausgleichen, jedoch ist ein Außenkonus als Steuerventilsitz vergleichsweise einfach fertigbar und messtechnisch gut erfassbar. Aufgrund der separaten Ausbildung von Druckstift und dem Bauelement mit Steuerventilsitz ist der Steuerventilsitz gut zugänglich, so dass der Steuerventilsitz auf einfache Weise fertigbar ist. Zudem können der Steuerventilsitz und die Führung für das hülsenförmige Steuerventilelement aufgrund der Anordnung an unterschiedlichen Bauteilen getrennt voneinander bearbeitet werden. Durch die Kombination von einem als Außenkonus ausgebildeten Steuerventilsitz mit einem separaten Druckstift wird also ein einfach zu fertigender Injektor geschaffen, der auf einfache Weise in axialer Richtung druckausgeglichen ausgebildet werden kann. Das hülsenförmige Steuerventilelement weist in seinem dem Sitzbereich zugewandten Ende mit Vorteil eine hohe radiale Steifigkeit auf. Zudem erzeugt der als Außenkegel ausgebildete Steuerventilsitz zentrierende Kräfte durch die das Steuerventilelement optimal zum Steuerventilsitz zentrierbar ist.The invention is based on the idea within the sleeve-shaped control valve element to arrange a pressure pin for receiving the fuel pressure acting in the axial direction and to form this pressure pin as a separate component of the equipped with the control valve seat component. Depending on the selected, later to be explained embodiment, it is conceivable that the pressure pin serves as a guide element for the sleeve-shaped control valve element or that additionally or alternatively an outer guide for guiding the sleeve-shaped control valve element is provided on its outer periphery. In particular, when the guide pin is designed as a freely adjustable component, in a trained according to the concept of the invention injector by displacement of the guide pin during assembly, a compensation of angular errors and a compensation of an axial displacement of the sleeve-shaped control valve element is possible. Theoretically, it is conceivable to form the control valve seat spherical, in order to provide an additional possibility to compensate for angular errors between the control valve member and the valve seat having the component. However, it has been found that the production of a part-spherical control valve seat is expensive, since this form is difficult to grind and to detect metrologically. According to the invention, it is therefore provided to combine the separate pressure pin with a designed as an outer cone control valve seat. With a control valve seat formed in this way, angular errors can be compensated similarly to a spherical control valve seat, but an outer cone as a control valve seat can be manufactured comparatively easily and can be detected well by measurement. Due to the separate formation of pressure pin and the component with control valve seat, the control valve seat is easily accessible, so that the control valve seat is easily manufacturable. In addition, the control valve seat and the guide for the sleeve-shaped control valve element can be processed separately due to the arrangement of different components. By combining a designed as an outer cone control valve seat with a separate pressure pin so easy to be manufactured injector is created, which can be formed in a simple manner pressure balanced in the axial direction. The sleeve-shaped Control valve element advantageously has a high radial rigidity in its end facing the seating area. In addition, the control valve seat formed as an outer cone generates centering forces by which the control valve element can be optimally centered to the control valve seat.

Von besonderem Vorteil ist eine Ausführungsform bei der das Steuerventil, genauer das Steuerventilelement, als in seiner Schließstellung in axialer Richtung druckausgeglichenes Bauteil ausgebildet ist. Dies kann beispielsweise dadurch realisiert werden, dass das hülsenförmige Steuerventilelement mit seinem Innenumfang am als Außenkonus ausgebildeten Steuerventil aufsitzt, so dass eine linienförmige Dichtfläche ohne Druckstufe erhalten wird.Of particular advantage is an embodiment in which the control valve, more precisely the control valve element, as in its closed position in the axial direction pressure compensated component is formed. This can be realized, for example, in that the sleeve-shaped control valve element is seated with its inner circumference on the control valve designed as an outer cone, so that a linear sealing surface is obtained without pressure step.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass der Außenkonus des Steuerventilsitzes einen Außenkonuswinkel aus einem Wertebereich zwischen etwa 60° und etwa 80° aufweist. Unter Außenkonuswinkel wird dabei der Winkel der Außenkonusfläche zur Längsmittelachse des Steuerventilsitzes (Außenkonus) verstanden. Bevorzugt wird der Außenkonuswinkel aus einem Bereich zwischen etwa 70° und etwa 75° gewählt.In a further development of the invention is advantageously provided that the outer cone of the control valve seat has an outer cone angle of a value range between about 60 ° and about 80 °. Under outer cone angle is understood to mean the angle of the outer cone surface to the longitudinal central axis of the control valve seat (outer cone). Preferably, the outer cone angle is selected from a range between about 70 ° and about 75 °.

Von besonderem Vorteil ist eine Ausführungsform, bei der an dem mit dem als Außenkonus ausgebildeten Steuerventilsitz zusammenwirkenden, in axialer Richtung verstellbaren, hülsenförmigen Steuerventilelement ein Innenkonus vorgesehen ist. Bevorzugt ist dabei der Innenkonuswinkel, also der Winkel der inneren Konusfläche und der Längsmittelachse des Innenkonus, größer als der Außenkonuswinkel. Hierdurch wird zum einen eine ring- und linienförmige Dichtfläche realisiert.Of particular advantage is an embodiment in which an inner cone is provided on the cooperating with the designed as an outer cone control valve seat, adjustable in the axial direction, sleeve-shaped control valve element. Preferably, the inner cone angle, ie the angle of the inner conical surface and the longitudinal center axis of the inner cone, is greater than the outer cone angle. As a result, on the one hand, a ring-shaped and linear sealing surface is realized.

Da der Steuerventilsitz des vorzugsweise druckausgeglichenen Steuerventils zwangsläufig über seine Lebensdauer einem Verschleiß unterliegt, ist es vorteilhaft, den eigentlichen Sitzbereich an dem hülsenförmigen Steuerventilelement in radialer Richtung zu begrenzen. Dies ist bei einem als Außenkonus ausgebildeten Steuerventilsitz überraschenderweise sehr einfach realisierbar. Die maximale Erstreckung der sich durch Verschleiß vergrößernden Dichtfläche kann auf ein Maximalmaß begrenzt werden, indem die dem Steuerventilsitz zugewandte Stirnseite des Steuerventilelementes von einer radial außerhalb des Innenkonus liegenden, ringförmigen, sich senkrecht zur Längserstreckung der Ventilhülse, also in radialer Richtung erstreckenden Endfläche begrenzt wird. Dadurch, dass die maximale Größe der sich durch Verschleiß vergrößernden Dichtfläche zwischen Steuerventilelement und Steuerventilsitz begrenzt ist, ist auch ein Mindestmaß an Flächenpressung im Dichtbereich des Steuerventilelementes garantiert, was wiederum dazu führt, dass die Dichtheit des Steuerventilelementes über die Lebensdauer des Injektors sichergestellt ist.Since the control valve seat of the preferably pressure-balanced control valve is inevitably subject to wear over its service life, it is advantageous to limit the actual seating area on the sleeve-shaped control valve element in the radial direction. This is surprisingly very easy to implement in a designed as an outer cone control valve seat. The maximum extent of the sealing surface which increases due to wear can be limited to a maximum by limiting the end face of the control valve element facing the control valve seat by an annular, perpendicular to the longitudinal extent of the valve sleeve, ie in the radial direction, extending end face. Due to the fact that the maximum size of the sealing surface enlarging due to wear between control valve element and control valve seat is limited, a minimum of surface pressure in the sealing region of the control valve element is guaranteed, which in turn results in the tightness of the control valve element being ensured over the service life of the injector.

Besonders bevorzugt ist eine Ausführungsform, bei der der axiale Abstand zwischen der ringförmigen, von dem Innenkonus gebildeten Sitzlinie (Dichtfläche) und der sich in radialer Richtung erstreckenden Endfläche des Steuerventilelementes weniger als 400 µm, bevorzugt weniger als 300 µm, besonders bevorzugt weniger als 200 µm, beträgt. Hierdurch kann die maximale stirnseitige, radiale Erstreckung der Sitzlinie durch Verschleiß auf ein Mindestmaß begrenzt werden, was auch bei einem bereits lange im Betrieb befindlichen Injektor noch zu einer hohen Flächenpressung im Anlagebereich des hülsenförmigen Steuerventilelementes am Steuerventilsitz führt.Particularly preferred is an embodiment in which the axial distance between the annular, formed by the inner cone seat line (sealing surface) and extending in the radial direction end surface of the control valve element less than 400 .mu.m, preferably less than 300 .mu.m, more preferably less than 200 microns , is. As a result, the maximum end-side, radial extension of the seat line can be limited by wear to a minimum, which even in a long-time in operation injector still a high surface pressure in the investment area the sleeve-shaped control valve element leads to the control valve seat.

Bezüglich der Anordnung und Ausbildung des Druckstiftes gibt es, wie eingangs erwähnt, unterschiedliche Möglichkeiten. So ist es beispielsweise denkbar, dass der Druckstift als inneres Führungselement für das Steuerventilelement ausgebildet ist, also das Steuerventilelement mit seinem zylindrischen Innenumfang am Außenumfang des Druckstiftes geführt ist. Hierzu ist es notwendig, den Druckstift fest innerhalb des Injektors zu positionieren. Dies kann beispielsweise dadurch realisiert werden, dass der Druckstift an einem von dem den Steuerventilsitz aufweisenden Bauelement in axialer Richtung beabstandeten Bauteil, beispielsweise formschlüssig, festgelegt oder einstückig mit diesem ist. Beispielsweise handelt es sich bei diesem Bauteil um eine Platte an der sich eine Elektromagnetanordnung eines elektromagnetischen Aktuators in axialer Richtung abstützt. Bevorzugt durchsetzt der Druckstift dabei diese Elektromagnetanordnung in axialer Richtung. Alternativ ist es denkbar, das Führungselement mittels einer Feder in axialer Richtung gegen ein Bauteil, welches in axialer Richtung von dem den Steuerventilsitz aufweisenden Bauelement beabstandet ist, mit einer Federkraft zu beaufschlagen.With regard to the arrangement and design of the pressure pin there are, as mentioned above, different possibilities. Thus, it is conceivable, for example, that the pressure pin is designed as an inner guide element for the control valve element, that is, the control valve element is guided with its cylindrical inner circumference on the outer circumference of the pressure pin. For this purpose it is necessary to position the pressure pin firmly inside the injector. This can be realized, for example, in that the pressure pin is fixed to, for example, a positive fit on a component which is axially spaced apart from the component having the control valve seat, or is integral therewith. For example, this component is a plate on which an electromagnet arrangement of an electromagnetic actuator is supported in the axial direction. Preferably, the pressure pin passes through this electromagnet arrangement in the axial direction. Alternatively, it is conceivable to apply a spring force to the guide element by means of a spring in the axial direction against a component which is spaced apart in the axial direction from the component having the control valve seat.

Zusätzlich oder bevorzugt alternativ zu der Ausbildung des Druckstiftes als inneres Führungselement kann eine Ausführungsform des Injektors realisiert werden, bei der eine Außenführung für das Steuerventilelement vorgesehen ist, das Steuerventilelement also an seinem Außenumfang geführt ist. Bei einer derartigen Ausführungsform ist es von Vorteil, wenn der Druckstift als eigenständiges Bauteil ausgebildet ist, welches bei abgeschalteter Brennkraftmaschine an dem den Steuerventilsitz aufweisenden Bauelement aufliegt und sich bei Druckbeaufschlagung an einem axial von diesem Bauelement angeordneten Bauteil abstützt.Additionally or preferably as an alternative to the embodiment of the pressure pin as an inner guide element, an embodiment of the injector can be realized in which an external guide for the control valve element is provided, the control valve element is thus guided on its outer circumference. In such an embodiment, it is advantageous if the pressure pin is formed as an independent component, which in switched off the internal combustion engine to the the control valve seat having component rests and is supported when pressurized on an axially disposed of this component component.

Bevorzugt handelt es sich bei dem Injektor mit Druckstift und außenkonischem Steuerventilsitz um einen Injektor mit einem elektromagnetischen Aktuator zur Betätigung des Steuerventils.Preferably, the injector with pressure pin and outer conical control valve seat is an injector with an electromagnetic actuator for actuating the control valve.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen. Diese zeigen in:

Fig. 1
eine schematische Darstellung eines Injektors mit einem Steuerventil, dessen hülsenförmiges Steuerventilelement von einem separaten Druckstift durchsetzt ist, wobei das Steuerventilelement mit einem als Außenkonus ausgebildeten Ventilsitz zusammenwirkend ausgebildet und angeordnet ist und
Fig.2
eine schematische Darstellung eines Ausschnittes eines alternativ ausgebildeten Injektors.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings. These show in:
Fig. 1
a schematic representation of an injector with a control valve, the sleeve-shaped control valve element is penetrated by a separate pressure pin, wherein the control valve element is formed and arranged cooperating with a formed as an outer cone valve seat and
Fig.2
a schematic representation of a section of an alternative trained injector.

Ausführungsformen der ErfindungEmbodiments of the invention

In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.

In Fig. 1 ist ein als Common-Rail-Injektor ausgebildeter Injektor 1 zum Einspritzen von Kraftstoff in einem Brennraum einer Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Eine Hochdruckpumpe 2 fördert Kraftstoff aus einem Vorratsbehälter 3 in einen Kraftstoff-Hochdruckspeicher 4 (Rail). In diesem ist Kraftstoff, insbesondere Diesel oder Benzin, unter hohem Druck, von in diesem Ausführungsbeispiel etwa 2000 bar, gespeichert. An den Kraftstoff-Hochdruckspeicher 4 ist der Injektor 1 neben anderen, nicht gezeigten Injektoren über eine Versorgungsleitung 5 angeschlossen. Die Versorgungsleitung 5 mündet zum einen in einen Druckraum 6 sowie in einen in der Zeichnungsebene unteren Düsenraum 7. Mittels einer Rücklaufleitung 8 ist ein Niederdruckbereich 9 des Injektors 1 an den Vorratsbehälter 3 angeschlossen. Über die Rücklaufleitung 8 kann eine später noch zu erläuternde Steuermenge an Kraftstoff von dem Injektor 1 zu dem Vorratsbehälter 3 abfließen.In Fig. 1 a designed as a common-rail injector injector 1 for injecting fuel in a combustion chamber of an internal combustion engine of a motor vehicle is shown. A high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored. To the high-pressure fuel accumulator 4, the injector 1 is connected via other, not shown, injectors via a supply line 5. By means of a return line 8, a low-pressure region 9 of the injector 1 is connected to the storage container 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 to flow.

Innerhalb eines Injektorkörpers 10 ist eine Steuerstange 11 eines in diesem Ausführungsbeispiel aus Steuerstange 11 und einer Düsennadel 12 bestehenden Einspritzventilelementes 13 angeordnet. Die Steuerstange 11 des Einspritzventilelementes 13 ist längsverschieblich in einem unteren Abschnitt des hülsenförmigen Bauelements 14 geführt. In einem auf Niederdruck liegenden Raum 15, der in der Zeichnungsebene axial unterhalb des Druckraums 6 angeordnet und mit einem Dichtelement 16 gegenüber diesem abgedichtet ist, liegt die Steuerstange 11 mit ihrer unteren Stirnseite an einer oberen Stirnseite der Düsennadel 12 an, die axial verschieblich innerhalb eines Düsenkörpers 18 geführt ist. Der Düsenkörper 18 ist mittels einer nicht dargestellten Überwurfmutter mit dem Injektorkörper 10 verschraubt. Der auf Niederdruck liegende Raum 15 ist über einen Kanal 19 mit dem Niederdruckbereich 9 des Injektors verbunden. Innerhalb des auf Niederdruck liegenden Raumes 15 weist das Einspritzventilelement 13 eine Durchmesserstufe 42 (Niederdruckstufe) auf, wodurch ein schnelles Schließverhalten des Injektors 1 sichergestellt wird.Within an injector body 10 is a control rod 11 of an existing in this embodiment of the control rod 11 and a nozzle needle 12 injection valve element 13 is arranged. The control rod 11 of the injection valve element 13 is guided longitudinally displaceably in a lower portion of the sleeve-shaped component 14. In a lying on low pressure chamber 15, which is arranged in the plane of the drawing axially below the pressure chamber 6 and sealed with a sealing element 16 with respect to this, the control rod 11 is located with its lower end face on an upper end side of the nozzle needle 12 which is axially displaceable within a Nozzle body 18 is guided. The nozzle body 18 is screwed by means of a union nut, not shown, with the injector body 10. The low-pressure chamber 15 is connected via a channel 19 with connected to the low pressure region 9 of the injector. Within the low-pressure chamber 15, the injection valve element 13 has a diameter stage 42 (low pressure stage), whereby a fast closing behavior of the injector 1 is ensured.

Die Düsennadel 12 weist an ihrer Spitze 20 eine Schließfläche 21 auf, mit welcher die Düsennadel 12, also das Einspritzventilelement 13, in dichter Anlage an einen innerhalb des Düsenkörpers 18 ausgebildeten Einspritzventilelementsitz 22 bringbar ist.The nozzle needle 12 has at its tip 20 a closing surface 21, with which the nozzle needle 12, so the injection valve element 13, in close contact with an injection valve member seat 22 formed within the nozzle body 18 can be brought.

Wenn das Einspritzventilelement 13 an seinem Einspritzventilelementsitz 22 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 23 gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz 22 abgehoben, kann Kraftstoff aus dem Düsenraum 7 über einen in einem unteren Bereich zwischen Düsennadel 12 und Düsenkörper 18 ausgebildeten Ringraum 24 an dem Einspritzventilelementsitz 22 vorbei zur Düsenlochanordnung 23 strömen und dort im Wesentlichen unter Hochdruck (Raildruck) stehend in einen Brennraum gespritzt werden.When the injection valve member 13 abuts its injection valve member seat 22, i. is in a closed position, the fuel outlet from a nozzle hole arrangement 23 is locked. On the other hand, if it is lifted off its injection valve element seat 22, fuel can flow from the nozzle chamber 7 past the injection valve element seat 22 to the nozzle hole arrangement 23 via an annular space 24 formed in a lower region between the nozzle needle 12 and the nozzle body 18 and stand there substantially at high pressure (rail pressure) to spray a combustion chamber.

Von einer oberen Stirnseite 25 der Steuerstange 11 des Einspritzventilelementes 13, welches neben der gezeigten mehrteiligen Ausführung auch einteilig ausbildbar ist, und dem in der Zeichnungsebene unteren, hülsenförmigen Abschnitt des Bauelementes 14 wird eine Steuerkammer 26 begrenzt, die über eine radial in dem hülsenförmigen Abschnitt des Bauelementes 14 verlaufende Zulaufdrossel 27 mit unter Hochdruck stehendem Kraftstoff aus dem Druckraum 6 versorgt wird. Die Steuerkammer 26 ist über einen, in dem oberen, plattenförmigen Abschnitt des Bauelementes 14 angeordneten Ablaufkanal 28 mit Ablaufdrossel 29 mit einer Ventilkammer 30 verbunden, die radial außen von einem hülsenförmigen Steuerventilelement 31 eines Steuerventils 32 (ServoVentil) begrenzt ist. Aus dieser kann Kraftstoff in den Niederdruckbereich 9 des Injektors 1 strömen, wenn das von einem elektromagnetischen Aktuator 33 betätigbare Steuerventilelement 31 von seinem als Außenkonus ausgebildeten und an dem plattenförmigen Abschnitt des Bauelementes 14 angeordneten Steuerventilsitzes 34 abgehoben, d.h. das Steuerventil 32 geöffnet ist. Die Durchflussquerschnitte der Zulaufdrossel 27 und der Ablaufdrossel 28 sind dabei derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 32 ein Nettoabfluss von Kraftstoff (Steuermenge) aus der Steuerkammer 26 über die Ventilkammer 30 in den Niederdruckbereich 9 des Injektors 1 und von dort aus über die Rücklaufleitung 8 in den Vorratsbehälter 3 erfolgt.From an upper end face 25 of the control rod 11 of the injection valve element 13, which is also integrally formed in addition to the multi-part design shown, and the lower in the drawing plane, sleeve-shaped portion of the component 14, a control chamber 26 is limited, via a radially in the sleeve-shaped portion of Component 14 extending inlet throttle 27 is supplied with high-pressure fuel from the pressure chamber 6. The control chamber 26 is above, in the upper, plate-shaped portion of the component 14 arranged drain channel 28 with outlet throttle 29 connected to a valve chamber 30 which is bounded radially outwardly by a sleeve-shaped control valve element 31 of a control valve 32 (servo valve). From this, fuel can flow into the low-pressure region 9 of the injector 1 when the control valve element 31 which can be actuated by an electromagnetic actuator 33 is lifted off its control valve seat 34, which is designed as an outer cone and arranged on the plate-shaped section of the component 14, ie the control valve 32 is open. The flow cross sections of the inlet throttle 27 and the outlet throttle 28 are matched to one another such that when the control valve 32 is open, a net outflow of fuel (control quantity) from the control chamber 26 via the valve chamber 30 into the low pressure region 9 of the injector 1 and from there via the return line 8 takes place in the reservoir 3.

Das Steuerventil 32 ist als im geschlossenen Zustand in axialer Richtung druckausgeglichenes Ventil ausgebildet, wobei das Steuerventilelement 31 in seinem in der Zeichnungsebene oberen Abschnitt einstückig mit einer Ankerplatte 35, die mit einer Elektromagnetanordnung 36 des Aktuators 33 zusammenwirkt, ausgebildet ist. Werden Elektromagnete 37 des elektromagnetischen Aktuators 33 bestromt, hebt das hülsenförmige Steuerventilelement 31 von seinem außenkonischen Steuerventilsitz 34 ab, wodurch der Druck innerhalb der Steuerkammer 26 rapide abfällt und sich die Steuerstange 11 in axialer Richtung in der Zeichnungsebene nach oben in die Steuerkammer 26 hineinbewegt, wodurch auch die Düsennadel 12 aufgrund des Kraftstoffdrucks innerhalb des Düsenraums 7 in der Zeichnungsebene nach oben in Richtung in den auf Niederdruck liegenden Raum 15 hinein bewegt wird und in der Folge der Kraftstoff aus dem Düsenraum 7 in den Brennraum strömen kann.The control valve 32 is designed as a pressure balanced in the axial direction in the closed state valve, wherein the control valve member 31 in its upper plane in the plane of the drawing in one piece with an anchor plate 35 which cooperates with an electromagnet assembly 36 of the actuator 33 is formed. When electromagnets 37 of the electromagnetic actuator 33 are energized, the sleeve-shaped control valve member 31 lifts from its outer conical control valve seat 34, whereby the pressure within the control chamber 26 drops rapidly and the control rod 11 in the axial direction in the drawing plane moves up into the control chamber 26, whereby Also, the nozzle needle 12 moves due to the fuel pressure within the nozzle chamber 7 in the drawing plane upwards in the direction of the low-pressure chamber 15 into it is and in the sequence of fuel from the nozzle chamber 7 can flow into the combustion chamber.

Zur Beendigung des Einspritzvorgangs wird die Bestromung der Elektromagneten 37 des Aktuators 33 unterbrochen. Eine Steuerschließfeder 40, die sich an einem als Injektordeckel ausgebildeten Bauteil 41 abstützt, bewegt das hülsenförmige Steuerventilelement 31 zurück auf seinen außenkonischen Steuerventilsitz 34 an der in der Zeichnungsebene oberen Seite des Bauelementes 14. Durch den durch die Zulaufdrossel 27 nachströmenden Kraftstoff steigt der Druck in der Steuerkammer 26 rapide an, wodurch die Steuerstange 11 und in der Folge die Düsennadel 12, unterstützt durch die Federkraft einer Schließfeder 38, die sich an einem Umfangsbund 39 der Steuerstange 11 abstützt, in Richtung des Einspritzventilelementsitzes 22 bewegt wird, wodurch der Kraftstofffluss aus der Düsenlochanordnung 23 in den Brennraum unterbrochen wird.To end the injection process, the energization of the electromagnet 37 of the actuator 33 is interrupted. A control closing spring 40, which is supported on a component 41 designed as an injector cover, moves the sleeve-shaped control valve element 31 back onto its outer conical control valve seat 34 on the upper side of the component 14 in the drawing plane. The fuel flowing in through the inlet throttle 27 increases the pressure in the cylinder Control chamber 26 rapidly, whereby the control rod 11 and subsequently the nozzle needle 12, supported by the spring force of a closing spring 38, which is supported on a circumferential collar 39 of the control rod 11, is moved in the direction of the injection valve member seat 22, whereby the fuel flow from the nozzle hole arrangement 23 is interrupted in the combustion chamber.

Innerhalb des Steuerventilelementes 31 ist ein Druckstift 43 aufgenommen, der die in axialer Richtung wirkenden Druckkräfte innerhalb der Ventilkammer 30 aufnimmt und die Ventilkammer 30 in axialer Richtung in der Zeichnungsebene nach oben abdichtet. Der Druckstift 43 stützt sich dabei an dem von dem Bauelement 14 angeordneten Bauteil 41 ab, wozu der Druckstift 43 die Elektromagnetanordnung 36 des Aktuators 33 in axialer Richtung durchsetzt. Bei abgeschalteter Brennkraftmaschine sinkt der Druckstift 43 ab und liegt bis zum erneuten Druckaufbau an der Oberseite des außenkonischen Steuerventilsitzes 34 auf.Within the control valve element 31, a pressure pin 43 is received, which receives the pressure forces acting in the axial direction within the valve chamber 30 and the valve chamber 30 seals in the axial direction in the plane of the drawing upwards. The pressure pin 43 is supported on the component 41 arranged by the component 14, for which purpose the pressure pin 43 passes through the electromagnet arrangement 36 of the actuator 33 in the axial direction. When the internal combustion engine is switched off, the pressure pin 43 drops and lies on the top of the outer conical control valve seat 34 until the pressure builds up again.

Zur Führung des hülsenförmigen Steuerventilelementes 31 ist eine Führungsplatte 44 (Außenführung) vorgesehen, die das Steuerventilelement 31 an seinem Außenumfang führt. Hierdurch hat der als separates Bauteil ausgebildete, lose Druckstift 43 keinerlei Führungsfunktion, sondern dient nur zur Aufnahme in axialer Richtung wirkender Druckkräfte. In der Führungsplatte 44 ist ein Axialkanal 45 vorgesehen, um den Kraftstofffluss innerhalb des Niederdruckbereichs zu einem Ankerraum 46 und von dort aus über eine zentrische, von dem Druckstift 43 durchsetzte Öffnung 51, in der auch die Steuerschließfeder 40 angeordnet ist, zur Rücklaufleitung 8 zu gewährleisten.To guide the sleeve-shaped control valve element 31, a guide plate 44 (outer guide) is provided, which is the Control valve element 31 leads at its outer periphery. As a result, the loose pressure pin 43 designed as a separate component has no guiding function, but serves only to absorb pressure forces acting in the axial direction. In the guide plate 44, an axial passage 45 is provided to the fuel flow within the low pressure region to an armature space 46 and from there via a central, penetrated by the pressure pin 43 opening 51, in which the control closing spring 40 is arranged to ensure the return line 8 ,

Wie insbesondere aus Fig. 2 ersichtlich ist, die ein leicht abgewandeltes Ausführungsbeispiel bzw. einen Ausschnitt aus diesem zeigt, weist das Steuerventilelement 31 einen radial innen gelegenen Innenkonus 47 auf. Von diesem wird am Innenumfang eine Sitzlinie 48 (Dichtlinie) gebildet, mittels der das Steuerventilelement 31 mit dem Steuerventilsitz 34 zusammenwirkt. Wie aus Fig. 2 ersichtlich ist, ist ein Innenkonuswinkel α des Innenkonus 47 größer als ein Außenkonuswinkel β des außenkonusförmigen Steuerventilsitzes 34.As in particular from Fig. 2 It can be seen that shows a slightly modified embodiment or a section of this, the control valve member 31 has a radially inner cone 47 located inside. From this, a seat line 48 (sealing line) is formed on the inner circumference, by means of which the control valve element 31 cooperates with the control valve seat 34. How out Fig. 2 it can be seen, an inner cone angle α of the inner cone 47 is greater than an outer cone angle β of the outer cone-shaped control valve seat 34th

Radial an den Innenkonus 47 schließt eine stirnseitige Endfläche 49 des Steuerventilelementes 31 an. Der Abstand A zwischen der Sitzlinie 48 und der ringförmigen Endfläche 50 beträgt in dem gezeigten Ausführungsbeispiel weniger als 200 µm. Die sich senkrecht zur Längsmittelachse L des Steuerventilsitzes 34 erstreckende Endfläche 49 begrenzt die sich durch Verschleiß vergrößernde, maximale Erstreckung der Sitzlinie 48, wodurch eine ausreichend hohe Flächenpressung auch nach einer langen Betriebszeit gewährleistet ist.Radially to the inner cone 47 includes an end face 49 of the control valve element 31 on the front side. The distance A between the seat line 48 and the annular end surface 50 is less than 200 microns in the embodiment shown. The perpendicular to the longitudinal central axis L of the control valve seat 34 extending end surface 49 limits the wear-increasing, maximum extension of the seat line 48, whereby a sufficiently high surface pressure is ensured even after a long period of operation.

Im Gegensatz zu dem Ausführungsbeispiel gemäß Fig. 1 dient der Druckstift 43 in dem Ausführungsbeispiel gemäß Fig. 2 als innere Führung für das hülsenförmige Steuerventilelement 31. Um dies zu gewährleisten, stützt sich die Steuerschließfeder 40 zum einen an dem Steuerventilelement 31 und zum anderen an einer Ringschulter 50 des Druckstiftes 43 ab und presst diesen so gegen das als Deckel dienende Bauteil 41.In contrast to the embodiment according to Fig. 1 serves the push pin 43 in the embodiment according to Fig. 2 as an inner guide for the sleeve-shaped control valve element 31. To ensure this, the control closing spring 40 is supported on the one hand on the control valve element 31 and on the other an annular shoulder 50 of the pressure pin 43 and presses it against the serving as a lid member 41st

Wie aus Fig. 2 zu erkennen ist, schließt radial außen an die ebene, in radialer Richtung sich erstreckende Endfläche 49 des Steuerventilelementes 31 ein radial äußerer Fasenabschnitt 17 an.How out Fig. 2 can be seen, includes radially outward of the flat, extending in the radial direction end surface 49 of the control valve member 31, a radially outer chamfer portion 17 at.

Claims (10)

  1. Injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, having an injection-valve element (13) which can be adjusted between a closed position and an open position which releases the fuel flow, which injection-valve element (13) can be actuated by means of a control valve (32) which has a sleeve-shaped control-valve element (31), the control-valve element (31) interacting with a control-valve seat (34) which is arranged on a component (14), and the control-valve seat (34) being configured as an outer cone, characterized in that a pressure pin (43) is provided which is enclosed by the control-valve element (31) and is separate from the component (14).
  2. Injector according to Claim 1, characterized in that the control valve (32) is configured so as to be pressure-equalized in the axial direction in the closed state.
  3. Injector according to either of Claims 1 and 2, characterized in that the outer cone has an outer cone angle (α) from a range between approximately 60° and approximately 80°, preferably between approximately 70° and approximately 75°.
  4. Injector according to one of the preceding claims, characterized in that the control-valve element (31) has an inner cone which opens in the direction of the control-valve seat (34).
  5. Injector according to Claim 4, characterized in that the outer cone angle (β) is smaller than the inner cone angle (α).
  6. Injector according to one of the preceding claims, characterized in that the control-valve element (31) is delimited on the seat side by an end face (49) which is annular and extends perpendicularly with respect to the longitudinal extent of the control-valve element (31).
  7. Injector according to one of the preceding claims, characterized in that the axial spacing (A) of a seat line (48) which is formed by the inner cone from the annular end face (49) is less than 400 µm, preferably less than 300 µm, particularly preferably less than 200 µm.
  8. Injector according to one of the preceding claims, characterized in that the pressure pin (43) serves as inner guide element for the control-valve element (31) and is fixed on a structural part (41), which is spaced apart from the component (14) which has the control-valve seat (34), or is configured integrally with it or is spring-loaded against it or is supported on it in the case of pressure loading.
  9. Injector according to one of the preceding claims, characterized in that the control-valve element (31) is guided on its outer circumference.
  10. Injector according to one of the preceding claims, characterized in that an electromagnetic actuator (33) is provided for actuating the control valve (32).
EP08803438A 2007-09-17 2008-09-01 Injector Active EP2201240B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710044356 DE102007044356A1 (en) 2007-09-17 2007-09-17 injector
PCT/EP2008/061455 WO2009037097A1 (en) 2007-09-17 2008-09-01 Injector

Publications (2)

Publication Number Publication Date
EP2201240A1 EP2201240A1 (en) 2010-06-30
EP2201240B1 true EP2201240B1 (en) 2012-12-19

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EP (1) EP2201240B1 (en)
DE (1) DE102007044356A1 (en)
WO (1) WO2009037097A1 (en)

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DE102007044356A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh injector
DE102009027932A1 (en) * 2009-07-22 2011-01-27 Robert Bosch Gmbh Fuel injector and fuel injection system
DE102009046563A1 (en) * 2009-11-10 2011-05-12 Robert Bosch Gmbh fuel injector
DE102010003202A1 (en) 2010-03-24 2011-09-29 Robert Bosch Gmbh Common rail injector with pressure compensated switching valve and additional storage volume
DE102011077618A1 (en) 2011-06-16 2012-12-20 Robert Bosch Gmbh Injector, in particular fuel injector for an internal combustion engine
DE102011078346A1 (en) * 2011-06-29 2013-01-03 Robert Bosch Gmbh Switching valve, method for manufacturing a switching valve and fuel injector with a switching valve
DE102011078407A1 (en) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Switching valve for controlling a fuel injector and fuel injector
DE102011079999A1 (en) 2011-07-28 2013-01-31 Robert Bosch Gmbh Injector e.g. fuel injector of common-rail injection system used for compression-ignition internal combustion engine, has several additional channels that are embedded in valve section of valve
DE102017207880A1 (en) * 2017-05-10 2018-11-15 Robert Bosch Gmbh fuel injector

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WO2008138743A1 (en) * 2007-05-14 2008-11-20 Robert Bosch Gmbh Injector
WO2009016003A1 (en) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Fuel injection valve with improved tightness on the sealing seat of a pressure-compensated control valve
WO2009037097A1 (en) * 2007-09-17 2009-03-26 Robert Bosch Gmbh Injector
WO2009037095A1 (en) * 2007-09-17 2009-03-26 Robert Bosch Gmbh Control valve for a fuel injector

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DE602004004254T2 (en) 2004-06-30 2007-07-12 C.R.F. S.C.P.A. Servo valve for controlling an injection valve of an internal combustion engine
DE102006021741A1 (en) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve

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EP1967727A2 (en) * 2007-03-08 2008-09-10 Robert Bosch Gmbh Fuel injector with improved implementation of a control valve for controlling an injection needle
WO2008138743A1 (en) * 2007-05-14 2008-11-20 Robert Bosch Gmbh Injector
WO2009016003A1 (en) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Fuel injection valve with improved tightness on the sealing seat of a pressure-compensated control valve
WO2009037097A1 (en) * 2007-09-17 2009-03-26 Robert Bosch Gmbh Injector
WO2009037095A1 (en) * 2007-09-17 2009-03-26 Robert Bosch Gmbh Control valve for a fuel injector

Also Published As

Publication number Publication date
DE102007044356A1 (en) 2009-03-19
EP2201240A1 (en) 2010-06-30
WO2009037097A1 (en) 2009-03-26

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