EP2499352B1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
EP2499352B1
EP2499352B1 EP10762649.1A EP10762649A EP2499352B1 EP 2499352 B1 EP2499352 B1 EP 2499352B1 EP 10762649 A EP10762649 A EP 10762649A EP 2499352 B1 EP2499352 B1 EP 2499352B1
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EP
European Patent Office
Prior art keywords
valve
guide
valve element
valve seat
fuel injector
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
EP10762649.1A
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German (de)
French (fr)
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EP2499352A1 (en
Inventor
Nadja Eisenmenger
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
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Robert Bosch GmbH
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Publication date
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Publication of EP2499352A1 publication Critical patent/EP2499352A1/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
    • 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
    • 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
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber in an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1, as he from DE 10 2006 020 724 A1 the applicant is known.
  • Hub-controlled fuel injectors are known with designed as a solenoid valve or piezoelectric valve control valve for controlling the pressure in a limited by an axially adjustable injection valve element control chamber.
  • the newest control valves are designed to be pressure-balanced, that is to say such that in the closed state in the axial direction the forces that are as small as possible, or preferably no forces at all, act in the axial direction.
  • the use of pressure compensated control valves allows smaller spring forces, small actuator forces, smaller control valve strokes and thus faster switching times. Due to the faster switching times, the multiple injection capability can be significantly improved.
  • the present invention seeks to further develop a fuel injector with a control valve according to the preamble of claim 1, that an improved tightness in extreme positions of the valve element is achieved, at the same time a comparatively inexpensive guide for the valve element feasible should be.
  • the invention is based on the consideration that in practice it can be assumed that during operation of the fuel injector on the valve element of the control valve Transverse forces act that cause the valve member to contact the guide at any point at any time.
  • two extreme positions are conceivable, namely, on the one hand, a fully tilted position, in which the valve element rests on an upper annular edge of the guide and the other on the opposite side to a lower annular edge of the guide and a second extreme position, wherein the valve element within the guide is moved completely parallel and abuts an axially extending line on the guide.
  • the invention further proceeds from the assumption that the lateral forces acting on the valve element, in particular the transverse forces of a valve spring acting on the valve element, act in such a way that the first alternative (first extreme position or position) is more likely, namely that the valve element is more full tilted lying in the guide and it will be based on the one hand at the top of the guide and the other on the opposite side at the bottom of the guide.
  • control valve for the first extreme position ie the fully tilted valve element is to be optimized, preferably such that the valve element on the valve seat does not even have to slip to cooperate sealingly with the valve seat, but already in the fully tilted Position (first extreme position) seals.
  • the invention achieves this by, inter alia, realizing the guide for the valve element and the geometric configuration and arrangement of the valve seat such that a fictitious pivot point of the valve seat is located within the axial extent of the guide. This is intended to ensure that this fictitious, later to be explained pivot point of the valve seat and the pivot point of the valve element, which is arranged on the axial center of the guide, as close as possible. This can be achieved in practice by adjusting the position and position of the valve guide to the seat angle and seat diameter.
  • the aforementioned, fictitious pivot point of the valve seat is defined formed by the center of an imaginary circle, in a the longitudinal central axis of the valve element receiving longitudinal section the valve seat, preferably two-angularly extending surface portions of the Valve seat each touched selectively, preferably such that the imaginary circle cuts none of the seats.
  • This in turn is based on the assumption that the, preferably conical, valve seat at small tilt angles of less than 1 ° approximately behaves like a ball.
  • the imaginary circle is thus under this assumption the turning circle on which the valve element moves during tilting.
  • the invention assumes that the valve seat is able to close a certain gap via a valve spring force and the elasticity of the material, so that the tightness of the control valve can be ensured in all extreme positions in the inventive arrangement of the fictitious pivot point of the valve seat.
  • valve seat and the guide are arranged stationary relative to each other in the fuel injector.
  • the object is also achieved with a second alternative, this differs from the first alternative only in that here the imaginary circle touches the sealing element formed on the valve element punctually in two spaced points (preferably does not cut the sealing area) and that the center of this Circle is a fictitious, imaginary pivot point of the sealing region of the valve element.
  • the sealing area and the guide are fixed relative to each other, which can be realized by the fact that the sealing area and the guide are formed by the valve element.
  • the assumption applies that the imaginary circle is the turning circle on which the valve element moves when tilted in the closed state, ie when the sealing area abuts on the valve seat.
  • the sealing region in the second alternative is designed as an inner or outer cone and in the longitudinal sectional view of the fuel injector two spaced, line-shaped sealing area surface sections each form a tangent to the imaginary circle.
  • the center of the imaginary, the valve seat at two spaced apart points each selectively touching and preferably the seat not cutting intersecting circle, i. the fictitious pivot point of the valve seat as close as possible to the axial center, i. the fulcrum of the valve element in the first extreme position (abutment on the upper guide edge and bearing on the opposite lower guide edge) is arranged.
  • the distance between the center of the circle and the axial center of the guide less than 40% of the axial guide length, in particular less than 30%, preferably less than 20%, more preferably less than 10%, most preferably less than 5 %.
  • the second alternative for the imaginary circle which contacts the sealing region at two points and which preferably does not intersect the sealing surface.
  • the center of the imaginary circle is half the guide length, i. is arranged in the axial center of the guide and thus preferably coincides with the previously mentioned several times pivot point of the valve element in the first extreme position.
  • the midpoint be at an axial height of the guide intermediate between the axial center and the valve seat facing the end of the guide is located.
  • the center of the imaginary circle (in the first or second alternative) is arranged on a longitudinal central axis of the guide.
  • Each cone has an inner cone side and an outer cone side, wherein inner cone-shaped valve seats or sealing regions with their inner cone side sealingly cooperate with the valve element and outer cone valve seats orphasekonusdicht Schemee with their outer cone side. It is particularly expedient if the axial guide for the valve element is arranged on the inner cone side of the valve seat or sealing area, irrespective of whether the valve seat or sealing area is an outer cone or an inner cone.
  • control valve in the closed state is designed as an axially pressure compensated valve.
  • the valve element is formed as a sleeve, which defines radially inwardly a hydraulically connected to the control chamber valve chamber, which is connected to the low pressure region when the control valve is open.
  • bolt-shaped control valve elements axially pressure-balanced by the aforementioned valve chamber is provided in the manner of an annular groove on the outer circumference of the bolt.
  • Fig. 1 is designed as a common rail injector fuel injector 1 for injecting fuel into a combustion chamber of an internal combustion engine, not shown, of a motor vehicle highly schematized and only partially 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, under high pressure, of about 2000bar in this embodiment, stored.
  • the fuel injector 1 is connected, among other fuel injectors, not shown, via a supply line 5.
  • the supply line 5 opens into a pressure chamber 6.
  • a return line 7 a low-pressure region 8 of the fuel injector 1 is connected to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the fuel injector 1 to the reservoir 3 to flow.
  • a one-part or multi-part injection valve element 9 is arranged axially adjustable.
  • the injection valve element 9 has at a tip (not shown) a closing surface with which the injection valve element 9 can be brought into tight engagement with an injection valve element seat (not shown) within a nozzle body.
  • a control chamber 13 (servo chamber) is limited, via a introduced in the sleeve 12 inlet throttle 14 under high pressure fuel from the pressure chamber. 6 is supplied.
  • the control chamber 10 is connected via a drain passage 15 with outlet throttle 16 (drain passage 15 and outlet throttle 16 is located within the throttle plate 11) with a valve chamber 17 which is bounded radially outwardly by a sleeve-shaped valve element 18 (control valve member) of a control valve 19.
  • a drain passage 15 with outlet throttle 16 drain passage 15 and outlet throttle 16 is located within the throttle plate 11
  • valve chamber 17 which is bounded radially outwardly by a sleeve-shaped valve element 18 (control valve member) of a control valve 19.
  • fuel can flow into the low-pressure region 8 of the fuel injector when the actuatable by an electromagnetic actuator valve member 18 of its designed as an inner cone and arranged on the throttle plate 11 valve seat 20 (control valve seat) lifted, ie the control valve 19 is opened.
  • the flow cross sections of the inlet throttle 14 and the outlet throttle 15 are matched to one another such that when open control valve 19, a net outflow of fuel (control amount) from the control chamber 13 via the valve chamber 17 in the low pressure region 8 of the fuel injector 1 and from there via the return line 7 into the reservoir. 3 results.
  • the control valve 19 is formed in the embodiment shown as a pressure-balanced valve in the axial direction in the closed state, wherein the valve member 18 is integrally connected in its upper portion with an anchor plate, not shown, which cooperates with an electromagnetic actuator, not shown.
  • an electromagnetic actuator not shown.
  • valve spring closing spring
  • a bolt 22 which has the task of sealing the valve chamber 17 in the axial direction upwards.
  • the diameter of the bolt 22 corresponds at least approximately to the diameter of the annular sealing line, with which the valve element 18 cooperates with the inner cone-shaped valve seat 20.
  • the valve member 18 is at its outer periphery in a circular contoured guide bore 23, the guide 24 for the valve element 18 forms, guided.
  • the guide 24 has the axial length L.
  • An imaginary circle 26 is arranged in the shown, the longitudinal central axis L receiving longitudinal sectional plane such that it contacts the valve seat 20 in two radially spaced points P 1 and P 2 punctually, wherein the circle 26 does not intersect the valve seat 20.
  • Two spaced, an inner cone angle ⁇ enclosing valve seat surface portions 27, 28 each form a tangent to the circle 26, so that the radius r s of the circle 26 at the points P 1 and P 2 perpendicular to the valve seat 20, more precisely on the valve seat surface portions 27, 28, stands.
  • ⁇ + 2 ⁇ 180 °, wherein the angle ⁇ is the slope angle at which the valve seat surface sections 27, 28 is inclined to a transversely to the longitudinal central axis L extending plane.
  • the center M of the previously described circle 26 is within the axial extent of the guide 24, in the embodiment shown even on the longitudinal central axis L.
  • the center M, ie a fictitious pivot point of the valve seat 20 coincides with the axial center 25 of the guide 24,
  • the axial center 25 is a pivot point of the valve element 18 in a first extreme position, in which the valve element 18 on the one an upper annular edge 29 of the guide 24 and on the other, rests on the opposite side to a lower annular edge 30 of the guide.
  • Fig. 2 shows an alternative embodiment of a control valve 19, wherein to avoid repetition substantially only to the differences to the embodiment according to Fig. 1 will be received. With regard to similarities, reference is made to the preceding embodiment.
  • valve element 18 is not sleeve-shaped, but is designed as a bolt which is guided in a guide 23 with the axial extension I.
  • the center M of a circle 26, the analogous to the embodiment according to Fig. 1 is arranged and as at Fig. 1 is located on the inner cone side of the valve seat 20 is disposed on the axial center (I / 2).
  • bolt-shaped valve element 18 On the outer circumference of the cylindrical, bolt-shaped valve element 18 is formed as an annular chamber valve chamber 17, flows into the obliquely outward fuel from the control chamber 13 and flows with the control valve open in the axial direction down to a low pressure region 8.
  • Fig. 3 shows a further embodiment.
  • the valve seat 20 is formed as an outer cone and the guide 23 for the bolt-shaped valve element 18 and the circuit 26 are located on the downwardly directed here mecanickonusseite the outer cone-shaped valve seat 20 which cooperates sealingly with its outer cone side with the valve element.
  • the valve seat surface portions 27, 28 form tangents on the circle 26. It can be seen that the center of the circle is disposed within the axial extent L of the guide 23 at U2, on the longitudinal center axis L of the valve element 18.
  • the valve chamber 17 is incorporated in the outer periphery of the valve element 18 in the manner of an annular groove and with open control valve 19 fuel can not as at Fig. 2 in the drawing plane down, but in the plane of the drawing up out of the valve chamber 17 out, also in a low pressure region 9 flow.
  • the embodiment according to Fig. 4 differs insofar fundamentally from the preceding embodiments, as that not the fixed valve seat but the valve element formed on, with the valve seat in the sealing position cooperating sealing region 31 is cone-shaped, here innenkonusförmig (alternatively outer cone-shaped) is formed.
  • the circle 26 is analogous to the preceding embodiments on the inner cone side of the inner cone-shaped sealing region 31 of the valve element 18 and touches the sealing area 31 at two spaced points P 1 and P 2 , sö that in the longitudinal sectional view of two inner cone angle ⁇ enclosing, line-shaped sealing area sections 32, 33 abut tangentially to the circle 26.
  • the center M of the circle 26 is located in the axial center 25 of the guide 24, which is formed in the embodiment shown by the valve member 18 and defined. With the guide 24, the valve member 18 slides axially along an axial extension 34 of the throttle plate eleventh
  • valve chamber 17 is located on the outer circumference of the extension 34 as an inner annular groove within the sleeve-shaped valve element 18th

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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)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum in einer Brennkraftmaschine, insbesondere ein Common-Rail-Injektor, gemäß dem Oberbegriff des Anspruchs 1, wie er aus der DE 10 2006 020 724 A1 der Anmelderin bekannt ist.The invention relates to a fuel injector for injecting fuel into a combustion chamber in an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1, as he from DE 10 2006 020 724 A1 the applicant is known.

Zur Einbringung von Kraftstoff in direkt einspritzende Dieselmotoren werden zurzeit hubgesteuerte Common-Rail-Systeme eingesetzt. Vorteilhaft ist dabei, dass der Einspritzdruck unabhängig ist von Last und Drehzahl. Bekannt sind hubgesteuerte Kraftstoffinjektoren mit als Magnetventil oder Piezoventil ausgebildetem Steuerventil zur Steuerung des Druckes in einer von einem axial verstellbaren Einspritzventilelement begrenzten Steuerkammer. Neuste Steuerventile werden dabei druckausgeglichen ausgebildet, also derart, dass im geschlossenen Zustand in axialer Richtung möglichst geringe oder bevorzugt gar keine Kräfte in axialer Richtung wirken. Der Einsatz von druckausgeglichenen Steuerventilen ermöglicht kleinere Federkräfte, kleine Aktuatorkräfte, kleinere Steuerventilhübe und somit schnellere Schaltzeiten. Durch die schnelleren Schaltzeiten kann die Mehrfacheinspritzfähigkeit wesentlich verbessert werden.Currently, stroke-controlled common-rail systems are used to introduce fuel into direct-injection diesel engines. It is advantageous that the injection pressure is independent of load and speed. Hub-controlled fuel injectors are known with designed as a solenoid valve or piezoelectric valve control valve for controlling the pressure in a limited by an axially adjustable injection valve element control chamber. The newest control valves are designed to be pressure-balanced, that is to say such that in the closed state in the axial direction the forces that are as small as possible, or preferably no forces at all, act in the axial direction. The use of pressure compensated control valves allows smaller spring forces, small actuator forces, smaller control valve strokes and thus faster switching times. Due to the faster switching times, the multiple injection capability can be significantly improved.

Bekannt ist es ferner, bei Steuerventilen von Kraftstoffinjektoren innen- oder außenkonusförmige Ventilsitze vorzusehen. Damit das axial verstellbare Ventilelement des Steuerventils in geschlossenem Zustand immer sicher mittels seines Dichtbereichs den ihm zugeordneten Ventilsitz abdichtet, muss die Führung des Ventilelementes bei bekannten Kraftstoffinjektoren mit höchster Genauigkeit und engem Paarungsspiel gefertigt werden. Dies ist vor allem dann der Fall, wenn der Sitzwinkel des innen- oder außenkonusförmigen Sitzes relativ flach zwischen etwa 120° und etwa 180° gewählt wird. Mit größer werdendem Ventilsitzwinkel werden die selbstzentrierenden Kräfte, die auf das Steuerventilelement wirken kleiner- je flacher der Sitzwinkel desto kleiner ist nämlich die Hangabtriebskraft, die das Ventilelement zur Mitte hin rutschen lässt.It is also known to provide internal or external cone-shaped valve seats in control valves of fuel injectors. In order for the axially adjustable valve element of the control valve in the closed state always to securely seal the valve seat assigned to it by means of its sealing area, the guide of the valve element must be manufactured in known fuel injectors with maximum accuracy and close mating play. This is especially the case when the seat angle of the inner or outer cone-shaped seat is chosen relatively flat between about 120 ° and about 180 °. With increasing valve seat angle the smaller the seat angle, the smaller the slope force that causes the valve element to slip towards the center.

Gegenüber kleineren zentrierenden Kräften haben flache Sitzwinkel jedoch den Vorteil, dass das Steuerventilelement beim Einschlag in den Ventilsitz weniger Schlupf hat und damit weniger Verschleiß auftritt. Es muss jedoch sichergestellt sein, dass das Steuerventilelement eng und präzise geführt ist. Da jedoch enge und hochpräzise Führungen für das Steuerventilelement nur kostenintensiv herstellbar sind, bestehen Bestrebungen einen Kompromiss zwischen maximaler Dichtheit und minimalem Verschleiß einzugehen.However, in comparison to smaller centering forces, flat seating angles have the advantage that the control valve element has less slippage when it is impacted in the valve seat and thus less wear occurs. However, it must be ensured that the control valve element is tight and precise. However, since tight and high-precision guides for the control valve element can only be produced costly, efforts are made to compromise between maximum tightness and minimal wear.

Bei der eingangs zitierten DE 10 2006 020 724 A1 der Anmelderin findet ein kugelförmiges Schließelement Verwendung, bei dem ein Mittelpunkt eines gedachten Kreises außerhalb der axialen Führungslänge der Führung des Ventilelements angeordnet ist, wobei der Kreis in einer eine Längsmittelachse des Ventilelementes des Steuerventils aufnehmenden Längsschnittebene des Kraftstoffinjektors den mit dem Ventilsitz zusammenwirkenden Dichtbereich des Ventilelementes in zwei beabstandeten Punkten jeweils punktuell berührt.In the cited above DE 10 2006 020 724 A1 the Applicant finds a spherical closure element use, in which a center of an imaginary circle outside the axial guide length of the guide of the valve element is arranged, wherein the circle in a longitudinal center axis of the valve element of the control valve receiving longitudinal sectional plane of the fuel injector cooperating with the valve seat sealing region of the valve element in two spaced points each touched punctually.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem vorgenannten Stand der Technik liegt der Erfindung die Aufgabe zugrunde einen Kraftstoffinjektor mit einem Steuerventil nach dem Oberbegriff des Anspruchs 1 derart weiter zu bilden, dass eine verbesserte Dichtheit in Extremlagen des Ventilelements erzielt wird, wobei gleichzeitig eine vergleichsweise kostengünstige Führung für das Ventilelement realisierbar sein soll.Based on the aforementioned prior art, the present invention seeks to further develop a fuel injector with a control valve according to the preamble of claim 1, that an improved tightness in extreme positions of the valve element is achieved, at the same time a comparatively inexpensive guide for the valve element feasible should be.

Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.This object is achieved with the features of claim 1. Advantageous developments of the invention are specified in the subclaims.

Die Erfindung geht von der Überlegung aus, dass in der Praxis davon auszugehen ist, dass im Betrieb des Kraftstoffinjektors auf das Ventilelement des Steuerventils Querkräfte wirken, die dazu führen, dass das Ventilelement zu jeder Zeit an zumindest irgendeiner Stelle die Führung berührt. Dabei sind zwei Extremlagen denkbar, nämlich zum einen eine voll verkippte Stellung, bei der das Ventilelement zum einen an einer oberen Ringkante der Führung und zum anderen auf der gegenüberliegenden Seite an einer unteren Ringkante der Führung anliegt und eine zweite Extremlage, bei der das Ventilelement innerhalb der Führung komplett parallel verschoben ist und an einer sich axial erstreckenden Linie an der Führung anliegt. Die Erfindung geht weiter von der Annahme aus, dass die auf das Ventilelement wirkenden Querkräfte, insbesondere die Querkräfte einer auf das Ventilelement wirkenden Ventilfeder derart wirken, dass die erste Alternative (erste Extremlage bzw. -position) wahrscheinlicher ist, nämlich dass das Ventilelement eher voll verkippt in der Führung liegen und sich dabei zum einen am obersten Ende der Führung und zum anderen auf der gegenüberliegenden Seite am untersten Ende der Führung abstützen wird.The invention is based on the consideration that in practice it can be assumed that during operation of the fuel injector on the valve element of the control valve Transverse forces act that cause the valve member to contact the guide at any point at any time. In this case, two extreme positions are conceivable, namely, on the one hand, a fully tilted position, in which the valve element rests on an upper annular edge of the guide and the other on the opposite side to a lower annular edge of the guide and a second extreme position, wherein the valve element within the guide is moved completely parallel and abuts an axially extending line on the guide. The invention further proceeds from the assumption that the lateral forces acting on the valve element, in particular the transverse forces of a valve spring acting on the valve element, act in such a way that the first alternative (first extreme position or position) is more likely, namely that the valve element is more full tilted lying in the guide and it will be based on the one hand at the top of the guide and the other on the opposite side at the bottom of the guide.

Hieraus kann gefolgert werden, dass das Steuerventil für die erste Extremlage, also dem voll verkippten Ventilelement zu optimieren ist, vorzugsweise derart, dass das Ventilelement auf dem Ventilsitz erst gar nicht verrutschen muss, um dichtend mit dem Ventilsitz zusammenzuwirken, sondern bereits in der voll verkippten Position (erste Extremlage) abdichtet.It can be concluded from this that the control valve for the first extreme position, ie the fully tilted valve element is to be optimized, preferably such that the valve element on the valve seat does not even have to slip to cooperate sealingly with the valve seat, but already in the fully tilted Position (first extreme position) seals.

Die Erfindung erreicht dies, indem unter anderem die Führung für das Ventilelement und die geometrische Ausgestaltung und Anordnung des Ventilsitzes derart realisiert werden, dass ein fiktiver Drehpunkt des Ventilsitzes innerhalb der Axialerstreckung der Führung lokalisiert ist. Hierdurch soll erreicht werden, dass dieser fiktive, später noch zu erläuternde Drehpunkt des Ventilsitzes und der Drehpunkt des Ventilelementes, welcher auf der axialen Mitte der Führung angeordnet ist, möglichst nahe zusammenrücken. Dies kann in der Praxis dadurch erreicht werden, dass die Lage und die Position der Ventilführung auf den Sitzwinkel und den Sitzdurchmesser abgestimmt werden.The invention achieves this by, inter alia, realizing the guide for the valve element and the geometric configuration and arrangement of the valve seat such that a fictitious pivot point of the valve seat is located within the axial extent of the guide. This is intended to ensure that this fictitious, later to be explained pivot point of the valve seat and the pivot point of the valve element, which is arranged on the axial center of the guide, as close as possible. This can be achieved in practice by adjusting the position and position of the valve guide to the seat angle and seat diameter.

Der zuvor erwähnte, fiktive Drehpunkt des Ventilsitzes wird definitionsgemäß gebildet von dem Mittelpunkt eines gedachten Kreises, der in einem die Längsmittelachse des Ventilelementes aufnehmenden Längsschnittabschnitt den Ventilsitz, vorzugsweise zweiwinklig zueinander verlaufende Flächenabschnitte des Ventilsitzes jeweils punktuell berührt, vorzugsweise derart, dass der gedachte Kreis keine der Sitzflächen schneidet. Dem liegt wiederum die Annahme zugrunde, dass sich der, vorzugsweise konische, Ventilsitz bei kleinen Kippwinkeln von weniger als 1° annähernd wie eine Kugel verhält. Der gedachte Kreis ist also unter dieser Annahme der Drehkreis, auf dem sich das Ventilelement beim Verkippen bewegt. Ferner geht die Erfindung davon aus, dass der Ventilsitz über eine Ventilfederkraft und die Materialelastizität in der Lage ist einen gewissen Spalt zu verschließen, wodurch bei erfindungsgemäßer Anordnung des fiktiven Drehpunktes des Ventilsitzes die Dichtheit des Steuerventils in allen Extremlagen gewährleistet werden kann.The aforementioned, fictitious pivot point of the valve seat is defined formed by the center of an imaginary circle, in a the longitudinal central axis of the valve element receiving longitudinal section the valve seat, preferably two-angularly extending surface portions of the Valve seat each touched selectively, preferably such that the imaginary circle cuts none of the seats. This in turn is based on the assumption that the, preferably conical, valve seat at small tilt angles of less than 1 ° approximately behaves like a ball. The imaginary circle is thus under this assumption the turning circle on which the valve element moves during tilting. Furthermore, the invention assumes that the valve seat is able to close a certain gap via a valve spring force and the elasticity of the material, so that the tightness of the control valve can be ensured in all extreme positions in the inventive arrangement of the fictitious pivot point of the valve seat.

Je exakter die Führung gefertigt wird, d.h. je kleiner das Führungsspiels ist, desto dichter ist das Steuerventil auch in der zweiten, parallelverschobenen Extremlage des Ventilelementes.The more accurate the guide is made, i. the smaller the guide clearance, the denser the control valve is also in the second, parallel shifted extreme position of the valve element.

Bei der zuvor diskutierten ersten Lösungsvariante, bei der die Drehachse des Ventilsitzes und der Drehpunkt des Ventilelementes in der ersten Extremlage möglichst nahe beieinander liegen, sind der Ventilsitz und die Führung ortsfest relativ zueinander im Kraftstoffinjektor angeordnet.In the first solution variant discussed above, in which the axis of rotation of the valve seat and the pivot point of the valve element in the first extreme position are as close as possible to each other, the valve seat and the guide are arranged stationary relative to each other in the fuel injector.

Die Aufgabe wird auch mit einer zweiten Alternative gelöst, diese unterscheidet sich von der ersten Alternative lediglich dadurch, dass hier der gedachte Kreis den am Ventilelement ausgebildeten Dichtbereich in zwei voneinander beabstandeten Punkten punktuell berührt (vorzugsweise den Dichtbereich nicht schneidet) und, dass der Mittelpunkt dieses Kreises ein fiktiver, gedachter Drehpunkt des Dichtbereichs des Ventilelementes ist. Bei der zweiten Alternative sind der Dichtbereich und die Führung ortsfest relativ zueinander ausgebildet, was dadurch realisiert werden kann, dass der Dichtbereich und die Führung von dem Ventilelement gebildet werden. Auch bei der zweiten Alternative gilt die Annahme, dass es sich bei dem gedachten Kreis um den Drehkreis handelt, auf dem sich das Ventilelement beim Verkippen im geschlossenen Zustand, d.h. bei der Anlage des Dichtbereichs auf dem Ventilsitz bewegt. Ganz besonders bevorzugt ist es, wenn der Dichtbereich bei der zweiten Alternative als Innen- oder Außenkonus ausgebildet ist und in der Längsschnittansicht des Kraftstoffinjektors zwei beabstandete, linienförmige Dichtbereichflächenabschnitte jeweils eine Tangente an den gedachten Kreis bilden.The object is also achieved with a second alternative, this differs from the first alternative only in that here the imaginary circle touches the sealing element formed on the valve element punctually in two spaced points (preferably does not cut the sealing area) and that the center of this Circle is a fictitious, imaginary pivot point of the sealing region of the valve element. In the second alternative, the sealing area and the guide are fixed relative to each other, which can be realized by the fact that the sealing area and the guide are formed by the valve element. In the second alternative, too, the assumption applies that the imaginary circle is the turning circle on which the valve element moves when tilted in the closed state, ie when the sealing area abuts on the valve seat. It is very particularly preferred if the sealing region in the second alternative is designed as an inner or outer cone and in the longitudinal sectional view of the fuel injector two spaced, line-shaped sealing area surface sections each form a tangent to the imaginary circle.

Erfindungsgemäß ist ferner vorgesehen, dass der Mittelpunkt des gedachten, den Ventilsitz an zwei voneinander beabstandeten Punkten jeweils punktuell berührenden und bevorzugt die Sitzfläche nicht schneidenden Kreises, d.h. der fiktive Drehpunkt des Ventilsitzes möglichst nahe an der axialen Mitte, d.h. dem Drehpunkt des Ventilelementes in der ersten Extremlage (Anlage am oberen Führungsrand und Anlage am gegenüberliegenden unteren Führungsrand) angeordnet ist. Ganz besonders bevorzugt beträgt der Abstand zwischen dem Mittelpunkt des Kreises und der axialen Mitte der Führung weniger als 40 % der axialen Führungslänge, insbesondere weniger als 30 %, bevorzugt weniger als 20 %, besonders bevorzugt weniger als 10 %, ganz besonders bevorzugt weniger als 5 %. Das gleiche gilt bei der zweiten Alternative für den den Dichtbereich an zwei Stellen punktuell berührenden und die Dichtfläche bevorzugt nicht schneidenden gedachten Kreis.According to the invention it is further provided that the center of the imaginary, the valve seat at two spaced apart points each selectively touching and preferably the seat not cutting intersecting circle, i. the fictitious pivot point of the valve seat as close as possible to the axial center, i. the fulcrum of the valve element in the first extreme position (abutment on the upper guide edge and bearing on the opposite lower guide edge) is arranged. Most preferably, the distance between the center of the circle and the axial center of the guide less than 40% of the axial guide length, in particular less than 30%, preferably less than 20%, more preferably less than 10%, most preferably less than 5 %. The same applies in the case of the second alternative for the imaginary circle which contacts the sealing region at two points and which preferably does not intersect the sealing surface.

Ganz besonders bevorzugt ist es, wenn der Mittelpunkt des gedachten Kreises (erste oder zweite Alternative) auf der halben Führungslänge, d.h. in der axialen Mitte der Führung angeordnet ist und somit bevorzugt mit dem zuvor mehrfach erwähnten Drehpunkt des Ventilelementes in der ersten Extremlage zusammenfällt.It is particularly preferred if the center of the imaginary circle (first or second alternative) is half the guide length, i. is arranged in the axial center of the guide and thus preferably coincides with the previously mentioned several times pivot point of the valve element in the first extreme position.

Für den Fall, dass der Mittelpunkt des gedachten Kreises (bei der ersten oder zweiten Alternative) axial von der axialen Mitte der Führung beabstandet ist, ist es bevorzugt, wenn sich der Mittelpunkt auf einer axialen Höhe der Führung befindet, die zwischen der axialen Mitte und dem dem Ventilsitz zugewandten Ende der Führung liegt.In the event that the center of the imaginary circle (in the first or second alternative) is axially spaced from the axial center of the guide, it is preferred that the midpoint be at an axial height of the guide intermediate between the axial center and the valve seat facing the end of the guide is located.

Besonders zweckmäßig ist es, wenn der Mittelpunkt des gedachten Kreises (bei der ersten oder zweiten Alternative) auf einer Längsmittelachse der Führung angeordnet ist.It is particularly useful if the center of the imaginary circle (in the first or second alternative) is arranged on a longitudinal central axis of the guide.

Ganz besonders zweckmäßig ist es, wenn der Konuswinkel des Ventilsitzes bzw. des Dichtbereichs, also der Winkel, der in der die Längsmittelachse des Ventilelementes aufnehmenden Längsschnittebene des Kraftstoffinjektors zwei voneinander beabstandete, schräg verlaufende, in der Schnittansicht linienförmige Ventilsitzflächenabschnitte bzw. Dichtbereichsflächenabschnitte aufspannen.It is particularly expedient if the cone angle of the valve seat or the sealing region, ie the angle, in the longitudinal axis of the valve element receiving longitudinal sectional plane of the fuel injector two spaced apart, obliquely, in the sectional view line-shaped valve seat surface sections or Dichtbereichsflächenabschnitte span.

Jeder Konus hat eine Innenkonusseite und eine Außenkonusseite, wobei innenkonusförmige Ventilsitze bzw. Dichtbereiche mit ihrer Innenkonusseite dichtend mit dem Ventilelement zusammenwirken und Außenkonusventilsitze bzw. Außenkonusdichtbereiche mit ihrer Außenkonusseite. Besonders zweckmäßig ist es, wenn die axiale Führung für das Ventilelement - unabhängig davon, ob es sich bei dem Ventilsitz bzw. Dichtbereich um einen Außenkonus oder einen Innenkonus handelt, auf der Innenkonusseite des Ventilsitzes bzw. Dichtbereichs angeordnet ist.Each cone has an inner cone side and an outer cone side, wherein inner cone-shaped valve seats or sealing regions with their inner cone side sealingly cooperate with the valve element and outer cone valve seats or Außenkonusdichtbereiche with their outer cone side. It is particularly expedient if the axial guide for the valve element is arranged on the inner cone side of the valve seat or sealing area, irrespective of whether the valve seat or sealing area is an outer cone or an inner cone.

Besonders zweckmäßig ist eine Ausführungsvariante, bei der das Steuerventil im geschlossenen Zustand, zumindest näherungsweise, als axial druckausgeglichenes Ventil ausgebildet ist. Eine Möglichkeit hierzu besteht darin, das Ventilelement als Hülse auszubilden, die radial innen eine hydraulisch mit der Steuerkammer verbundene Ventilkammer begrenzt, welche bei geöffnetem Steuerventil mit dem Niederdruckbereich verbunden ist. Es ist jedoch auch möglich bolzenförmige Steuerventilelemente axial druckausgeglichen auszubilden, indem die vorerwähnte Ventilkammer in der Art einer Ringnut am Außenumfang des Bolzens vorgesehen ist.Particularly useful is a variant in which the control valve in the closed state, at least approximately, is designed as an axially pressure compensated valve. One possibility for this is to form the valve element as a sleeve, which defines radially inwardly a hydraulically connected to the control chamber valve chamber, which is connected to the low pressure region when the control valve is open. However, it is also possible to form bolt-shaped control valve elements axially pressure-balanced by the aforementioned valve chamber is provided in the manner of an annular groove on the outer circumference of the bolt.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings.

Diese zeigen in:

Fig. 1
ein erstes Ausführungsbeispiel eines nur ausschnittsweise dargestellten Kraftstoffinjektors mit Steuerventil, bei dem das Ventilelement als Hülse ausgebildet ist und mit einem innenkonusförmigen Ventilsitz dichtend in der Schließstellung zusammenwirkt,
Fig. 2
eine alternative Ausgestaltung eines Steuerventils mit einem bolzenförmigen Ventilelement und einer am Außenumfang angeordneten Ventilkammer,
Fig. 3
ein weiteres alternatives Ausführungsbeispiel eines Steuerventils mit einem bolzenförmigen Ventilelement, welches am Außenumfang eine ringnutartige Vertiefung aufweist, die die mit der Steuerkammer verbundene Ventilkammer bildet, wobei der Ventilsitz als Außenkonus ausgebildet ist und
Fig. 4
ein weiteres alternatives Ausführungsbeispiel eines Steuerventils, bei dem das Ventilelement hülsenförmig ausgebildet ist und der gedachte Kreis einen innenkonusförmigen Dichtbereich des Ventilelementes punktuell berührt und wobei der Ventilsitz an einem axialen, in das Ventilelement hineinragenden Fortsatz einer Drosselplatte angeordnet ist und mit einer am Ventilelement ausgebildeten Führung zusammenwirkt.
These show in:
Fig. 1
a first embodiment of a fuel injector with control valve shown only partially, in which the valve element is designed as a sleeve and cooperates sealingly with an inner cone-shaped valve seat in the closed position,
Fig. 2
an alternative embodiment of a control valve with a bolt-shaped valve element and a valve disposed on the outer circumference valve chamber,
Fig. 3
a further alternative embodiment of a control valve with a bolt-shaped valve element which has an annular groove-like depression on the outer circumference, which forms the valve chamber connected to the control chamber, wherein the valve seat is formed as an outer cone and
Fig. 4
a further alternative embodiment of a control valve, in which the valve element is sleeve-shaped and the imaginary circle touches a innenkonusförmigen sealing region of the valve element punctually and wherein the valve seat is disposed on an axial, projecting into the valve element extension of a throttle plate and cooperates with a formed on the valve element guide ,

In den Figuren sind gleiche Elemente und Elemente mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, like elements and elements having the same function are denoted by the same reference numerals.

In Fig. 1 ist ein als Common-Rail-Injektor ausgebildeter Kraftstoffinjektor 1 zum Einspritzen von Kraftstoff in einen Brennraum einer nicht dargestellten Brennkraftmaschine eines Kraftfahrzeugs stark schematisiert und lediglich ausschnittsweise dargestellt. Eine Hochdruckpumpe 2 fördert Kraftstoff aus einem Vorratsbehälter 3 in einen Kraftstoff-Hochdruckspeicher 4 (Rail). In diesem ist Kraftstoff, insbesondere Diesel, unter hohem Druck, von in diesem Ausführungsbeispiel etwa 2000bar, gespeichert. An einem Kraftstoff-Hochdruckspeicher 4 ist der Kraftstoffinjektor 1 neben anderen, nicht gezeigten Kraftstoffinjektoren über eine Versorgungsleitung 5 angeschlossen. Die Versorgungsleitung 5 mündet in einem Druckraum 6. Mittels einer Rücklaufleitung 7 ist ein Niederdruckbereich 8 des Kraftstoffinjektors 1 an den Vorratsbehälter 3 angeschlossen. Über die Rücklaufleitung 8 kann eine später noch zu erläuternde Steuermenge an Kraftstoff von dem Kraftstoffinjektor 1 zu dem Vorratsbehälter 3 abfließen.In Fig. 1 is designed as a common rail injector fuel injector 1 for injecting fuel into a combustion chamber of an internal combustion engine, not shown, of a motor vehicle highly schematized and only partially 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, under high pressure, of about 2000bar in this embodiment, stored. At a fuel high-pressure accumulator 4, the fuel injector 1 is connected, among other fuel injectors, not shown, via a supply line 5. The supply line 5 opens into a pressure chamber 6. By means of a return line 7, a low-pressure region 8 of the fuel injector 1 is connected to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the fuel injector 1 to the reservoir 3 to flow.

Innerhalb eines Injektorkörpers ist ein ein- oder mehrteiliges Einspritzventilelement 9 axial verstellbar angeordnet. Das Einspritzventilelement 9 weist an einer nicht dargestellten Spitze eine Schließfläche auf, mit welcher das Einspritzventilelement 9 in dichte Anlage an einem innerhalb eines Düsenkörpers (nicht gezeigt) ausgebildeten Einspritzventilelementsitz bringbar ist.Within an injector body, a one-part or multi-part injection valve element 9 is arranged axially adjustable. The injection valve element 9 has at a tip (not shown) a closing surface with which the injection valve element 9 can be brought into tight engagement with an injection valve element seat (not shown) within a nozzle body.

Wenn das Einspritzventilelement 9 an seinem Einspritzventilelementsitz anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer nicht gezeigten Düsenlochanordnung gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz abgehoben, kann Kraftstoff aus dem Druckraum 6 durch die Düsenlochanordnung in den Brennraum der Brennkraftmaschine strömen.When the injection valve member 9 abuts against its injection valve member seat, i. is in a closed position, the fuel outlet is blocked from a nozzle hole arrangement, not shown. If, on the other hand, it is lifted from its injection valve element seat, fuel can flow from the pressure chamber 6 through the nozzle hole arrangement into the combustion chamber of the internal combustion engine.

Von einer oberen Stirnseite 10 des Einspritzventilelementes 9 und einer Federkraft belasteten, sich axial an einer Drosselplatte 11 abstützenden Hülse 12 wird eine Steuerkammer 13 (Servokammer) begrenzt, die über eine in der Hülse 12 eingebrachte Zulaufdrossel 14 mit unter Hochdruck stehendem Kraftstoff aus dem Druckraum 6 versorgt wird. Die Steuerkammer 10 ist über einen Ablaufkanal 15 mit Ablaufdrossel 16 (Ablaufkanal 15 und Ablaufdrossel 16 befindet sich innerhalb der Drosselplatte 11) mit einer Ventilkammer 17 verbunden, die radial außen von einem hülsenförmigen Ventilelement 18 (Steuerventilelement) eines Steuerventils 19 begrenzt ist. In der Darstellung gemäß Fig. 1 ist in der linken Zeichnungshälfte das Steuerventil 19 einer Schnittansicht gezeigt und in der rechten Zeichnungshälfte lediglich die Bemaßung einer später noch zu erläuternden Führung für das Ventilelement 18.From an upper end face 10 of the injection valve element 9 and a spring force loaded axially on a throttle plate 11 supporting sleeve 12, a control chamber 13 (servo chamber) is limited, via a introduced in the sleeve 12 inlet throttle 14 under high pressure fuel from the pressure chamber. 6 is supplied. The control chamber 10 is connected via a drain passage 15 with outlet throttle 16 (drain passage 15 and outlet throttle 16 is located within the throttle plate 11) with a valve chamber 17 which is bounded radially outwardly by a sleeve-shaped valve element 18 (control valve member) of a control valve 19. In the illustration according to Fig. 1 is shown in the left half of the drawing, the control valve 19 a sectional view and in the right half of the drawing only the dimension of a later still to be explained guide for the valve element 18th

Aus der Ventilkammer 17 kann Kraftstoff in den Niederdruckbereich 8 des Kraftstoffinjektors einströmen, wenn das von einem elektromagnetischen Aktuator betätigbare Ventilelement 18 von seinem als Innenkonus ausgebildeten und an der Drosselplatte 11 angeordneten Ventilsitz 20 (Steuerventilsitz) abgehoben, d.h. das Steuerventil 19 geöffnet ist. Die Durchflussquerschnitte der Zulaufdrossel 14 und der Ablaufdrossel 15 sind dabei derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 19 ein Nettoabfluss von Kraftstoff (Steuermenge) aus der Steuerkammer 13 über die Ventilkammer 17 in den Niederdruckbereich 8 des Kraftstoffinjektors 1 und von dort aus über die Rücklaufleitung 7 in den Vorratsbehälter 3 resultiert.From the valve chamber 17, fuel can flow into the low-pressure region 8 of the fuel injector when the actuatable by an electromagnetic actuator valve member 18 of its designed as an inner cone and arranged on the throttle plate 11 valve seat 20 (control valve seat) lifted, ie the control valve 19 is opened. The flow cross sections of the inlet throttle 14 and the outlet throttle 15 are matched to one another such that when open control valve 19, a net outflow of fuel (control amount) from the control chamber 13 via the valve chamber 17 in the low pressure region 8 of the fuel injector 1 and from there via the return line 7 into the reservoir. 3 results.

Das Steuerventil 19 ist im gezeigten Ausführungsbeispiel als im geschlossenen Zustand in axialer Richtung druckausgeglichenes Ventil ausgebildet, wobei das Ventilelement 18 in seinem oberen Abschnitt einstückig mit einer nicht dargestellten Ankerplatte verbunden ist, die mit einem nicht dargestellten elektromagnetischen Aktuator zusammenwirkt. Wird der Aktuator bestromt, hebt das hülsenförmige Ventilelement 18 von seinem innenkonischen Ventilsitz 20 ab, wodurch der Druck innerhalb der Steuerkammer 13 rapide abfällt und sich das Einspritzventilelement 9 in axialer Richtung in der Zeichnungsebene nach oben in die Hülse 12 hineinbewegt, wodurch das Einspritzventilelement 9 von seinem Einspritzventilelementsitz abhebt und Kraftstoff in den Brennraum strömen kann. Zum Beenden des Einspritzvorgangs wird die Bestromung des elektromagnetischen Aktuators unterbrochen und eine nicht gezeigte in axialer Richtung auf das Ventilelement 18 wirkende Schließfeder (Ventilfeder, Steuerschließfeder) bewegt das hülsenförmige Ventilelement 18 zurück auf seinen Ventilsitz 20. Durch den durch die Zulaufdrossel 17 nachströmenden Kraftstoff steigt der Druck in der Steuerkammer 13 rapide an, wodurch das Einspritzventilelement 9 unterstützt durch die Federkraft einer Schließfeder 21, die sich an einem Umfangbund (nicht dargestellt) des Einspritzventilelementes 9 abstützt, in Richtung des Einspritzventilelementsitzes bewegt wird, wodurch der Kraftstofffluss aus der Düsenlochanordnung in den Brennraum unterbrochen wird.The control valve 19 is formed in the embodiment shown as a pressure-balanced valve in the axial direction in the closed state, wherein the valve member 18 is integrally connected in its upper portion with an anchor plate, not shown, which cooperates with an electromagnetic actuator, not shown. When the actuator is energized, lifts the sleeve-shaped valve member 18 from its inner conical valve seat 20, whereby the pressure within the control chamber 13 drops rapidly and the injection valve element 9 moves in the axial direction in the drawing plane up into the sleeve 12, whereby the injection valve element 9 of lifts off its injection valve element seat and fuel can flow into the combustion chamber. To terminate the injection process, the energization of the electromagnetic actuator is interrupted and an unillustrated acting in the axial direction on the valve element 18 closing spring (valve spring, control closing spring) moves the sleeve-shaped valve member 18 back to its valve seat 20. By the inflowing through the inlet throttle 17 fuel increases Pressure in the control chamber 13 rapidly, whereby the injection valve element 9 is supported by the spring force of a closing spring 21, which is supported on a peripheral collar (not shown) of the injection valve element 9, is moved in the direction of the injection valve element seat, whereby the fuel flow from the nozzle hole arrangement in the combustion chamber is interrupted.

In das hülsenförmige Ventilelement 18 ragt von oben nach unten ein Bolzen 22 hinein, der die Aufgabe hat, die Ventilkammer 17 in axialer Richtung nach oben abzudichten. Der Durchmesser des Bolzens 22 entspricht zumindest näherungsweise dem Durchmesser der ringförmigen Dichtlinie, mit der das Ventilelement 18 mit dem innenkonusförmigen Ventilsitz 20 zusammenwirkt.In the sleeve-shaped valve member 18 protrudes from top to bottom, a bolt 22, which has the task of sealing the valve chamber 17 in the axial direction upwards. The diameter of the bolt 22 corresponds at least approximately to the diameter of the annular sealing line, with which the valve element 18 cooperates with the inner cone-shaped valve seat 20.

Wie sich aus Fig. 1 ergibt, ist das Ventilelement 18 an seinem Außenumfang in einer kreisringförmig konturierten Führungsbohrung 23, die die Führung 24 für das Ventilelement 18 bildet, geführt. Die Führung 24 weist die axiale Länge L auf. Die axiale Mitte 25 der Führung 24 liegt in dem gezeigten Ausführungsbeispiel auf einer Längsmittelachse L des Ventilelementes 18 und auf der Höhe der halben Axialerstreckung (I/2 = Ia = Ib) der Führung 24.As it turned out Fig. 1 results, the valve member 18 is at its outer periphery in a circular contoured guide bore 23, the guide 24 for the valve element 18 forms, guided. The guide 24 has the axial length L. The axial center 25 of the guide 24 is in the embodiment shown on a longitudinal central axis L of the valve element 18 and at the height of the half axial extent (I / 2 = Ia = Ib) of the guide 24th

Ein gedachter Kreis 26 ist in der gezeigten, die Längsmittelachse L aufnehmenden Längsschnittebene derart angeordnet, dass dieser den Ventilsitz 20 in zwei in radialer Richtung beabstandeten Punkten P1 und P2 punktuell berührt, wobei der Kreis 26 den Ventilsitz 20 nicht schneidet. Zwei voneinander beabstandete, einen Innenkonuswinkel β einschließende Ventilsitzflächenabschnitte 27, 28 bilden jeweils eine Tangente an den Kreis 26, so dass der Radius rs des Kreises 26 in den Punkten P1 und P2 rechtwinklig auf dem Ventilsitz 20, genauer auf den Ventilsitzflächenabschnitten 27, 28, steht. Es gilt die Beziehung β + 2α = 180°, wobei der Winkel α der Hangwinkel ist, unter dem die Ventilsitzflächenabschnitte 27, 28 zu einer quer zur Längsmittelachse L verlaufenden Ebene geneigt ist. Zu erkennen ist, dass sich der Mittelpunkt M des zuvor beschriebenen Kreises 26 innerhalb der Axialerstreckung der Führung 24, in dem gezeigten Ausführungsbeispiel sogar auf der Längsmittelachse L befindet. In dem gezeigten Ausführungsbeispiel fällt der Mittelpunkt M, also ein fiktiver Drehpunkt des Ventilsitzes 20 zusammen mit der axialen Mitte 25 der Führung 24, wobei die axiale Mitte 25 einen Drehpunkt des Ventilelementes 18 in einer ersten Extremlage darstellt, bei der das Ventilelement 18 zum einen an einer oberen Ringkante 29 der Führung 24 und zum anderen, auf der gegenüberliegenden Seite an einer unteren Ringkante 30 der Führung anliegt.An imaginary circle 26 is arranged in the shown, the longitudinal central axis L receiving longitudinal sectional plane such that it contacts the valve seat 20 in two radially spaced points P 1 and P 2 punctually, wherein the circle 26 does not intersect the valve seat 20. Two spaced, an inner cone angle β enclosing valve seat surface portions 27, 28 each form a tangent to the circle 26, so that the radius r s of the circle 26 at the points P 1 and P 2 perpendicular to the valve seat 20, more precisely on the valve seat surface portions 27, 28, stands. The relationship β + 2α = 180 °, wherein the angle α is the slope angle at which the valve seat surface sections 27, 28 is inclined to a transversely to the longitudinal central axis L extending plane. It can be seen that the center M of the previously described circle 26 is within the axial extent of the guide 24, in the embodiment shown even on the longitudinal central axis L. In the embodiment shown, the center M, ie a fictitious pivot point of the valve seat 20 coincides with the axial center 25 of the guide 24, the axial center 25 is a pivot point of the valve element 18 in a first extreme position, in which the valve element 18 on the one an upper annular edge 29 of the guide 24 and on the other, rests on the opposite side to a lower annular edge 30 of the guide.

In der Zeichnung ist ferner das Führungsspiel S/2 zwischen Ventilelement 18 und Führung 23 eingezeichnet.In the drawing, the guide play S / 2 between the valve element 18 and guide 23 is also shown.

Aus den Größen rs (Radius des Kreises 26) und dem Hangwinkel α lässt sich der axiale Abstand x zwischen der Dichtlinie, d.h. im eigentlichen Sitz und dem Drehpunkt M des Ventilsitzes berechnen.From the variables r s (radius of the circle 26) and the slope angle α, the axial distance x between the sealing line, ie in the actual seat and the pivot point M of the valve seat can be calculated.

Fig. 2 zeigt ein alternatives Ausführungsbeispiel eines Steuerventils 19, wobei zur Vermeidung von Wiederholungen im Wesentlichen nur auf die Unterschiede zu dem Ausführungsbeispiel gemäß Fig. 1 eingegangen wird. Im Hinblick auf Gemeinsamkeiten wird auf das vorangehende Ausführungsbeispiel verwiesen. Fig. 2 shows an alternative embodiment of a control valve 19, wherein to avoid repetition substantially only to the differences to the embodiment according to Fig. 1 will be received. With regard to similarities, reference is made to the preceding embodiment.

Zu erkennen ist, dass das Ventilelement 18 nicht hülsenförmig, sondern als Bolzen ausgebildet ist, der in einer Führung 23 mit der Axialerstreckung I geführt ist. Der Mittelpunkt M eines Kreises 26, der analog zu dem Ausführungsbeispiel gemäß Fig. 1 angeordnet ist und sich wie bei Fig. 1 auf der Innenkonusseite des Ventilsitzes 20 befindet, ist auf der axialen Mitte (I/2) angeordnet.It can be seen that the valve element 18 is not sleeve-shaped, but is designed as a bolt which is guided in a guide 23 with the axial extension I. The center M of a circle 26, the analogous to the embodiment according to Fig. 1 is arranged and as at Fig. 1 is located on the inner cone side of the valve seat 20 is disposed on the axial center (I / 2).

Am Außenumfang des zylindrischen, bolzenförmigen Ventilelementes 18 befindet sich die als Ringkammer ausgebildete Ventilkammer 17, in die von schräg außen Kraftstoff aus der Steuerkammer 13 strömt und bei geöffnetem Steuerventil in axialer Richtung nach unten zu einem Niederdruckbereich 8 abströmt.On the outer circumference of the cylindrical, bolt-shaped valve element 18 is formed as an annular chamber valve chamber 17, flows into the obliquely outward fuel from the control chamber 13 and flows with the control valve open in the axial direction down to a low pressure region 8.

Fig. 3 zeigt ein weiteres Ausführungsbeispiel. Hier ist der Ventilsitz 20 als Außenkonus ausgebildet und die Führung 23 für das bolzenförmige Ventilelement 18 sowie der Kreis 26 befinden sich auf der hier nach unten gerichteten Innenkonusseite des außenkonusförmigen Ventilsitzes 20, der mit seiner Außenkonusseite mit dem Ventilelement dichtend zusammenwirkt. Die Ventilsitzflächenabschnitte 27, 28 bilden Tangenten an dem Kreis 26. Zu erkennen ist, dass der Mittelpunkt des Kreises innerhalb der Axialerstreckung L der Führung 23 bei U2 angeordnet ist, und zwar auf der Längsmittelachse L des Ventilelementes 18. Im Gegensatz zu dem Ausführungsbeispiel gemäß Fig. 2 ist die Ventilkammer 17 in den Außenumfang des Ventilelementes 18 in der Art einer Ringnut eingearbeitet und bei geöffnetem Steuerventil 19 kann Kraftstoff nicht wie bei Fig. 2 in der Zeichnungsebene nach unten, sondern in der Zeichnungsebene nach oben aus der Ventilkammer 17 heraus, ebenfalls in einem Niederdruckbereich 9 strömen. Fig. 3 shows a further embodiment. Here, the valve seat 20 is formed as an outer cone and the guide 23 for the bolt-shaped valve element 18 and the circuit 26 are located on the downwardly directed here Innenkonusseite the outer cone-shaped valve seat 20 which cooperates sealingly with its outer cone side with the valve element. The valve seat surface portions 27, 28 form tangents on the circle 26. It can be seen that the center of the circle is disposed within the axial extent L of the guide 23 at U2, on the longitudinal center axis L of the valve element 18. In contrast to the embodiment according to FIG Fig. 2 the valve chamber 17 is incorporated in the outer periphery of the valve element 18 in the manner of an annular groove and with open control valve 19 fuel can not as at Fig. 2 in the drawing plane down, but in the plane of the drawing up out of the valve chamber 17 out, also in a low pressure region 9 flow.

Das Ausführungsbeispiel gemäß Fig. 4 unterscheidet sich insofern grundlegend von den vorangehenden Ausführungsbeispielen, als dass nicht der feststehende Ventilsitz sondern der am Ventilelement ausgebildete, mit dem Ventilsitz in der Dichtstellung zusammenwirkende Dichtbereich 31 konusförmig, hier innenkonusförmig (alternativ außenkonusförmig) ausgebildet ist. Der Kreis 26 liegt analog zu dem vorangehenden Ausführungsbeispielen auf der Innenkonusseite des innenkonusförmigen Dichtbereichs 31 des Ventilelementes 18 und berührt den Dichtbereich 31 an zwei voneinander beabstandeten Punkten P1 und P2, sö dass in der Längsschnittansicht zwei einen Innenkonuswinkel β einschließende, linienförmige Dichtbereichabschnitte 32, 33 tangential an dem Kreis 26 anliegen. Der Mittelpunkt M des Kreises 26 liegt in der axialen Mitte 25 der Führung 24, die in dem gezeigten Ausführungsbeispiel von dem Ventilelement 18 gebildet bzw. definiert ist. Mit der Führung 24 gleitet das Ventilelement 18 axial entlang eines axialen Fortsatzes 34 der Drosselplatte 11.The embodiment according to Fig. 4 differs insofar fundamentally from the preceding embodiments, as that not the fixed valve seat but the valve element formed on, with the valve seat in the sealing position cooperating sealing region 31 is cone-shaped, here innenkonusförmig (alternatively outer cone-shaped) is formed. The circle 26 is analogous to the preceding embodiments on the inner cone side of the inner cone-shaped sealing region 31 of the valve element 18 and touches the sealing area 31 at two spaced points P 1 and P 2 , sö that in the longitudinal sectional view of two inner cone angle β enclosing, line-shaped sealing area sections 32, 33 abut tangentially to the circle 26. The center M of the circle 26 is located in the axial center 25 of the guide 24, which is formed in the embodiment shown by the valve member 18 and defined. With the guide 24, the valve member 18 slides axially along an axial extension 34 of the throttle plate eleventh

In dem gezeigten Ausführungsbeispiel befindet sich die Ventilkammer 17 am Außenumfang des Fortsatzes 34 als innere Ringnut innerhalb des hülsenförmigen Ventilelementes 18.In the embodiment shown, the valve chamber 17 is located on the outer circumference of the extension 34 as an inner annular groove within the sleeve-shaped valve element 18th

Claims (7)

  1. Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular common rail injector, comprising a control valve (19) for hydraulically connecting a control chamber (13), which is operatively connected to a single-part or multi-part injection valve element (9), to a low-pressure region (8), wherein the control valve (19) comprises a valve element (18) which can be adjusted axially by means of an actuator and which, in its closed position, interacts via a sealing region (31) with a valve seat (20), which valve element is assigned an axial guide (24), which is arranged positionally fixedly with respect to the sealing region (31) or with respect to the valve seat (20), for guiding the valve element (18) during its axial adjusting movement,
    characterized
    in that a central point (M) of an imaginary circle (26) is arranged within the axial guide length of the guide (24) and in that, in a longitudinal central plane, which encompasses a longitudinal central axis (L) of the valve element (18) of the control valve (19), of the fuel injector (1), the circle makes contact with the valve seat (20), or with the sealing region (31) which interacts with the valve seat (20), of the valve element (18) at two spaced-apart points (P1, P2) in a punctiform manner in each case, in that the central point (M) of the imaginary circle (26) is spaced apart from an axial centre (25) of the guide (24) by less than 40%, preferably less than 30%, preferably less than 20%, particularly preferably less than 10%, of the axial guide length of the guide (24)
    in that the valve seat (20) or the sealing region (31) of the valve element (18) is formed as an internal or external cone and
    in that, in the longitudinal sectional plane of the fuel injector (1), two linear valve seat surface portions (27, 28), or two linear sealing region portions (32, 33), arranged with a cone angle with respect to one another form in each case a tangent to the imaginary circle (26).
  2. Fuel injector according to Claim 1,
    characterized
    in that the central point (M) of the imaginary circle (26) is arranged at least approximately at the axial centre (25) of the guide (24).
  3. Fuel injector according to Claim 1,
    characterized
    in that the central point (M) of the imaginary circle (26) is arranged axially between the axial centre (25) of the guide (24) and that end of the guide (24) which faces toward the valve seat (20).
  4. Fuel injector according to one of the preceding claims,
    characterized
    in that the central point (M) of the imaginary circle (26) is arranged on a longitudinal central axis (L) of the axial guide (24).
  5. The fuel injector according to Claim 1,
    characterized
    in that the cone angle of the valve seat (20) or of the sealing region (31) is selected from an angle range of between approximately 140° and approximately 170°.
  6. Fuel injector according to Claim 1,
    characterized
    in that the axial guide (24) is arranged on an internal cone side of the externally conical or internally conical valve seat (20) or of the sealing region (31).
  7. Fuel injector according to one of the preceding claims,
    characterized
    in that the control valve (19) is formed as a valve which is axially at least approximately pressure-balanced when in the closed state.
EP10762649.1A 2009-11-10 2010-10-01 Fuel injector Active EP2499352B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009046563A DE102009046563A1 (en) 2009-11-10 2009-11-10 fuel injector
PCT/EP2010/064655 WO2011057864A1 (en) 2009-11-10 2010-10-01 Fuel injector

Publications (2)

Publication Number Publication Date
EP2499352A1 EP2499352A1 (en) 2012-09-19
EP2499352B1 true EP2499352B1 (en) 2013-07-03

Family

ID=43127213

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Application Number Title Priority Date Filing Date
EP10762649.1A Active EP2499352B1 (en) 2009-11-10 2010-10-01 Fuel injector

Country Status (7)

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US (1) US20120216772A1 (en)
EP (1) EP2499352B1 (en)
CN (1) CN102597488B (en)
DE (1) DE102009046563A1 (en)
IN (1) IN2012DN02007A (en)
RU (1) RU2572028C2 (en)
WO (1) WO2011057864A1 (en)

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JP6866243B2 (en) * 2017-06-22 2021-04-28 ボッシュ株式会社 Fuel injection device

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Also Published As

Publication number Publication date
RU2012123964A (en) 2013-12-20
CN102597488A (en) 2012-07-18
US20120216772A1 (en) 2012-08-30
DE102009046563A1 (en) 2011-05-12
CN102597488B (en) 2016-03-30
WO2011057864A1 (en) 2011-05-19
RU2572028C2 (en) 2015-12-27
IN2012DN02007A (en) 2015-07-24
EP2499352A1 (en) 2012-09-19

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