EP2466107B1 - Fuel injector with pressure-equalised control valve - Google Patents

Fuel injector with pressure-equalised control valve Download PDF

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Publication number
EP2466107B1
EP2466107B1 EP20110192957 EP11192957A EP2466107B1 EP 2466107 B1 EP2466107 B1 EP 2466107B1 EP 20110192957 EP20110192957 EP 20110192957 EP 11192957 A EP11192957 A EP 11192957A EP 2466107 B1 EP2466107 B1 EP 2466107B1
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EP
European Patent Office
Prior art keywords
valve
sealing
pressure
chamber
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.)
Not-in-force
Application number
EP20110192957
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German (de)
French (fr)
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EP2466107A1 (en
Inventor
Torsten Leukert
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2466107A1 publication Critical patent/EP2466107A1/en
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Publication of EP2466107B1 publication Critical patent/EP2466107B1/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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.
  • a fuel injector with a pressure compensated control valve is off DE 10 2008 001 330 known.
  • the control valve actuates a nozzle needle for injecting fuel, wherein the nozzle needle is exposed to a control chamber and the control valve controls the pressure in the control chamber.
  • the control valve has a valve pin and a valve sleeve, wherein the valve sleeve is axially guided on a guide of the valve pin.
  • the valve sleeve is biased by a valve spring urging an annular surface in a high pressure side valve space against a component fixed to the housing, thereby hydraulically separating the high pressure side valve space from a low pressure side valve space.
  • the valve pin is thereby exposed with an end face the low pressure side valve chamber and thus receives a constant low-pressure connection.
  • valve pin is thereby not pressed against the opening of the valve seat against the entire rail pressure in the high-pressure side valve chamber, but has by the low-pressure connection in the low-pressure side valve chamber a pressure equalization with respect to the also exposed to the low pressure counter surface.
  • the guide between valve pin and valve sleeve forms a guide gap, via which a leakage from the high-pressure side valve chamber in the low-pressure side valve chamber can flow out. This leakage must be compensated by a correspondingly higher flow rate in the high-pressure inlet, which in turn is a high-pressure pump providing the high pressure is more heavily loaded or can be used to the leakage lower pressure for injecting the fuel.
  • the invention has for its object to provide a fuel injector in which the control valve no or a greatly reduced leakage occurs, so that the hydraulic losses of the fuel injector can be reduced.
  • the present invention solves the problem in that the opening into the high pressure side valve space guide gap between the valve pin and the valve sleeve is closed by means of a seal to the low pressure side valve chamber out at least when the sealing seat is closed. As a result, hydraulic losses of the fuel injector are reduced, so that a higher efficiency of the entire injection system is achieved.
  • the leakage gap is closed in the closed state of the valve seat.
  • the leakage gap can be opened, because ideally there is no pressure gradient between the high-pressure-side valve chamber and the low-pressure-side valve chamber when the valve seat is open.
  • no leakage occurs at this time.
  • the inner seal on the valve pin is opened, insofar the guide gap is closed only when the valve seat is closed.
  • the seal is effective both when the valve seat is closed and when the valve seat is open.
  • the seal is formed by a sealing disc, which acts on the valve sleeve and the valve pin.
  • the seal on an outer sealing edge and an inner sealing edge, which cooperate in each case with a sealing mating surface.
  • the sealing edges are preferably designed as B sulfurkanten.
  • the outer sealing edge and the inner sealing edge are formed at a radial distance on an end face of the sealing disc, wherein the guide gap is located between the sealing edges.
  • the sealing mating surfaces are formed by an outer sealing surface formed on the valve sleeve and by an inner sealing surface formed on the valve piston. The sealing effect is achieved by the outer sealing edge rests sealingly on the outer sealing surface of the valve sleeve and the inner sealing edge on the inner sealing surface of the valve pin when the sealing seat is closed.
  • the outer sealing edge is arranged on an end face of the valve sleeve and the inner sealing edge on a further annular surface formed on the valve piston, wherein the sealing mating surfaces are executed by an end face formed on the sealing disc.
  • outer sealing edge and outer sealing surface takes place in an outer Dichtben and the interaction of inner sealing edge and inner sealing surface in an inner sealing plane.
  • inner Dichtben in the direction of it opening stroke of the valve pin is slightly below or behind the outer sealing layer.
  • the valve pin has a diameter step.
  • the valve pin is made at least two parts.
  • an annular surface is formed on the diameter graduation, which forms the inner sealing surface or a base surface for forming the inner sealing edge.
  • a montagemese execution is done by a valve pin part and a valve pin sleeve are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston connected become.
  • a further assembly-oriented design is carried out by a stepped valve pin member and a separate valve seat body are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston are connected.
  • Fig. 1 is a designed as a common rail injector fuel injector for injecting fuel into a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic representation shown in fragmentary form.
  • the fuel injector comprises a control valve 10 designed as a hydraulic servo valve and an injection valve element 12.
  • the control valve 10 is actuated by an actuator (not shown), for example a piezoactuator, via a hydraulic coupler 14. From the hydraulic coupler 14, only a valve-side piston 15 is shown with an end face 13, which is arranged in a low-pressure space 17.
  • the low-pressure chamber 17 is connected to a low-pressure connection, not shown, which is connected to a fuel return.
  • the control valve 10, the injection valve element 12, the hydraulic coupler and the actuator are housed in an injector housing, which in FIG. 1
  • an injector housing which in FIG. 1
  • individual housing components are hydraulically sealed, such as a holding body 18, a first valve plate 21, a second valve plate 22, a throttle plate 23 and a Nozzle body 24.
  • a high-pressure inlet 16 which is connected at one end to a high-pressure accumulator, not shown (common rail) and the other ends in a pressure chamber 19 within the nozzle body 24 opens.
  • the injector can also be made in one piece.
  • the injection valve element 12 is arranged within the nozzle body 24 and comprises an axially movable nozzle needle 25 and a control chamber sleeve 26.
  • the control chamber sleeve 26 is axially displaceably guided on the nozzle needle 25 and is supported in the axial direction on the housing-fixed throttle plate 23 from.
  • the nozzle needle 25 and the control chamber sleeve 26 are surrounded by the pressure chamber 19, wherein the nozzle needle 25 acts within the pressure chamber 19 in a closed position sealingly on a nozzle needle seat, not shown, in a conventional manner.
  • the injection ports are closed. If, however, the nozzle needle 25 is lifted from the nozzle needle seat, fuel is injected at high pressure within the pressure chamber 19 through the injection openings in the combustion chamber of the internal combustion engine.
  • control chamber sleeve 26 surrounds a control chamber 27, which the nozzle needle 25 is exposed to a pressure surface 28.
  • the control chamber sleeve 26 is supported in the axial direction of the housing-fixed throttle plate 23 and thus separates the control chamber 27 from the pressure chamber 19 hydraulically, the control chamber 27 via the forming sealing gap between Steuerraumhülse 26 and throttle plate 23 from the high pressure region of the pressure chamber 19 with fuel is filled.
  • an inlet throttle may be introduced, for example, in the control chamber sleeve 26 or in the throttle plate 23, which then connect the control chamber 27 with the high-pressure inlet 16.
  • a drain channel 31 is introduced with an outlet throttle 32.
  • About the drain passage 31 of the control chamber 27 is permanently connected to a high-pressure side valve chamber 33 which is radially and axially bounded by the first and second valve plate 21, 22 and by the throttle plate 23.
  • the high-pressure-side valve chamber 33 is part of the control valve 10 and is hydraulically connected via a valve seat 30 to the low-pressure chamber 17.
  • connection channel 34 which is designed with a Mountaindrossel 35, wherein the connecting channel 34 connects the high-pressure side valve chamber 33 with the high-pressure inlet 16.
  • the connecting channel 34 is not absolutely necessary, because the filling of the valve chamber 33 can also take place out of the control chamber 27 via the outlet channel 31.
  • the control valve 10 comprises a valve pin 41, a valve sleeve 42, a sealing disc 43 and a valve spring 44.
  • the valve pin 41 is designed with a mushroom-shaped valve seat body 45 which presses against the housing-fixed valve seat 30 with a sealing seat surface 46.
  • the valve pin 41 has at the end facing the coupler 14 on a counter surface 38 against which the end surface 13 of the valve-side piston 15 of the coupler 14 presses.
  • the valve sleeve 42 and the sealing disc 43 are axially displaceably guided on the valve piston 41, wherein the guide between the valve piston 41 and valve sleeve 42 due to the function, a guide gap 50 is present ( FIG. 2 ).
  • valve pin 41 rests with the sealing seat surface 46 on the housing-tight sealing seat 30.
  • the closing force is applied substantially by the valve spring 44, which is supported on a collar of the mushroom-shaped valve seat body 45 and the sealing discs 43, wherein the sealing disc 43 in turn on the valve sleeve 42 and the valve sleeve 42 with a circumferential annular surface 48 on the Throttle plate 23 is supported.
  • the annular surface 48 forms a sealing surface, so that within the annular surface 48, a low-pressure side valve chamber 49 is formed, which is hydraulically separated by the sealing action of the annular surface 48 from the high-pressure side valve chamber 33.
  • the low-pressure-side valve chamber 49 is exposed to the valve pin 41 with an end face 47.
  • the low-pressure side valve chamber 49 is connected via a formed in the throttle plate 23 hydraulic connection 37 to the mentioned low-pressure connection, which leads into the return line.
  • the valve pin 41 points through the constant low-pressure connection of the low-pressure side Valve chamber 49 a pressure equalization for the end face 47 with respect to the ebenfelle low pressure exposed counter surface 38, wherein the counter surface 38 is determined by the diameter of the valve seat 30.
  • the valve pin 41 for opening the valve seat 30 is not to be pressed against the entire high pressure in the high-pressure-side valve space 33.
  • there is a pressure-compensated control valve 10 in which the valve opening force applied to the end face 47 is essentially determined only by the spring force of the valve spring 44.
  • the diameter of the valve seat 30 determining the mating surface 38 of the valve bolt 41 is selected to be slightly smaller than the pressure surface 47 of the valve bolt 41 exposed to the low-pressure space. As a result, a permanent closing force acts on the valve bolt 41 within the valve space 33.
  • a seal 40 is formed, which closes the guide gap 50 to the high pressure side valve chamber 33 out.
  • the sealing disks 43 are formed on an end face 54 facing the valve sleeve 42 with an outer circumferential sealing edge 51 and an inner circumferential sealing edge 52, wherein the sealing edges 51, 52 extend at a radial distance on the end face 54. Within the radial distance is the guide gap 50.
  • the outer sealing edge 51 acts on the valve sleeve 42 and the inner sealing edge 52 on the valve piston 41 a.
  • respective sealing mating surfaces are provided on the valve sleeve 42 and on the valve piston 41 for the outer and inner sealing edges 51, 52.
  • the sealing edges 51, 52 are expediently designed as B reactkanten.
  • the sealing mating surfaces are formed by an outer sealing surface 56 formed on the valve sleeve 42 and an inner sealing surface 58 formed on the valve piston 41, the outer sealing surface 51 acting on the outer sealing surface 56 and the inner sealing edge 52 on the inner sealing surface 58.
  • the outer sealing surface 56 is of the Sealing disk 43 facing annular surface of the valve sleeve 42 is formed.
  • the valve pin 41 is designed with a diameter graduation, wherein the annular surface lying in the diameter gradation forms the inner sealing surface 58.
  • valve pin 41 of two parts composed, namely according to FIG. 2 from a valve pin part 64 and a valve pin sleeve 65, wherein the valve sleeve 42 is guided on the valve pin sleeve 65.
  • the valve pin sleeve 65 is fastened to the valve pin part 64, for example by means of welding.
  • valve pin 41 it is just as possible to assemble the valve pin 41 from a stepped valve pin part and a separate, separate valve seat body 45.
  • the sealing disc 43 and the valve spring 44 is pushed from the koppler Konen end to the valve pin part and then inserted the koppler Konen end of the valve pin part in a bore of the separate valve seat body 45 and fixed there, for example by welding.
  • the high pressure applied in the high pressure side valve space 33 deforms the sealing disc 43 slightly in the elastic region and presses it with the sealing edges 51, 52 against the sealing surfaces 56, 58 and thus closes the guide gap 50.
  • the stator valve 10 opens the valve seat 30 the valve pin 41 is pressed by the actuator in the direction throttle plate 23.
  • the inner sealing surface 58 on the valve sleeve 42 also dips in the direction of the throttle plate 23. Because at the same time the pressure in the high pressure side valve chamber 33 drops very sharply and thus the contact pressure on the sealing disc 43 decreases, the inner sealing surface 58 is separated from the inner sealing edge 52.
  • the outer sealing edge 51 is arranged on the sealing face 43 facing the end face of the valve sleeve 42 and the inner sealing edge 52 on the annular surface of the valve pin 41 formed by the diameter graduation.
  • the sealing mating surfaces with the outer sealing surface 56 for the outer sealing edge 51 and with the inner sealing surface 58 for the inner sealing edge 52 are then formed by the valve sleeve 42 facing end face 54 of the sealing disc 43.
  • outer sealing edge 51 and outer sealing surface 56 forms an outer sealing edge 61; the interaction of inner sealing edge 52 and inner sealing surface 58 forms an inner sealing plane 62.
  • outer sealing plane 61 and the inner sealing plane 62 are not exactly in the same plane, but that the inner sealing surfaces 62 in the direction of the opening stroke for opening the valve seat 30 is slightly below or behind the outer sealing layer 61. It must be ensured that the control valve 10 in the valve seat 30 closes. Ie.
  • the need for subsequent displacement of the two sealing planes 61, 62 results from the axial tolerances to form a secure valve seat 30, the axial tolerances of the valve sleeve 42 and valve pin sleeve 65 and the vorzuhaltenden wear of the valve seat 30.
  • the maximum offset may be so large that the possible deformation of the Sealing disc 43 does not pass through the high pressure in the plastic deformation range.
  • the high pressure in the control chamber 27 acts on the pressure surface 26 on the nozzle needle 25, whereby the nozzle needle 25 is placed in the nozzle needle seat.
  • the injection openings are closed.
  • the actuator If the actuator is actuated, press the valve-side piston 15 of the coupler 14 with the end face 13 on the counter surface 38 of the valve pin 41.
  • the sealing seat surface 46 is pushed away from the valve seat 30 and a hydraulic connection between the high pressure side valve chamber 33 and the low pressure chamber 17 is formed.
  • the pressure in the high-pressure-side valve chamber 33 and via the drainage channel 31 is also relaxed in the control chamber 27, so that the opening force acting on the nozzle needle 25 in the pressure chamber 19 exceeds the closing force acting on the pressure surface 26 of the nozzle needle 25 in the control chamber 27.
  • the nozzle needle 25 lifts from the nozzle needle seat and releases the injection ports for injecting fuel.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoffinjektor für eine Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.

Ein Kraftstoffinjektor mit einem druckausgeglichenen Steuerventil ist aus DE 10 2008 001 330 bekannt. Das Steuerventil betätigt eine Düsennadel zum Einspritzen von Kraftstoff, wobei die Düsennadel einem Steuerraum ausgesetzt ist und das Steuerventil den Druck im Steuerraum steuert. Das Steuerventil weist einen Ventilbolzen und eine Ventilhülse auf, wobei die Ventilhülse an einer Führung des Ventilbolzens axial geführte ist. Die Ventilhülse ist von einer Ventilfeder vorgespannt, die eine Ringfläche in einem hochdruckseitigen Ventilraum gegen ein gehäusefestes Bauteil drückt und dadurch den hochdruckseitigen Ventilraum von einem niederdruckseitigen Ventilraum hydraulisch trennt. Der Ventilbolzen ist dadurch mit einer Stirnfläche dem niederdruckseitigen Ventilraum ausgesetzt und erhält damit eine ständige Niederdruckanbindung. Der Ventil bolzen wird zur Öffnung des Ventilsitzes dadurch nicht gegen den gesamten Raildruck im hochdruckseitigen Ventilraum gedrückt, sondern weist durch die Niederdruckanbindung im niederdruckseitigen Ventilraum einen Druckausgleich in Bezug auf die ebenfalls dem Niederdruck ausgesetzte Gegenfläche auf. Die Führung zwischen Ventil bolzen und Ventilhülse bildet dabei jedoch einen Führungsspalt, über den eine Leckage aus dem hochdruckseitigen Ventilraum in den niederdruckseitigen Ventilraum abströmen kann. Diese Leckage muss durch eine entsprechend höhere Fördermenge im Hochdruckzulauf ausgeglichen werden, wodurch wiederum eine den Hochdruck bereitstellende Hochdruckpumpe stärker belastet wird oder ein um die Leckage geringerer Druck zum Einspritzen des Kraftstoffs genutzt werden kann.A fuel injector with a pressure compensated control valve is off DE 10 2008 001 330 known. The control valve actuates a nozzle needle for injecting fuel, wherein the nozzle needle is exposed to a control chamber and the control valve controls the pressure in the control chamber. The control valve has a valve pin and a valve sleeve, wherein the valve sleeve is axially guided on a guide of the valve pin. The valve sleeve is biased by a valve spring urging an annular surface in a high pressure side valve space against a component fixed to the housing, thereby hydraulically separating the high pressure side valve space from a low pressure side valve space. The valve pin is thereby exposed with an end face the low pressure side valve chamber and thus receives a constant low-pressure connection. The valve pin is thereby not pressed against the opening of the valve seat against the entire rail pressure in the high-pressure side valve chamber, but has by the low-pressure connection in the low-pressure side valve chamber a pressure equalization with respect to the also exposed to the low pressure counter surface. The guide between valve pin and valve sleeve, however, forms a guide gap, via which a leakage from the high-pressure side valve chamber in the low-pressure side valve chamber can flow out. This leakage must be compensated by a correspondingly higher flow rate in the high-pressure inlet, which in turn is a high-pressure pump providing the high pressure is more heavily loaded or can be used to the leakage lower pressure for injecting the fuel.

Der Erfindung liegt die Aufgabe zugrunde, einen Kraftstoffinjektor anzugeben, bei dem am Steuerventil keine oder eine stark reduzierte Leckage auftritt, so dass die hydraulischen Verluste des Kraftstoffinjektors reduziert werden können.The invention has for its object to provide a fuel injector in which the control valve no or a greatly reduced leakage occurs, so that the hydraulic losses of the fuel injector can be reduced.

Offenbarung der ErfindungDisclosure of the invention

Diese Aufgabe wird in einem Kraftstoffinjektor mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst. Die vorliegende Erfindung löst die Aufgabe dadurch, dass der in den hochdruckseitigen Ventilraum mündende Führungsspalt zwischen Ventilbolzen und Ventilhülse mittels einer Abdichtung zum niederdruckseitigen Ventilraum hin zumindest bei geschlossenem Dichtsitz verschlossen ist. Dadurch werden hydraulische Verluste des Kraftstoffinjektors reduziert, so dass ein höherer Wirkungsgrad des gesamten Einspritzsystems erzielt wird.This object is achieved in a fuel injector with the characterizing features of claim 1. The present invention solves the problem in that the opening into the high pressure side valve space guide gap between the valve pin and the valve sleeve is closed by means of a seal to the low pressure side valve chamber out at least when the sealing seat is closed. As a result, hydraulic losses of the fuel injector are reduced, so that a higher efficiency of the entire injection system is achieved.

Für das Verständnis des weitestgehend leckagefreien Steuerventils ist, dass der Leckagespalt im geschlossenen Zustand des Ventilsitzes verschlossen ist. Im geöffneten Zustand kann der Leckagespalt geöffnet sein, weil idealerweise bei geöffnetem Ventilsitz kein Druckgefälle zwischen hochdruckseitigem Ventilraum und niederdruckseitigem Ventilraum besteht. Dadurch tritt zu diesem Zeitpunkt auch kein Leckage auf. Bei dem beschriebenen Ausführungsbeispiel ist bedingt durch den Öffnungshub des Ventilsbolzen bei geöffnetem Ventilsitz die innere Abdichtung am Ventilbolzen geöffnet, insofern ist der Führungsspalt nur bei geschlossenem Ventilsitz verschlossen. Es ist aber denkbar, dass mit einer speziellen technischen Lösung die Abdichtung sowohl bei geschlossenem als auch bei geöffneten Ventilsitz wirksam ist.To understand the largely leakage-free control valve is that the leakage gap is closed in the closed state of the valve seat. In the opened state, the leakage gap can be opened, because ideally there is no pressure gradient between the high-pressure-side valve chamber and the low-pressure-side valve chamber when the valve seat is open. As a result, no leakage occurs at this time. In the described embodiment, due to the opening stroke of the valve bolt with the valve seat open, the inner seal on the valve pin is opened, insofar the guide gap is closed only when the valve seat is closed. However, it is conceivable that with a special technical solution, the seal is effective both when the valve seat is closed and when the valve seat is open.

Vorteilhafte Weiterbildungen der Erfindung sind durch die Merkmale der Unteransprüche möglich.Advantageous developments of the invention are possible by the features of the subclaims.

Vorteilhaft wird die Abdichtung von einer Abdichtscheiben gebildet, die auf die Ventilhülse und den Ventilbolzen einwirkt. Dazu weist die Abdichtung eine äußere Dichtkante und eine innere Dichtkante auf, die jeweils mit einer dichtenden Gegenfläche zusammenwirken. Die Dichtkanten sind vorzugsweise als Beißkanten ausgeführt. Gemäß einer ersten Ausführungsform sind die äußere Dichtkante und die innere Dichtkante in einem radialen Abstand an einer Stirnfläche der Abdichtscheibe ausgebildet, wobei sich zwischen den Dichtkanten der Führungsspalt befindet. Die dichtenden Gegenflächen werden dabei von einer an der Ventilhülse ausgebildeten äußeren Dichtfläche und von einer am Ventilkolben ausgebildeten inneren Dichtfläche gebildet. Die Dichtwirkung wird erzielt, indem bei geschlossenem Dichtsitz die äußere Dichtkante auf der äußeren Dichtfläche der Ventilhülse und die innere Dichtkante auf der inneren Dichtfläche des Ventilbolzens dichtend aufliegt.Advantageously, the seal is formed by a sealing disc, which acts on the valve sleeve and the valve pin. For this purpose, the seal on an outer sealing edge and an inner sealing edge, which cooperate in each case with a sealing mating surface. The sealing edges are preferably designed as Beißkanten. According to a first embodiment, the outer sealing edge and the inner sealing edge are formed at a radial distance on an end face of the sealing disc, wherein the guide gap is located between the sealing edges. The sealing mating surfaces are formed by an outer sealing surface formed on the valve sleeve and by an inner sealing surface formed on the valve piston. The sealing effect is achieved by the outer sealing edge rests sealingly on the outer sealing surface of the valve sleeve and the inner sealing edge on the inner sealing surface of the valve pin when the sealing seat is closed.

Gemäß einer zweiten Ausführungsform ist die äußere Dichtkante an einer Stirnfläche der Ventilhülse und die innere Dichtkante an einer am Ventilkolben ausgebildeten weiteren Ringfläche angeordnet, wobei die dichtenden Gegenflächen von einer an der Abdichtscheibe ausgebildeten Stirnfläche ausgeführt sind.According to a second embodiment, the outer sealing edge is arranged on an end face of the valve sleeve and the inner sealing edge on a further annular surface formed on the valve piston, wherein the sealing mating surfaces are executed by an end face formed on the sealing disc.

Das Zusammenwirken von äußerer Dichtkante und äußerer Dichtfläche erfolgt in einer äußere Dichteben und das Zusammenwirken von innerer Dichtkante und innerer Dichtfläche in einer inneren Dichtebene. Wichtig für die Ausbildung eines sicheren Dichtsitzes des Steuerventils ist, dass die innere Dichteben in Richtungd es Öffnungshubs des Ventilbolzen geringfügig unterhalb bzw. hinter der äußeren Dichtebene liegt.The interaction of outer sealing edge and outer sealing surface takes place in an outer Dichtben and the interaction of inner sealing edge and inner sealing surface in an inner sealing plane. Important for the formation of a secure sealing seat of the control valve is that the inner Dichtben in the direction of it opening stroke of the valve pin is slightly below or behind the outer sealing layer.

Zur Ausbildung der inneren Dichtebenen weist der Ventilbolzen eine Durchmesserstufe auf. Zum Einsetzen der Abdichtscheibe und der Ventilfeder hinter der Durchmesserstufe ist es notwendig, dass der Ventilbolzen mindestens zweiteilig ausgeführt ist. Dazu ist an der Durchmesserstufung eine Ringfläche ausgebildet, welche die innere Dichtfläche oder eine Grundfläche zur Ausbildung der inneren Dichtkante bildet. Eine montagegerechte Ausführung erfolgt dadurch, indem eine Ventilbolzenteil und eine Ventilbolzenhülse vorgesehen sind, wobei nach Einsetzen der Abdichtscheibe und der Ventilfeder die beiden Teile des Ventilkolbens verbunden werden. Eine weiter montagegerechte Ausführung erfolgt dadurch, indem eine gestuftes Ventilbolzenteil und ein separater Ventilsitzkörper vorgesehen sind, wobei nach Einsetzen der Abdichtscheibe und der Ventilfeder die beiden Teile des Ventilkolbens verbunden werden.To form the inner sealing levels, the valve pin has a diameter step. To insert the sealing disc and the valve spring behind the diameter step, it is necessary that the valve pin is made at least two parts. For this purpose, an annular surface is formed on the diameter graduation, which forms the inner sealing surface or a base surface for forming the inner sealing edge. A montagegerechte execution is done by a valve pin part and a valve pin sleeve are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston connected become. A further assembly-oriented design is carried out by a stepped valve pin member and a separate valve seat body are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston are connected.

Ausführungsbeispielembodiment

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description.

Es zeigen:

Fig. 1
eine ausschnittsweise, schematische Darstellung eines Kraftstoffinjektors und
Fig. 2
einen vergrößerten Ausschnitt X des Kraftstoffinjektor in Figur 1.
Show it:
Fig. 1
a fragmentary, schematic representation of a fuel injector and
Fig. 2
an enlarged section X of the fuel injector in FIG. 1 ,

In Fig. 1 ist ein als Common-Rail-Injektor ausgebildeter Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen nicht gezeigten Brennraum einer ebenfalls nicht gezeigten Brennkraftmaschine eines Kraftfahrzeuges in einer schematischen Darstellung ausschnittsweise gezeigt.In Fig. 1 is a designed as a common rail injector fuel injector for injecting fuel into a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic representation shown in fragmentary form.

Der Kraftstoffinjektor umfasst ein als hydraulisches Servoventil ausgebildetes Steuerventil 10 und ein Einspritzventilelement 12. Das Steuerventil 10 wird von einem nicht dargestellten Aktuator, beispielsweise einem Piezo-Aktor über einen hydraulischen Koppler 14 betätigt. Vom hydraulischen Koppler 14 ist lediglich ein ventilseitiger Kolben 15 mit einer Endfläche 13 gezeigt, der in einem Niederdruckraum 17 angeordnet ist. Der Niederdruckraum 17 ist an einen nicht dargestellten Niederdruckanschluss angeschlossen, der mit einem Kraftstoffrücklauf verbunden ist.The fuel injector comprises a control valve 10 designed as a hydraulic servo valve and an injection valve element 12. The control valve 10 is actuated by an actuator (not shown), for example a piezoactuator, via a hydraulic coupler 14. From the hydraulic coupler 14, only a valve-side piston 15 is shown with an end face 13, which is arranged in a low-pressure space 17. The low-pressure chamber 17 is connected to a low-pressure connection, not shown, which is connected to a fuel return.

Das Steuerventil 10, das Einspritzventilelement 12, der hydraulische Koppler und der Aktuator sind in einem Injektorgehäuse untergebracht, das in Figur 1 beispielsweise aus einzelnen Gehäusebauteilen hydraulisch dicht zusammengesetzt sind, wie beispielsweise einem Haltekörper 18, einer ersten Ventilplatte 21, einer zweiten Ventilplatte 22, einer Drosselplatte 23 und einem Düsenkörper 24. Durch die Gehäuseteile führt ein Hochdruckzulauf 16, der einenends an einen nicht gezeigten Hochdruckspeicher (Common-Rail) anschlossen ist und anderenends in einen Druckraum 19 innerhalb des Düsenkörpers 24 mündet. Das Injektorgehäuse kann aber auch einteilig ausgeführt sein.The control valve 10, the injection valve element 12, the hydraulic coupler and the actuator are housed in an injector housing, which in FIG. 1 For example, from individual housing components are hydraulically sealed, such as a holding body 18, a first valve plate 21, a second valve plate 22, a throttle plate 23 and a Nozzle body 24. Through the housing parts performs a high-pressure inlet 16, which is connected at one end to a high-pressure accumulator, not shown (common rail) and the other ends in a pressure chamber 19 within the nozzle body 24 opens. But the injector can also be made in one piece.

Das Einspritzventilelement 12 ist innerhalb des Düsenkörpers 24 angeordnet und umfasst eine axial beweglichen Düsennadel 25 und eine Steuerraumhülse 26. Die Steuerraumhülse 26 ist axial verschiebbar an der Düsennadel 25 geführt und stützt sich in axialer Richtung an der gehäusefesten Drosselplatte 23 ab. Die Düsennadel 25 und die Steuerraumhülse 26 sind vom Druckraum 19 umgeben, wobei die Düsennadel 25 innerhalb des Druckraums 19 in einer Schließstellung dichtend auf einen nicht gezeigten Düsennadelsitz in an sich bekannter Weise einwirkt. Wenn die Düsennadel 25 am Düsennadelsitz anliegt, sind die Einspritzöffnungen geschlossen. Ist dagegen die Düsennadel 25 vom Düsennadelsitz abgehoben, wird Kraftstoff mit dem Hochdruck innerhalb des Druckraums 19 durch die Einspritzöffnungen in den Brennraum der Brennkraftmaschine eingespritzt.The injection valve element 12 is arranged within the nozzle body 24 and comprises an axially movable nozzle needle 25 and a control chamber sleeve 26. The control chamber sleeve 26 is axially displaceably guided on the nozzle needle 25 and is supported in the axial direction on the housing-fixed throttle plate 23 from. The nozzle needle 25 and the control chamber sleeve 26 are surrounded by the pressure chamber 19, wherein the nozzle needle 25 acts within the pressure chamber 19 in a closed position sealingly on a nozzle needle seat, not shown, in a conventional manner. When the nozzle needle 25 abuts the nozzle needle seat, the injection ports are closed. If, however, the nozzle needle 25 is lifted from the nozzle needle seat, fuel is injected at high pressure within the pressure chamber 19 through the injection openings in the combustion chamber of the internal combustion engine.

Die an der Düsennadel 25 axial geführte Steuerraumhülse 26 umgibt einem Steuerraum 27, dem die Düsennadel 25 mit einer Druckfläche 28 ausgesetzt ist. Die Steuerraumhülse 26 stützt sich dabei in axialer Richtung an der gehäusefesten Drosselplatte 23 ab und trennt damit den Steuerraum 27 vom Druckraum 19 hydraulisch ab, wobei der Steuerraum 27 über den sich ausbildenden Dichtspalt zwischen Steuerraumhülse 26 und Drosselplatte 23 aus dem Hochdruckbereich des Druckraums 19 mit Kraftstoff befüllt wird. Alternativ kann auch eine Zulaufdrossel beispielsweise in der Steuerraumhülse 26 oder in der Drosselplatte 23 eingebracht sein, die dann den Steuerraum 27 mit dem Hochdruckzulauf 16 verbinden.The axially guided on the nozzle needle 25 control chamber sleeve 26 surrounds a control chamber 27, which the nozzle needle 25 is exposed to a pressure surface 28. The control chamber sleeve 26 is supported in the axial direction of the housing-fixed throttle plate 23 and thus separates the control chamber 27 from the pressure chamber 19 hydraulically, the control chamber 27 via the forming sealing gap between Steuerraumhülse 26 and throttle plate 23 from the high pressure region of the pressure chamber 19 with fuel is filled. Alternatively, an inlet throttle may be introduced, for example, in the control chamber sleeve 26 or in the throttle plate 23, which then connect the control chamber 27 with the high-pressure inlet 16.

In der Drosselplatte 23 ist ein Ablaufkanal 31 mit einer Ablaufdrossel 32 eingebracht. Über den Ablaufkanal 31 ist der Steuerraum 27 dauerhaft mit einem hochdruckseitigen Ventilraum 33 verbunden, der radial und axial von der ersten und zweiten Ventilplatte 21, 22 sowie von der Drosselplatte 23 begrenzt ist.In the throttle plate 23, a drain channel 31 is introduced with an outlet throttle 32. About the drain passage 31 of the control chamber 27 is permanently connected to a high-pressure side valve chamber 33 which is radially and axially bounded by the first and second valve plate 21, 22 and by the throttle plate 23.

Der hochdruckseitige Ventilraum 33 ist Teil des Steuerventils 10 und ist über einen Ventilsitz 30 hydraulisch mit dem Niederdruckraum 17 verbindbar. In den hochdruckseitigen Ventilraum 33 mündet ein in die zweite Ventilplatte 22 eingebrachter Verbindungskanal 34, der mit einer Fülldrossel 35 ausgeführt ist, wobei der Verbindungskanal 34 den hochdruckseitiger Ventilraum 33 mit dem Hochdruckzulauf 16 verbindet. Die Verbindungskanal 34 ist nicht zwingend erforderlich, denn die Befüllung des Ventilraums 33 kann auch aus dem Steuerraum 27 heraus über den Ablaufkanal 31 erfolgen.The high-pressure-side valve chamber 33 is part of the control valve 10 and is hydraulically connected via a valve seat 30 to the low-pressure chamber 17. In the high-pressure-side valve chamber 33 opens into the second valve plate 22 inserted connection channel 34, which is designed with a Fülldrossel 35, wherein the connecting channel 34 connects the high-pressure side valve chamber 33 with the high-pressure inlet 16. The connecting channel 34 is not absolutely necessary, because the filling of the valve chamber 33 can also take place out of the control chamber 27 via the outlet channel 31.

Das Steuerventil 10 umfasst einen Ventilbolzen 41, eine Ventilhülse 42, eine Abdichtscheibe 43 und eine Ventilfeder 44. Der Ventilbolzen 41 ist mit einem pilzförmigen Ventilsitzkörper 45 ausgeführt, welcher mit einer Dichtsitzfläche 46 gegen den gehäusefesten Ventilsitz 30 drückt. Der Ventilbolzen 41 weist an dem zum Koppler 14 weisenden Ende eine Gegenfläche 38 auf, gegen die die Endfläche 13 des ventilseitigen Kolbens 15 des Kopplers 14 drückt. Die Ventilhülse 42 und die Abdichtscheibe 43 sind axial verschiebbar am Ventilkolben 41 geführt, wobei zur Führung zwischen Ventilkolben 41 und Ventilhülse 42 funktionsbedingt ein Führungsspalt 50 vorhanden ist (Figur 2).The control valve 10 comprises a valve pin 41, a valve sleeve 42, a sealing disc 43 and a valve spring 44. The valve pin 41 is designed with a mushroom-shaped valve seat body 45 which presses against the housing-fixed valve seat 30 with a sealing seat surface 46. The valve pin 41 has at the end facing the coupler 14 on a counter surface 38 against which the end surface 13 of the valve-side piston 15 of the coupler 14 presses. The valve sleeve 42 and the sealing disc 43 are axially displaceably guided on the valve piston 41, wherein the guide between the valve piston 41 and valve sleeve 42 due to the function, a guide gap 50 is present ( FIG. 2 ).

In der gezeigten Schaltstellung liegt der Ventilbolzen 41 mit der Dichtsitzfläche 46 am gehäusefesten Dichtsitz 30 an. Die Schließkraft wird dabei im Wesentlichen von der Ventilfeder 44 aufgebracht, die sich an einem Bund des pilzförmigen Ventilsitzkörpers 45 und an der Abdichtscheiben 43 abstützt, wobei die Abdichtscheibe 43 wiederum sich an der Ventilhülse 42 und die Ventilhülse 42 sich mit einer umlaufenden Ringfläche 48 an der Drosselplatte 23 abstützt. Die Ringfläche 48 bildet eine Dichtfläche, so dass innerhalb der Ringfläche 48 ein niederdruckseitiger Ventilraum 49 entsteht, der durch die Dichtwirkung der Ringfläche 48 vom hochdruckseitigen Ventilraum 33 hydraulisch getrennt ist. Dem niederdruckseitigen Ventilraum 49 ist der Ventilbolzen 41 mit einer Stirnfläche 47 ausgesetzt. Der niederdruckseitige Ventilraum 49 ist über eine in der Drosselplatte 23 ausgebildete hydraulische Verbindung 37 an den erwähnten Niederdruckanschluss gelegt, der in die Rücklaufleitung führt. Der Ventilbolzen 41 weist durch die ständigen Niederdruckanbindung des niederdruckseitigen Ventilraums 49 einen Druckausgleich für die Stirnfläche 47 in Bezug auf die ebenfelle dem Niederdruck ausgesetzte Gegenfläche 38 auf, wobei die Gegenfläche 38 vom Durchmesser des Ventilsitzes 30 bestimmt wird. Dadurch ist der Ventilbolzen 41 zum Öffnen des Ventilsitzes 30 nicht gegen den gesamten Hochdruck im hochdruckseitigen Ventilraum 33 zu drücken. Dadurch liegt ein druckausgeglichenes Steuerventil 10 vor, bei dem die an der Stirnfläche 47 anliegende Ventilöffnungskraft im Wesentlichen nur von der Federkraft der Ventilfeder 44 bestimmt wird. Um eine stabile Schließstellung des Steuerventils 10 im Ventilsitz 30 zu garantieren, ist in der Praxis jedoch kein vollständiger Druckausgleich gewünscht. Daher wird der die Gegenfläche 38 des Ventilbolzens 41 bestimmende Durchmesser des Ventilsitze 30 geringfügig kleiner gewählt als die dem Niederdruckraum ausgesetzte Druckfläche 47 des Ventilbolzens 41. Dadurch wirkt innerhalb des Ventilraums 33 eine ständige Schließkraft auf den Ventilbolzen 41.In the switching position shown, the valve pin 41 rests with the sealing seat surface 46 on the housing-tight sealing seat 30. The closing force is applied substantially by the valve spring 44, which is supported on a collar of the mushroom-shaped valve seat body 45 and the sealing discs 43, wherein the sealing disc 43 in turn on the valve sleeve 42 and the valve sleeve 42 with a circumferential annular surface 48 on the Throttle plate 23 is supported. The annular surface 48 forms a sealing surface, so that within the annular surface 48, a low-pressure side valve chamber 49 is formed, which is hydraulically separated by the sealing action of the annular surface 48 from the high-pressure side valve chamber 33. The low-pressure-side valve chamber 49 is exposed to the valve pin 41 with an end face 47. The low-pressure side valve chamber 49 is connected via a formed in the throttle plate 23 hydraulic connection 37 to the mentioned low-pressure connection, which leads into the return line. The valve pin 41 points through the constant low-pressure connection of the low-pressure side Valve chamber 49 a pressure equalization for the end face 47 with respect to the ebenfelle low pressure exposed counter surface 38, wherein the counter surface 38 is determined by the diameter of the valve seat 30. As a result, the valve pin 41 for opening the valve seat 30 is not to be pressed against the entire high pressure in the high-pressure-side valve space 33. As a result, there is a pressure-compensated control valve 10, in which the valve opening force applied to the end face 47 is essentially determined only by the spring force of the valve spring 44. In order to guarantee a stable closed position of the control valve 10 in the valve seat 30, however, in practice, no complete pressure equalization is desired. Therefore, the diameter of the valve seat 30 determining the mating surface 38 of the valve bolt 41 is selected to be slightly smaller than the pressure surface 47 of the valve bolt 41 exposed to the low-pressure space. As a result, a permanent closing force acts on the valve bolt 41 within the valve space 33.

Zwischen Ventilbolzen 41 und Ventilhülse 42 ist eine Abdichtung 40 ausgebildet, die den Führungsspalt 50 zum hochdruckseitigen Ventilraum 33 hin verschließt. Zur Ausführung der Abdichtung 40 des Führungsspaltes 50 ist gemäß einer ersten Ausführungsform in Figur 2 die Abdichtscheiben 43 an einer zur Ventilhülse 42 weisenden Stirnfläche 54 mit einer äußeren umlaufenden Dichtkante 51 und einer inneren umlaufenden Dichtkante 52 ausgeführt, wobei die Dichtkanten 51, 52 in einem radialen Abstand an der Stirnfläche 54 verlaufen. Innerhalb des radialen Abstandes liegt der Führungsspalt 50. Die äußere Dichtkante 51 wirkt auf die Ventilhülse 42 und die inner Dichtkante 52 auf den Ventilkolben 41 ein. Zur Ausbildung der Abdichtung 40 sind an der Ventilhülse 42 und am Ventilkolben 41 für die äußere und innere Dichtkante 51, 52 jeweils dichtende Gegenflächen vorhanden. Die Dichtkanten 51, 52 sind zweckmäßigerweise als Beißkanten ausgeführt.Between valve pin 41 and valve sleeve 42, a seal 40 is formed, which closes the guide gap 50 to the high pressure side valve chamber 33 out. For the execution of the seal 40 of the guide gap 50 is according to a first embodiment in FIG. 2 the sealing disks 43 are formed on an end face 54 facing the valve sleeve 42 with an outer circumferential sealing edge 51 and an inner circumferential sealing edge 52, wherein the sealing edges 51, 52 extend at a radial distance on the end face 54. Within the radial distance is the guide gap 50. The outer sealing edge 51 acts on the valve sleeve 42 and the inner sealing edge 52 on the valve piston 41 a. In order to form the seal 40, respective sealing mating surfaces are provided on the valve sleeve 42 and on the valve piston 41 for the outer and inner sealing edges 51, 52. The sealing edges 51, 52 are expediently designed as Beißkanten.

Die dichtenden Gegenflächen werden von einer an der Ventilhülse 42 ausgebildeten äußeren Dichtfläche 56 und einer am Ventilkolben 41 ausgebildeten inneren Dichtfläche 58 gebildet, wobei auf die äußere Dichtfläche 56 die äußere Dichtkante 51 und auf die inneren Dichtfläche 58 die innere Dichtkante 52 einwirkt. Die äußere Dichtfläche 56 wird von der der Abdichtscheibe 43 zugewandten Ringfläche der Ventilhülse 42 gebildet. Zur Ausbildung der inneren Dichtfläche 58 ist der Ventilbolzen 41 mit einer Durchmesserstufung ausgeführt, wobei die in der Durchmesserstufung liegende Ringfläche die innere Dichtfläche 58 bildet.The sealing mating surfaces are formed by an outer sealing surface 56 formed on the valve sleeve 42 and an inner sealing surface 58 formed on the valve piston 41, the outer sealing surface 51 acting on the outer sealing surface 56 and the inner sealing edge 52 on the inner sealing surface 58. The outer sealing surface 56 is of the Sealing disk 43 facing annular surface of the valve sleeve 42 is formed. To form the inner sealing surface 58, the valve pin 41 is designed with a diameter graduation, wherein the annular surface lying in the diameter gradation forms the inner sealing surface 58.

Zur Ausbildung der zwei Dichtflächen 56 und 58 an der Ventilhülse 42 und dem Ventilbolzen 41 gemäß der ersten Ausführungsform oder zur Ausbildung der zwei Dichtkanten 51, 52 an der Ventilhülse 42 und am Ventilbolzen 41 gemäß der zweiten Ausführungsform ist aus Montagegründen der Ventilbolzen 41 aus zwei Teilen zusammengesetzt, nämlich gemäß Figur 2 aus einem Ventilbolzenteil 64 und einer Ventilbolzenhülse 65, wobei die Ventilhülse 42 an der Ventilbolzenhülse 65 geführt ist. Nachdem die Abdichtscheibe 43 und die Ventilfeder 44 auf das Ventilbolzenteil 64 aufgeschoben ist, wird die Ventilbolzenhülse 65 am Ventilbolzenteil 64, beispielsweise mittels Schweißen befestigt.To form the two sealing surfaces 56 and 58 on the valve sleeve 42 and the valve pin 41 according to the first embodiment or to form the two sealing edges 51, 52 on the valve sleeve 42 and the valve pin 41 according to the second embodiment is for assembly reasons, the valve pin 41 of two parts composed, namely according to FIG. 2 from a valve pin part 64 and a valve pin sleeve 65, wherein the valve sleeve 42 is guided on the valve pin sleeve 65. After the sealing disc 43 and the valve spring 44 is pushed onto the valve pin part 64, the valve pin sleeve 65 is fastened to the valve pin part 64, for example by means of welding.

Es ist aber genauso möglich, den Ventilbolzen 41 aus einem gestuften Ventilbolzenteil und einem davon getrennten, separaten Ventilsitzkörper 45 zusammenzusetzen. Zur Montage wird die Abdichtscheibe 43 und die Ventilfeder 44 vom kopplerseitigen Ende auf das Ventilbolzenteil geschoben und dann das kopplerseitigen Ende des Ventilbolzenteils in eine Bohrung des separaten Ventilsitzköpers 45 eingeschoben und dort beispielsweise mittels Schweißen befestigt.However, it is just as possible to assemble the valve pin 41 from a stepped valve pin part and a separate, separate valve seat body 45. For assembly, the sealing disc 43 and the valve spring 44 is pushed from the kopplerseitigen end to the valve pin part and then inserted the kopplerseitigen end of the valve pin part in a bore of the separate valve seat body 45 and fixed there, for example by welding.

Bei geschlossenem Dichtsitz 30 verformt der im hochdruckseitigen Ventilraum 33 anliegende Hochdruck die Abdichtscheibe 43 leicht im elastischen Bereich und presst diese mit den Dichtkanten 51, 52 an die Dichtflächen 56, 58 und verschließt somit den Führungsspalt 50. Wenn das Sterventil 10 den Ventilsitz 30 öffnet wird der Ventilbolzen 41 durch den Aktuator in Richtung Drosselplatte 23 gedrückt. Dabei taucht auch die innere Dichtfläche 58 an der Ventilhülse 42 in Richtung Drosselplatte 23 ab. Weil zeitgleich der Druck im hochdruckseitigen Ventilraum 33 sehr stark abfällt und damit der Anpressdruck auf die Abdichtscheibe 43 sinkt wird die innere Dichtfläche 58 von der inneren Dichtkkante 52 getrennt. Bei geöffnetem Ventisitz 30 ist somit der Führungsspalt 50 nicht mehr verschlossen, d. h. an der inneren Dichtflcähe 58 offen. Die im geöffneten Zustand des Steuerventils10 auftretende Leckagemeng ist jedoch sehr gering, da zu diesem Zeitpunkt nur ein sehr kleines Druckgefälle zwischen hochdruckseitigem Ventilraum 33 und niederdruckseitigem Ventilraum 49 vorliegt. Auserdem ist die Öffnungszeit des Steurventils 10 gegenüber der Schließzeit sehr klein, so dass die Leckage gegenüber eine Ausführung gänzlich ohne Abdichtung des Führungsspaltes 50 sehr klein ist. Wird der Ventilsitz 30 wieder geschlossen steigt sofort der Druck im hochdruckseitigen Ventilraum 33 wieder auf das Hochdruckniveau an. Aufgrund der Drosselung im Spalt zwischen Ventilbolzen 41 und Abdichtscheibe 43 steigt der Anpressdruck auf die Abdichtscheibe 43 und verformt diese elastisch, wodurch die Abdichtscheibe 43 wieder an die innere Dichtfläche 58 gepresst wird. Der Führungsspalt 50 als Leckagpfad ist wieder verschlossen.When the sealing seat 30 is closed, the high pressure applied in the high pressure side valve space 33 deforms the sealing disc 43 slightly in the elastic region and presses it with the sealing edges 51, 52 against the sealing surfaces 56, 58 and thus closes the guide gap 50. When the stator valve 10 opens the valve seat 30 the valve pin 41 is pressed by the actuator in the direction throttle plate 23. At the same time, the inner sealing surface 58 on the valve sleeve 42 also dips in the direction of the throttle plate 23. Because at the same time the pressure in the high pressure side valve chamber 33 drops very sharply and thus the contact pressure on the sealing disc 43 decreases, the inner sealing surface 58 is separated from the inner sealing edge 52. When the Ventisitz 30 is open thus the guide gap 50 no longer closed, ie at the inner Dichtflcähe 58 open. However, occurring in the open state of the control valve 10 Leckagemeng is very low, since at this time only a very small pressure gradient between high pressure side valve chamber 33 and niederdruckseitigem valve chamber 49 is present. Auserdem the opening time of the control valve 10 is compared to the closing time very small, so that the leakage over a design entirely without sealing the guide gap 50 is very small. When the valve seat 30 is closed again, the pressure in the high-pressure-side valve chamber 33 rises again to the high-pressure level. Due to the throttling in the gap between the valve pin 41 and sealing disc 43, the contact pressure on the sealing disc 43 increases and deforms it elastically, whereby the sealing disc 43 is pressed against the inner sealing surface 58 again. The guide gap 50 as a leakage path is closed again.

Gemäß einer weiteren nicht dargestellten Ausführungsform, ist die äußere Dichtkante 51 an der zur Abdichtscheibe 43 weisenden Stirnfläche der Ventilhülse 42 und die innere Dichtkante 52 an der von der Durchmesserstufung gebildeten Ringfläche des Ventilbolzens 41 angeordnet. Die dichtenden Gegenflächen mit der äußeren Dichtfläche 56 für die äußere Dichtkante 51 und mit der inneren Dichtfläche 58 für die innere Dichtkante 52 werden dann von der zur Ventilhülse 42 weisenden Stirnfläche 54 der Abdichtscheibe 43 gebildet.According to a further embodiment, not shown, the outer sealing edge 51 is arranged on the sealing face 43 facing the end face of the valve sleeve 42 and the inner sealing edge 52 on the annular surface of the valve pin 41 formed by the diameter graduation. The sealing mating surfaces with the outer sealing surface 56 for the outer sealing edge 51 and with the inner sealing surface 58 for the inner sealing edge 52 are then formed by the valve sleeve 42 facing end face 54 of the sealing disc 43.

Das Zusammenwirken von äußerer Dichtkante 51 und äußerer Dichtfläche 56 bildet eine äußere Dichteben 61; das Zusammenwirken von innerer Dichtkante 52 und innerer Dichtfläche 58 bildet eine innere Dichtebene 62. Wichtig für das Funktionieren der Abdichtung 40 ist, dass die äußere Dichtebene 61 und die innere Dichtebene 62 nicht exakt in der gleichen Ebene liegen, sondern, dass die innere Dichteben 62 in Richtung des Öffnungshubs zum Öffnen des Ventilsitzes 30 geringfügig unterhalb bzw. hinter der äußeren Dichtebene 61 liegt. Es muss sicher gestellt sein, dass das Steuerventil 10 im Ventilsitz 30 schließt. D. h. der nowendige Versatz der beiden Dichtebenen 61, 62 ergibt sich aus den axialen Toleranzen zur Ausbildung eines sichern Ventilsitzes 30, den axialen Toleranzen von Ventilhülse 42 und Ventilbolzenhülse 65 sowie den vorzuhaltenden Verschleiß des Ventilsitzes 30. Andererseits darf der Versatz maximal so groß sein, dass die mögliche Verformung der Abdichtscheibe 43 durch den Hochdruck nicht in den plastischen Verformungsbereich übergeht.The interaction of outer sealing edge 51 and outer sealing surface 56 forms an outer sealing edge 61; the interaction of inner sealing edge 52 and inner sealing surface 58 forms an inner sealing plane 62. Important for the functioning of the seal 40 is that the outer sealing plane 61 and the inner sealing plane 62 are not exactly in the same plane, but that the inner sealing surfaces 62 in the direction of the opening stroke for opening the valve seat 30 is slightly below or behind the outer sealing layer 61. It must be ensured that the control valve 10 in the valve seat 30 closes. Ie. the need for subsequent displacement of the two sealing planes 61, 62 results from the axial tolerances to form a secure valve seat 30, the axial tolerances of the valve sleeve 42 and valve pin sleeve 65 and the vorzuhaltenden wear of the valve seat 30. On the other hand, the maximum offset may be so large that the possible deformation of the Sealing disc 43 does not pass through the high pressure in the plastic deformation range.

In der gezeigt ersten Schaltstellung befindlichem sich im Steuerraum 27 der gleiche Druck wie im hochdruckseitigen Ventilraum 33, der seinerseits über den Verbindungskanal 34 mit Hochdruck beaufschlagt ist, so dass im Steuerraum 27 ebenfalls Hochdruck anliegt. Der Hochdruck im Steuerraum 27 wirkt über die Druckfläche 26 auf die Düsennadel 25, wodurch die Düsennadel 25 in den Düsennadelsitz gestellt ist. Die Einspritzöffnungen sind geschlossen.In the first switching position shown located in the control chamber 27, the same pressure as in the high-pressure side valve chamber 33, which in turn is acted upon via the connecting channel 34 with high pressure, so that in the control chamber 27 also applies high pressure. The high pressure in the control chamber 27 acts on the pressure surface 26 on the nozzle needle 25, whereby the nozzle needle 25 is placed in the nozzle needle seat. The injection openings are closed.

Wird der Aktuator betätigt, drückt der ventilseitige Kolben 15 des Kopplers 14 mit der Endfläche 13 auf die Gegenfläche 38 des Ventilbolzens 41. Dadurch wird die Dichtsitzfläche 46 vom Ventilsitz 30 weggedrückt und eine hydraulische Verbindung zwischen dem hochdruckseitigen Ventilraum 33 und dem Niederdruckraum 17 entsteht. Dadurch wird der Druck im hochdruckseitigen Ventilraum 33 und über die Ablaufkanal 31 auch im Steuerraum 27 entspannt, so dass die auf die Düsenadel 25 im Druckraum 19 wirkende Öffnungskraft die auf die Druckfläche 26 der Düsennadel 25 im Steuerraum 27 wirkenden Schließkraft übersteigt. Die Düsennadel 25 hebt von Düsennadelsitz ab und gibt die Einspritzöffnungen zum Einspritzen von Kraftstoff frei.If the actuator is actuated, press the valve-side piston 15 of the coupler 14 with the end face 13 on the counter surface 38 of the valve pin 41. Thus, the sealing seat surface 46 is pushed away from the valve seat 30 and a hydraulic connection between the high pressure side valve chamber 33 and the low pressure chamber 17 is formed. As a result, the pressure in the high-pressure-side valve chamber 33 and via the drainage channel 31 is also relaxed in the control chamber 27, so that the opening force acting on the nozzle needle 25 in the pressure chamber 19 exceeds the closing force acting on the pressure surface 26 of the nozzle needle 25 in the control chamber 27. The nozzle needle 25 lifts from the nozzle needle seat and releases the injection ports for injecting fuel.

Claims (10)

  1. Fuel injector for an internal combustion engine, having a control valve (10) which is actuated by an actuator and which actuates a nozzle needle (25) for the injection of fuel by virtue of the nozzle needle (25) being exposed to a control chamber (27) and the control valve (10) controlling the pressure in the control chamber (27) by opening or closing off a highpressure-side valve chamber (33), which is hydraulically connected to the control chamber (27), in the direction of a low-pressure chamber (17) by means of a valve seat (30), wherein the control valve (10) has a valve pin (41) and a valve sleeve (42), wherein the valve sleeve (42) is guided axially on a guide of the valve pin (41), wherein the guide forms a guide gap (50) between the valve pin (41) and valve sleeve (42), wherein the valve sleeve (42), under a preload exerted by a valve spring (44), abuts with an annular surface (48) against a component (23) fixed with respect to a housing and thereby hydraulically separates the highpressure-side valve chamber (33) from a low-pressure side valve chamber (49), characterized in that the guide gap (50) between the valve pin (41) and valve sleeve (42), which guide gap issues into the highpressure-side valve chamber (32), is closed off with respect to the low-pressure-side valve chamber (49) by means of a seal (40) at least when the sealing seat (30) is closed.
  2. Fuel injector according to Claim 1, characterized in that the seal (40) is formed by a sealing disc (43) which acts on the valve sleeve (42) and on the valve pin (41).
  3. Fuel injector according to Claim 1 or 2, characterized in that the seal (40) has an outer sealing edge (51) and an inner sealing edge (52), which sealing edges interact in each case with a sealing counterpart surface.
  4. Fuel injector according to Claim 3, characterized in that the outer sealing edge (51) and the inner sealing edge (52) are formed, so as to be radially spaced apart, on an end surface (54) of the sealing disc (53), in that the guide gap (50) is situated between the sealing edges (51, 52), and in that the sealing counterpart surfaces are formed by an outer sealing surface (56) formed on the valve sleeve (42) and by an inner sealing surface (58) formed on the valve piston (41).
  5. Fuel injector according to one of Claims 2 to 4, characterized in that, at least when the sealing seat (30) is closed, the outer sealing edge (51) abuts sealingly against the outer sealing surface (56) of the valve sleeve (42) and the inner sealing edge (52) abuts sealingly against the inner sealing surface (58) of the valve pin (41).
  6. Fuel injector according to Claim 3, characterized in that the outer sealing edge (51) is arranged on an end surface, which points towards the sealing disc (43), of the valve sleeve (42), and the inner sealing edge (52) is arranged on a further annular surface formed on the valve piston (41), and in that the sealing counterpart surfaces are formed by an end surface (54) formed on the sealing disc (43).
  7. Fuel injector according to one of Claims 2 to 6, characterized in that the interaction of the outer sealing edge (51) and of the outer sealing surface (56) forms an outer sealing plane (61), and the interaction of the inner sealing edge (52) and of the inner sealing surface (58) forms an inner sealing plane (62), and in that the inner sealing plane (62) is situated behind the outer sealing plane (61) as viewed in the direction of the opening stroke of the valve pin (41) for the opening of the valve seat (30).
  8. Fuel injector according to one of the preceding claims, characterized in that the valve pin (41) is of stepped design and in that, at the diameter step, there is formed an annular surface which forms the inner sealing surface (58) or a base surface for forming the inner sealing edge (51).
  9. Fuel injector according to one of the preceding claims, characterized in that the valve pin (41) is formed in at least two parts and has a valve pin part (64) and a valve pin sleeve (65), and in that, after the insertion of the sealing disc (43) and of the valve spring (44), the two parts (64, 65) of the valve piston (41) are connected.
  10. Fuel injector according to one of the preceding claims, characterized in that the valve pin (41) is formed in at least two parts and has a stepped valve pin part (64) and a valve seat body (45), and in that, after the insertion of the sealing disc (41) and of the valve spring (44), the two parts (64, 45) of the valve piston (41) are connected.
EP20110192957 2010-12-16 2011-12-12 Fuel injector with pressure-equalised control valve Not-in-force EP2466107B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010063183 DE102010063183A1 (en) 2010-12-16 2010-12-16 Fuel injector with pressure compensated control valve

Publications (2)

Publication Number Publication Date
EP2466107A1 EP2466107A1 (en) 2012-06-20
EP2466107B1 true EP2466107B1 (en) 2013-07-17

Family

ID=45318959

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110192957 Not-in-force EP2466107B1 (en) 2010-12-16 2011-12-12 Fuel injector with pressure-equalised control valve

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EP (1) EP2466107B1 (en)
DE (1) DE102010063183A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9016603B2 (en) 2013-01-23 2015-04-28 Caterpillar Inc. Fuel injector
DE102016202945A1 (en) * 2016-02-25 2017-08-31 Robert Bosch Gmbh Electromagnetically actuated inlet valve and high-pressure pump with inlet valve
CN106704067B (en) * 2017-01-25 2019-05-14 中国第一汽车股份有限公司 The weak anti-oil return fuel injection device of leakage

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008001330A1 (en) 2008-04-23 2009-10-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102008041167A1 (en) * 2008-08-12 2010-02-18 Robert Bosch Gmbh Fuel injector for storage-type injector systems for injecting pressurized fuel into combustion chamber of internal combustion engine, has injector housing, which comprises internal high-pressure volume for injecting highly pressurized fuel
DE102009001099A1 (en) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Fuel injection valve for internal-combustion engine, has valve unit partially guided in sleeve, and spring element surrounding sleeve and subjecting sleeve with compressive force for position fixation in axial and/or radial directions
DE102009002742A1 (en) * 2009-04-30 2010-11-04 Robert Bosch Gmbh Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, particularly common rail injector, comprises single or multipart injection valve element for opening and closing injection opening

Also Published As

Publication number Publication date
DE102010063183A1 (en) 2012-06-21
EP2466107A1 (en) 2012-06-20

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