EP1055062B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1055062B1
EP1055062B1 EP99957931A EP99957931A EP1055062B1 EP 1055062 B1 EP1055062 B1 EP 1055062B1 EP 99957931 A EP99957931 A EP 99957931A EP 99957931 A EP99957931 A EP 99957931A EP 1055062 B1 EP1055062 B1 EP 1055062B1
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EP
European Patent Office
Prior art keywords
valve
fuel injection
guide
hole
fuel
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.)
Expired - Lifetime
Application number
EP99957931A
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German (de)
French (fr)
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EP1055062A1 (en
Inventor
Yalcin Ertem
Ergün Filiz
Güngör Yurtseven
Heinz Stutzenberger
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of Claim 1 from.
  • known fuel injector is a piston-shaped valve member axially displaceable in one Guide bore of a valve body.
  • the valve member has one at its lower, combustion chamber end conical valve sealing surface with which it with a stationary valve seat at the closed end of the Guide hole cooperates.
  • the known Fuel injector of the valve seat surface downstream two injection ports arranged downstream from the closed End of the pilot hole starting in the combustion chamber of the Internal combustion engine open. The fuel inflow too these injection openings is thereby by the Sealing cross section between valve seat and Valve sealing surface controlled.
  • the valve member of the known The fuel injector has two guide areas with which it can slide on the wall of the Guide hole is guided.
  • there the upper management area takes over next to the safe Valve link guidance also seals the pressure chamber opposite a spring chamber, in which the valve member in Valve spring acting on the closing direction is.
  • the valve member has a second lower guide region in an area facing the combustion chamber, the ring collar is formed with which the valve member with a Diameter reduction of the guide hole cooperates.
  • the lower one which is designed as a ring collar, separates Guiding area between the valve member and the Wall of the guide hole formed by the pressure chamber outgoing annular gap from an underlying, to the Valve seat surface opening lower pressure chamber closed fuel injector.
  • the collar of the lower guide area of the Valve member from the overlap with the Diameter reduction of the guide bore and opens such an unrestricted flow cross section between the Annular gap and the pressure chamber below.
  • Throttle cross section is the known Fuel injection valve as a ring throttle gap between the Ring collar of the lower guide area and the Reduced diameter of the guide bore formed.
  • the fuel injector according to the invention for Internal combustion engines with the characteristic features of the Claim 1 has the advantage that the Throttle connection cross section between the annular gap and the pressure chamber at the bottom of the fuel injection valve easily and reproducibly producible is. This is due to the training according to the invention of the throttle connection cross section as a throttle bore reached, which penetrates the valve member obliquely, the Inlet opening of the throttle bore in the area of Annular gap and the outlet opening in the area of the bottom lying pressure chamber is arranged.
  • Throttle bore contrary to the state of the art, independently of fit tolerances between the valve member and the Geometry of the pilot hole is.
  • the Throttle bore in the valve member consistently the same Have throttle cross-section, but it is also possible to design the throttle bore in two or more stages, then the smallest bore diameter Throttle flow cross section determined. This can smallest throttle bore cross section at the inlet of the Throttle bore, in its central area or at the outlet the throttle bore (as shown in the exemplary embodiment) be provided.
  • the design of the throttle bore as two or Multi-stage drilling has the advantage that a good flow with sufficient throttling effect is achievable, the difference in diameter between the large and the smallest throttle diameter Hole and the respective hole lengths between larger bore part and throttle cross section in constructive simply the desired throttling effect for everyone Can set fuel injector type.
  • Fuel injector is provided by providing a Ring groove at the transition between the lower one Leadership area forming a ring collar and one itself subsequent, reduced cross-sectional area of the Valve member reached.
  • This annular groove has the advantage that the lower edge of the collar, which is a control edge forms, sharp-edged is worked out, so that precise control in cooperation with the corresponding paragraph of the guide hole can be achieved.
  • Fuel injector is provided by Recesses on the valve member in the area below Pressure chamber reached, this, preferably as Surface grinding formed recesses after replacement the ring collar from the hole sales area a better one unobstructed overflow from the annular gap into the allow the lower pressure chamber so that the under high Pressurized fuel from the fuel supply channel over the annular gap and the pressure space below can flow evenly to the injection openings.
  • Fuel injection valve for internal combustion engines is in shown in the drawing and will be described in more detail below explained.
  • FIG. 1 shows a first embodiment of the Fuel injection valve in a longitudinal section through the Valve body and the valve member guided therein and the Figure 2 shows an enlarged section of Figure 1 in essential area of the combustion chamber facing the invention Valve body with the representation of the geometry of it guided valve member at the end facing the combustion chamber.
  • Fuel injector for internal combustion engines has a valve body 1 with its lower free end in a manner not shown in the combustion chamber supplying internal combustion engine and that with its upper end facing away from the combustion chamber against one also not shown valve holding body is tense.
  • the valve body 1 has one of its upper end face 3 outgoing, as an axial Blind bore trained guide bore 5.
  • this Guide bore 5 is a piston-shaped valve member 7 axially slidably guided at its lower end of the combustion chamber has a conical valve sealing surface 9 with which it is connected to a closed end of the Guide bore 5 formed stationary valve seat 11th interacts.
  • valve seat surface 11 downstream of the between the line of contact between Valve seat surface 11 and valve sealing surface 9 formed Sealing cross-section from an injection opening 13, which in the Combustion chamber of the internal combustion engine to be supplied opens.
  • the exemplary embodiment has only one Injection opening, but it is alternatively also possible to provide a plurality of injection openings, these also alternatively from below the valve member 7 formed blind hole of the guide hole 5 can discharge.
  • the piston-shaped valve member 7 has two guide areas with which it can slide on the wall of the Guide bore 5 is guided. There is a first top Guide area 15 at the end of the Valve member 7 provided in one Upper region of the guide bore 5 facing away from the combustion chamber is led. The upper guide area 15 of the valve member 7 goes over a, forming a pressure shoulder 17 in a valve member shaft part 19 with reduced diameter about. The pressure shoulder 17 is in an overhead Pressure chamber 21 arranged by a Cross-sectional expansion of the guide bore 5 is formed and into which a high-pressure fuel inlet channel 23 opens. This high-pressure fuel inlet channel 23 is not shown in FIG to a high-pressure injection line connected, on the other hand by a High-pressure fuel pump discharges through the fuel a storage tank under high pressure the individual Fuel injectors is supplied.
  • a second lower guide area at the end near the combustion chamber of the valve member 7 is formed as an annular collar 25, the its cylindrical outer wall surface with the wall of a Bore paragraph 27 of the guide bore 5 cooperates. This separates the second lower guide area forming collar 25 of the valve member 7 one between the Valve member part 19 and the wall of the guide bore 5 formed annular gap 29 when closed Fuel injector from a downstream below of the collar 25 arranged below, to the Valve seat surface 11 opening pressure chamber 31.
  • the annular collar 25 forms, as enlarged in FIG. 2 shown with its lower combustion chamber facing Boundary edge a control edge 33, with which he with a bore shoulder edge 35 facing away from the combustion chamber Hole paragraph 27 cooperates.
  • control edge 33 and bore shoulder edge 35 arranged so that the Control edge 33 on the collar 25 of the valve member 7 at its upward opening stroke movement the overhead Bore heel edge 35 runs over and so one Flow cross section between the annular gap 29 and the underlying pressure chamber 31 releases.
  • Valve member 7 in the area of the pressure chamber 31 below Recesses in the form of surface grinding 39 incorporated over which the flow cross section in this Area is enlarged again.
  • a throttle bore 41 in the valve member 7 intended for filling the pressure in the pressure chamber 31 below with valve member 7 resting on the valve seat surface 11 furthermore a throttle bore 41 in the valve member 7 intended.
  • the throttle bore 41 is so inclined arranged that its inlet opening in the annular gap 29th and its outlet opening into the pressure chamber 31 below empties. Furthermore, the throttle bore 41 as two-stage bore formed, the diameter larger bore section in the annular gap 29 and in Diameter smaller bore section in the below Pressure chamber 31 opens. The small, throttling diameter and its placement within the Throttle bore 41 the throttle effect at Adjust fuel flow in a simple manner.
  • the fuel injector according to the invention for Internal combustion engines work in the following way.
  • a valve spring 45 holds when the injection valve is closed the valve member 15 via a valve plate 43 with its Valve sealing surface 9 in contact with the valve seat surface 11, see above that a flow cross-section to the injection opening 13 is closed.
  • the collar 25 is Valve member 7 immersed in the bore paragraph 27 and separates the pressure chamber 31 below from the annular gap 29, which on the other hand opens into the overhead pressure chamber 21.
  • the one in the high-pressure fuel supply channel 23, in the overhead Pressure chamber 21 and standing pressure of the pending in the annular gap 29 Fuel is also in the throttle bore 41 pressure chamber 31 built up.
  • the high-pressure fuel injection at the injection valve is by supplying high pressure Fuel from the injection pump via the High-pressure fuel inlet channel 23 in the overhead Pressure chamber 21 initiated.
  • the valve sealing surface 9 lifts from the valve seat 11 and gives the flow cross-section to the injection opening 13 free, so that the pressure chamber 31 pending fuel via the injection opening 13 in the Combustion chamber of the internal combustion engine is injected.
  • the fuel injector closes in known way by interrupting the High-pressure fuel supply in the upper pressure chamber 21, in the consequence of which is the pressure present at the injection valve falls below the necessary opening pressure so that the Valve spring 45 now the valve member 7 in contact with the Valve seat 11 moves back, now over the throttle bore 41 of the pressure build-up described at the beginning again.

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

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen gemäß der Gattung des Oberbegriffs des Patentanspruchs 1 aus. Bei einem derartigen aus der Schrift US-4,987,887 bekannten Kraftstoffeinspritzventil ist ein kolbenförmiges Ventilglied axial verschiebbar in einer Führungsbohrung eines Ventilkörpers geführt. Das Ventilglied weist dabei an seinem unteren, brennraumseitigen Ende eine konische Ventildichtfläche auf, mit der es mit einer ortsfesten Ventilsitzfläche am geschlossenen Ende der Führungsbohrung zusammenwirkt. Dabei sind bei dem bekannten Kraftstoffeinspritzventil der Ventilsitzfläche stromabwärts zwei Einspritzöffnungen nachgeordnet, die vom geschlossenen Ende der Führungsbohrung ausgehend in den Brennraum der Brennkraftmaschine münden. Die Kraftstoffzuströmung zu diesen Einspritzöffnungen wird dabei durch den Dichtquerschnitt zwischen Ventilsitzfläche und Ventildichtfläche gesteuert. Das Ventilglied des bekannten Kraftstoffeinspritzventils weist dabei zwei Führungsbereiche auf, mit denen es gleitverschiebbar an der Wand der Führungsbohrung geführt ist. Dabei ist ein erster oberer Führungsbereich am brennraumabgewandten Ende des Ventilgliedes vorgesehen, der sich dabei oberhalb eines Kraftstoffdruckraumes erstreckt, der durch eine Querschnittserweiterung der Führungsbohrung gebildet ist und in den ein Kraftstoffhochdruckzulaufkanal einmündet. Dabei übernimmt der obere Führungsbereich neben der sicheren Ventilgliedführung auch die Abdichtung des Druckraumes gegenüber einem Federraum, in dem eine das Ventilglied in Schließrichtung beaufschlagende Ventilfeder untergebracht ist. Zusätzlich zu diesem oberen ersten Führungsbereich weist das Ventilglied einen zweiten unteren Führungsbereich in einem brennraumzugewandten Bereich auf, der als Ringbund ausgebildet ist, mit dem das Ventilglied mit einer Durchmesserverringerung der Führungsbohrung zusammenwirkt. Dabei trennt der als Ringbund ausgebildete untere Führungsbereich einen zwischen dem Ventilgliedschaft und der Wand der Führungsbohrung gebildeten, vom Druckraum ausgehenden Ringspalt von einem untenliegenden, an die Ventilsitzfläche mündenden unteren Druckraum bei geschlossenem Kraftstoffeinspritzventil. Während der nach oben gerichteten Öffnungshubbewegung des Ventilgliedes taucht der Ringbund des unteren Führungsbereiches des Ventilgliedes aus der Überdeckung mit der Durchmesserverringerung der Führungsbohrung aus und öffnet so einen ungedrosselten Durchströmquerschnitt zwischen dem Ringspalt und dem untenliegenden Druckraum.The invention relates to a fuel injection valve for Internal combustion engines according to the preamble of Claim 1 from. In such a case from Scripture US 4,987,887 known fuel injector is a piston-shaped valve member axially displaceable in one Guide bore of a valve body. The valve member has one at its lower, combustion chamber end conical valve sealing surface with which it with a stationary valve seat at the closed end of the Guide hole cooperates. The known Fuel injector of the valve seat surface downstream two injection ports arranged downstream from the closed End of the pilot hole starting in the combustion chamber of the Internal combustion engine open. The fuel inflow too these injection openings is thereby by the Sealing cross section between valve seat and Valve sealing surface controlled. The valve member of the known The fuel injector has two guide areas with which it can slide on the wall of the Guide hole is guided. There is a first top Guide area at the end of the Valve member provided, which is above a Fuel pressure chamber extends through a Cross-sectional expansion of the guide bore is formed and into which a high-pressure fuel inlet duct opens. there the upper management area takes over next to the safe Valve link guidance also seals the pressure chamber opposite a spring chamber, in which the valve member in Valve spring acting on the closing direction is. In addition to this top first management area the valve member has a second lower guide region in an area facing the combustion chamber, the ring collar is formed with which the valve member with a Diameter reduction of the guide hole cooperates. The lower one, which is designed as a ring collar, separates Guiding area between the valve member and the Wall of the guide hole formed by the pressure chamber outgoing annular gap from an underlying, to the Valve seat surface opening lower pressure chamber closed fuel injector. During the after upward opening stroke movement of the valve member the collar of the lower guide area of the Valve member from the overlap with the Diameter reduction of the guide bore and opens such an unrestricted flow cross section between the Annular gap and the pressure chamber below.

Zur Kraftstoffversorgung des untenliegenden Druckraumes ist dabei bei geschlossenem Kraftstoffeinspritzventil, das heißt bei am Ventilsitz anliegendem Ventilglied ein Drosseldurchtrittsquerschnitt zwischen dem Ringspalt und dem untenliegenden Druckraum vorgesehen, über den Kraftstoff in den untenliegenden Druckraum einströmen kann. Dieser Drosselquerschnitt ist dabei beim bekannten Kraftstoffeinspritzventil als Ringdrosselspalt zwischen dem Ringbund des unteren Führungsbereiches und der Durchmesserverringerung der Führungsbohrung ausgebildet. For supplying fuel to the pressure chamber below doing so with the fuel injector closed, that is with the valve member in contact with the valve seat Throttle cross section between the annular gap and the pressure chamber provided below, via the fuel in can flow into the pressure chamber below. This Throttle cross section is the known Fuel injection valve as a ring throttle gap between the Ring collar of the lower guide area and the Reduced diameter of the guide bore formed.

Diese Ausbildung des Drosselverbindungsquerschnittes zwischen dem Ringspalt und dem untenliegenden Druckraum hat bei dem bekannten Kraftstoffeinspritzventil für Brennkraftmaschinen jedoch den Nachteil, daß es aufgrund von Oberflächentoleranzen am Ringbund und an der Führungsbohrungswand schwierig ist, einen korrekten Drosselquerschnitt an verschiedenen Kraftstoffeinspritzventilen reproduzierbar einzustellen. Dabei erfordert diese Art der Herstellung eines korrekten Drosselspaltes insbesondere einen hohen Aufwand hinsichtlich der Fertigungsgenauigkeit und ist somit nur mit hohem Aufwand und Kosten erzielbar. Da der präzisen Einstellung des Drosselquerschnittes jedoch hinsichtlich einer korrekten Funktion des Kraftstoffeinspritzventils, insbesondere der Einstellung der Voreinspritzung eine hohe Bedeutung zukommt, ist die Möglichkeit des Einstellens über den Ringdrosselspalt zwischen Führungsbund und Wand der Führungsbohrung nicht ausreichend.This design of the throttle connection cross section between the annular gap and the pressure space below in the known fuel injection valve for However, internal combustion engines have the disadvantage that it is due to Surface tolerances on the ring collar and on the Guide hole wall is difficult to get a correct one Throttle cross section at different Adjust fuel injection valves reproducibly. In doing so, this type of manufacturing requires a correct one Throttle gap in particular a high effort in terms the manufacturing accuracy and is therefore only with high Effort and costs achievable. Because of the precise setting of the throttle cross section, however, with regard to a correct one Function of the fuel injector, especially the Pre-injection setting is of great importance is the possibility of setting via the Ring throttle gap between the guide collar and the wall of the Guide hole not sufficient.

Aus der Schrift US 5 769 319 ist darüber hinaus ein Kraftstoffeinspritzventil bekannt, bei dem das Ventilglied zwei Führungsbereiche aufweist, die denselben Durchmesser aufweisen. Der Kraftstoff, der zwischen den beiden Führungsbereichen eingebracht wird, fließt durch eine im Ventilglied ausgebildete Drosselbohrung in Richtung eines Druckraums, von dem die Einspritzöffnungen abgehen. Die Einspritzung erfolgt durch langsamen Druckaufbau im Druckraum, so dass sich bis zum Austauchen des unteren Führungsbereichs aus einem entsprechenden Führungsabschnitt, was bei einem bestimmten Hub des Ventilglieds eintritt, nur eine geringe Einspritzrate einstellt.From US 5 769 319 is also a fuel injector known in which the valve member two Has guide areas that have the same diameter. The fuel that runs between the two leadership areas is introduced, flows through a formed in the valve member Throttle bore towards a pressure chamber, from where the injection openings go. The injection takes place due to slow pressure build-up in the pressure chamber, so that up to for replacing the lower guide area from a corresponding one Guide section what at a given stroke of the valve member occurs, only a low injection rate established.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der Drosselverbindungsquerschnitt zwischen dem Ringspalt und dem untenliegenden Druckraum am Kraftstoffeinspritzventil einfach und mit hoher Genauigkeit reproduzierbar herstellbar ist. Dies wird dabei durch die erfindungsgemäße Ausbildung des Drosselverbindungsquerschnittes als Drosselbohrung erreicht, die das Ventilglied schräg durchdringt, wobei die Eintrittsöffnung der Drosselbohrung im Bereich des Ringspaltes und die Austrittsöffnung im Bereich des unten liegenden Druckraumes angeordnet ist. Dabei läßt sich eine derartige Drosselbohrung fertigungstechnisch mit geringem Aufwand sehr genau fertigen, wobei insbesondere auch sehr kleine Streubreiten bei einer Serienfertigung reduzierbar sind. Besonders vorteilhaft ist, daß eine derartige Drosselbohrung, entgegen dem Stand der Technik, unabhängig von Passungstoleranzen zwischen dem Ventilglied und der Geometrie der Führungsbohrung ist. Dabei kann die Drosselbohrung im Ventilglied durchgängig den gleichen Drosselquerschnitt aufweisen, es ist jedoch auch möglich, die Drosselbohrung zwei- oder mehrstufig auszubilden wobei, dann der kleinste Bohrungsdurchmesser den Drosseldurchströmquerschnitt bestimmt. Dabei kann dieser kleinste Drosselbohrungsquerschnitt am Eintritt der Drosselbohrung, in deren mittigem Bereich oder am Austritt der Drosselbohrung (wie im Ausführungsbeispiel dargestellt) vorgesehen sein. Die Ausbildung der Drosselbohrung als zweioder mehrstufige Bohrung hat dabei den Vorteil, daß ein gutes Durchströmen bei ausreichender Drosselwirkung erzielbar ist, wobei sich über die Durchmesserdifferenz zwischen dem großen und dem kleinsten Drosseldurchmesser der Bohrung sowie den jeweiligen Bohrungslängen zwischen größerem Bohrungsteil und Drosselquerschnitt in konstruktiv einfacher Weise die gewünschte Drosselwirkung für jeden Kraftstoffeinspritzventiltyp einstellen läßt.The fuel injector according to the invention for Internal combustion engines with the characteristic features of the Claim 1 has the advantage that the Throttle connection cross section between the annular gap and the pressure chamber at the bottom of the fuel injection valve easily and reproducibly producible is. This is due to the training according to the invention of the throttle connection cross section as a throttle bore reached, which penetrates the valve member obliquely, the Inlet opening of the throttle bore in the area of Annular gap and the outlet opening in the area of the bottom lying pressure chamber is arranged. One can such throttle bore manufacturing technology with little Manufacture effort very precisely, especially very well small spreads can be reduced in series production are. It is particularly advantageous that such Throttle bore, contrary to the state of the art, independently of fit tolerances between the valve member and the Geometry of the pilot hole is. The Throttle bore in the valve member consistently the same Have throttle cross-section, but it is also possible to design the throttle bore in two or more stages, then the smallest bore diameter Throttle flow cross section determined. This can smallest throttle bore cross section at the inlet of the Throttle bore, in its central area or at the outlet the throttle bore (as shown in the exemplary embodiment) be provided. The design of the throttle bore as two or Multi-stage drilling has the advantage that a good flow with sufficient throttling effect is achievable, the difference in diameter between the large and the smallest throttle diameter Hole and the respective hole lengths between larger bore part and throttle cross section in constructive simply the desired throttling effect for everyone Can set fuel injector type.

Es ist somit mit dem erfindungsgemäßen Kraftstoffeinspritzventil in konstruktiv einfacher Weise möglich, den für die Formung des Einspritzverlaufs am Einspritzventil wichtigen Drosselquerschnitt zwischen dem Ringspalt und dem untenliegenden Druckraum präzise und reproduzierbar einzustellen.It is thus with the invention Fuel injection valve in a structurally simple manner possible for the formation of the injection process on Injector important throttle cross section between the Annular gap and the pressure space below and precise adjust reproducible.

Ein weiterer Vorteil des erfindungsgemäßen Kraftstoffeinspritzventils wird durch das Vorsehen einer Ringnut am Übergang zwischen dem, den unteren Führungsbereich bildenden Ringbund und einem sich anschließenden, im Querschnitt verringerten Bereich des Ventilgliedes erreicht. Dabei hat diese Ringnut den Vorteil, daß die untere Kante des Ringbundes, die eine Steuerkante bildet, scharfkantiger herausgearbeitet ist, so daß sich eine präzise Steuerung im Zusammenwirken mit dem entsprechenden Absatz der Führungsbohrung erzielen läßt.Another advantage of the invention Fuel injector is provided by providing a Ring groove at the transition between the lower one Leadership area forming a ring collar and one itself subsequent, reduced cross-sectional area of the Valve member reached. This annular groove has the advantage that the lower edge of the collar, which is a control edge forms, sharp-edged is worked out, so that precise control in cooperation with the corresponding paragraph of the guide hole can be achieved.

Ein weiterer Vorteil des erfindungsgemäßen Kraftstoffeinspritzventils wird durch das Vorsehen von Ausnehmungen am Ventilglied im Bereich des untenliegenden Druckraumes erreicht, wobei diese, vorzugsweise als Flächenanschliffe ausgebildeten Ausnehmungen nach Austauchen des Ringbundes aus der Bohrungsabsatzfläche ein besseres ungehindertes Überströmen aus dem Ringspalt in den untenliegenden Druckraum ermöglichen, so daß der unter hohem Druck stehende Kraftstoff aus dem Kraftstoffzulaufkanal über den Ringspalt und den untenliegenden Druckraum möglichst gleichmäßig zu den Einspritzöffnungen überströmen kann.Another advantage of the invention Fuel injector is provided by Recesses on the valve member in the area below Pressure chamber reached, this, preferably as Surface grinding formed recesses after replacement the ring collar from the hole sales area a better one unobstructed overflow from the annular gap into the allow the lower pressure chamber so that the under high Pressurized fuel from the fuel supply channel over the annular gap and the pressure space below can flow evenly to the injection openings.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the The invention relates to the description of Drawing and the claims can be found.

Zeichnungdrawing

Ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen ist in der Zeichnung dargestellt und wird im folgenden näher erläutert.An embodiment of the invention Fuel injection valve for internal combustion engines is in shown in the drawing and will be described in more detail below explained.

Es zeigen die Figur 1 ein erstes Ausführungsbeispiel des Kraftstoffeinspritzventils in einem Längsschnitt durch den Ventilkörper und das darin geführte Ventilglied und die Figur 2 einen vergrößerten Ausschnitt aus der Figur 1 im erfindungswesentlichen brennraumzugewandten Bereich des Ventilkörpers mit der Darstellung der Geometrie des darin geführten Ventilgliedes an dessen brennraumzugewandtem Ende.1 shows a first embodiment of the Fuel injection valve in a longitudinal section through the Valve body and the valve member guided therein and the Figure 2 shows an enlarged section of Figure 1 in essential area of the combustion chamber facing the invention Valve body with the representation of the geometry of it guided valve member at the end facing the combustion chamber.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in der Figur 1 in einem vereinfachten Schnitt dargestellte Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen weist einen Ventilkörper 1 auf, der mit seinem unteren freien Ende in nicht näher dargestellter Weise in den Brennraum der zu versorgenden Brennkraftmaschine ragt und der mit seiner oberen, brennraumabgewandten Stirnseite gegen einen ebenfalls nicht näher dargestellten Ventilhaltekörper verspannt ist. Der Ventilkörper 1 weist dabei eine von seiner oberen Stirnfläche 3 ausgehende, als axiale Sackbohrung ausgebildete Führungsbohrung 5 auf. In dieser Führungsbohrung 5 ist ein kolbenförmiges Ventilglied 7 axial verschiebbar geführt, das an seinem unteren brennraumseitigen Ende eine konische Ventildichtfläche 9 aufweist, mit der es mit einer am geschlossenen Ende der Führungsbohrung 5 gebildeten ortsfesten Ventilsitzfläche 11 zusammenwirkt. Dabei führt von dieser Ventilsitzfläche 11 stromabwärts des zwischen der Berührungslinie zwischen Ventilsitzfläche 11 und Ventildichtfläche 9 gebildeten Dichtquerschnittes eine Einspritzöffnung 13 ab, die in den Brennraum der zu versorgenden Brennkraftmaschine mündet. Dabei weist das Ausführungsbeispiel lediglich eine Einspritzöffnung auf, es ist alternativ jedoch auch möglich, eine Vielzahl von Einspritzöffnungen vorzusehen, wobei diese zudem alternativ vom unterhalb des Ventilgliedes 7 gebildeten Sackloches der Führungsbohrung 5 abführen können.1 in a simplified section illustrated embodiment of the invention Fuel injector for internal combustion engines has a valve body 1 with its lower free end in a manner not shown in the combustion chamber supplying internal combustion engine and that with its upper end facing away from the combustion chamber against one also not shown valve holding body is tense. The valve body 1 has one of its upper end face 3 outgoing, as an axial Blind bore trained guide bore 5. In this Guide bore 5 is a piston-shaped valve member 7 axially slidably guided at its lower end of the combustion chamber has a conical valve sealing surface 9 with which it is connected to a closed end of the Guide bore 5 formed stationary valve seat 11th interacts. This leads from this valve seat surface 11 downstream of the between the line of contact between Valve seat surface 11 and valve sealing surface 9 formed Sealing cross-section from an injection opening 13, which in the Combustion chamber of the internal combustion engine to be supplied opens. The exemplary embodiment has only one Injection opening, but it is alternatively also possible to provide a plurality of injection openings, these also alternatively from below the valve member 7 formed blind hole of the guide hole 5 can discharge.

Das kolbenförmige Ventilglied 7 weist zwei Führungsbereiche auf, mit denen es gleitverschiebbar an der Wand der Führungsbohrung 5 geführt ist. Dabei ist ein erster oberer Führungsbereich 15 am brennraumabgewandten Ende des Ventilgliedes 7 vorgesehen, der in einem brennraumabgewandten oberen Bereich der Führungsbohrung 5 geführt ist. Der obere Führungsbereich 15 des Ventilgliedes 7 geht über einen, eine Druckschulter 17 bildenden Absatz in einen, im Durchmesser verringerten Ventilgliedschaftteil 19 über. Dabei ist die Druckschulter 17 in einem obenliegenden Druckraum 21 angeordnet, der durch eine Querschnittserweiterung der Führungsbohrung 5 gebildet ist und in den ein Kraftstoffhochdruckzulaufkanal 23 einmündet. Dieser Kraftstoffhochdruckzulaufkanal 23 ist dabei in nicht näher gezeigter Weise an eine Hochdruckeinspritzleitung angeschlossen, die andererseits von einer Kraftstoffhochdruckpumpe abführt, über die Kraftstoff aus einem Vorratstank unter hohem Druck den einzelnen Kraftstoffeinspritzventilen zugeführt wird.The piston-shaped valve member 7 has two guide areas with which it can slide on the wall of the Guide bore 5 is guided. There is a first top Guide area 15 at the end of the Valve member 7 provided in one Upper region of the guide bore 5 facing away from the combustion chamber is led. The upper guide area 15 of the valve member 7 goes over a, forming a pressure shoulder 17 in a valve member shaft part 19 with reduced diameter about. The pressure shoulder 17 is in an overhead Pressure chamber 21 arranged by a Cross-sectional expansion of the guide bore 5 is formed and into which a high-pressure fuel inlet channel 23 opens. This high-pressure fuel inlet channel 23 is not shown in FIG to a high-pressure injection line connected, on the other hand by a High-pressure fuel pump discharges through the fuel a storage tank under high pressure the individual Fuel injectors is supplied.

Ein zweiter unterer Führungsbereich am brennraumnahen Ende des Ventilgliedes 7 ist als Ringbund 25 ausgebildet, der mit seiner zylindrischen Außenwandfläche mit der Wand eines Bohrungsabsatzes 27 der Führungsbohrung 5 zusammenwirkt. Dabei trennt der den zweiten unteren Führungsbereich bildende Ringbund 25 des Ventilgliedes 7 einen zwischen dem Ventilgliedschaftteil 19 und der Wand der Führungsbohrung 5 gebildeten Ringspalt 29 bei geschlossenem Kraftstoffeinspritzventil von einem stromabwärts unterhalb des Ringbundes 25 angeordneten untenliegenden, an die Ventilsitzfläche 11 mündenden Druckraum 31.A second lower guide area at the end near the combustion chamber of the valve member 7 is formed as an annular collar 25, the its cylindrical outer wall surface with the wall of a Bore paragraph 27 of the guide bore 5 cooperates. This separates the second lower guide area forming collar 25 of the valve member 7 one between the Valve member part 19 and the wall of the guide bore 5 formed annular gap 29 when closed Fuel injector from a downstream below of the collar 25 arranged below, to the Valve seat surface 11 opening pressure chamber 31.

Der Ringbund 25 bildet, wie in der Figur 2 vergrößert dargestellt, mit seiner unteren brennraumzugewandten Begrenzungskante eine Steuerkante 33, mit der er mit einer brennraumabgewandten Bohrungsabsatzkante 35 des Bohrungsabsatzes 27 zusammenwirkt. Dabei sind Steuerkante 33 und Bohrungsabsatzkante 35 so angeordnet, daß die Steuerkante 33 am Ringbund 25 des Ventilgliedes 7 bei dessen nach oben gerichteter Öffnungshubbewegung die obenliegende Bohrungsabsatzkante 35 überfährt und so einen Durchströmquerschnitt zwischen dem Ringspalt 29 und dem untenliegenden Druckraum 31 freigibt. Dabei weist das Ventilglied 7 für eine präzisere Herausarbeitung der Steuerkante 33 am Ringbund 25 zwischen dem Übergang des Ringbundes 25 zum Ventilgliedschaft im untenliegenden Druckraum 31 eine Ringnut 37 auf. Desweiteren sind am Ventilglied 7 im Bereich des untenliegenden Druckraumes 31 Ausnehmungen in Form von Flächenanschliffen 39 eingearbeitet, über die der Durchströmquerschnitt in diesem Bereich noch einmal vergrößert wird.The annular collar 25 forms, as enlarged in FIG. 2 shown with its lower combustion chamber facing Boundary edge a control edge 33, with which he with a bore shoulder edge 35 facing away from the combustion chamber Hole paragraph 27 cooperates. Here are control edge 33 and bore shoulder edge 35 arranged so that the Control edge 33 on the collar 25 of the valve member 7 at its upward opening stroke movement the overhead Bore heel edge 35 runs over and so one Flow cross section between the annular gap 29 and the underlying pressure chamber 31 releases. This points Valve member 7 for a more precise elaboration of the Control edge 33 on the collar 25 between the transition of Ring collar 25 to the valve member in the bottom Pressure chamber 31 an annular groove 37. Furthermore, on Valve member 7 in the area of the pressure chamber 31 below Recesses in the form of surface grinding 39 incorporated over which the flow cross section in this Area is enlarged again.

Zur Kraftstoffbefüllung des untenliegenden Druckraumes 31 bei an der Ventilsitzfläche 11 anliegendem Ventilglied 7 ist desweiteren eine Drosselbohrung 41 im Ventilglied 7 vorgesehen. Die Drosselbohrung 41 ist dabei derart schräg angeordnet, daß ihre Eintrittsöffnung in den Ringspalt 29 und ihre Austrittsöffnung in den untenliegenden Druckraum 31 mündet. Desweiteren ist die Drosselbohrung 41 als zweistufige Bohrung ausgebildet, wobei der im Durchmesser größere Bohrungsabschnitt in den Ringspalt 29 und der im Durchmesser kleinere Bohrungsabschnitt in den untenliegenden Druckraum 31 einmündet. Dabei läßt sich über den kleinen, drosselnden Durchmesser und dessen Anordnung innerhalb der Drosselbohrung 41 die Drosselwirkung beim Kraftstoffdurchtritt in einfacher Weise einstellen.For filling the pressure in the pressure chamber 31 below with valve member 7 resting on the valve seat surface 11 furthermore a throttle bore 41 in the valve member 7 intended. The throttle bore 41 is so inclined arranged that its inlet opening in the annular gap 29th and its outlet opening into the pressure chamber 31 below empties. Furthermore, the throttle bore 41 as two-stage bore formed, the diameter larger bore section in the annular gap 29 and in Diameter smaller bore section in the below Pressure chamber 31 opens. The small, throttling diameter and its placement within the Throttle bore 41 the throttle effect at Adjust fuel flow in a simple manner.

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen arbeitet in folgender Weise.The fuel injector according to the invention for Internal combustion engines work in the following way.

Bei geschlossenem Einspritzventil hält eine Ventilfeder 45 das Ventilglied 15 über einen Ventilteller 43 mit seiner Ventildichtfläche 9 in Anlage an der Ventilsitzfläche 11, so daß ein Durchströmquerschnitt zur Einspritzöffnung 13 verschlossen ist. Zugleich ist der Ringbund 25 am Ventilglied 7 in den Bohrungsabsatz 27 eingetaucht und trennt so den untenliegenden Druckraum 31 vom Ringspalt 29, der andererseits in den obenliegenden Druckraum 21 mündet. Der im Kraftstoffhochdruckzulaufkanal 23, im obenliegenden Druckraum 21 und im Ringspalt 29 anstehende Standdruck des Kraftstoffes wird über die Drosselbohrung 41 auch im untenliegenden Druckraum 31 aufgebaut.A valve spring 45 holds when the injection valve is closed the valve member 15 via a valve plate 43 with its Valve sealing surface 9 in contact with the valve seat surface 11, see above that a flow cross-section to the injection opening 13 is closed. At the same time, the collar 25 is Valve member 7 immersed in the bore paragraph 27 and separates the pressure chamber 31 below from the annular gap 29, which on the other hand opens into the overhead pressure chamber 21. The one in the high-pressure fuel supply channel 23, in the overhead Pressure chamber 21 and standing pressure of the pending in the annular gap 29 Fuel is also in the throttle bore 41 pressure chamber 31 built up.

Die Kraftstoffhochdruckeinspritzung am Einspritzventil wird durch das Zuführen von unter hohem Druck stehenden Kraftstoff von der Einspritzpumpe über den Kraftstoffhochdruckzulaufkanal 23 in den obenliegenden Druckraum 21 eingeleitet. Dabei verschiebt nunmehr der an der Druckschulter 17 in Öffnungsrichtung angreifende Kraftstoffhochdruck das Ventilglied 7 entgegen der Schließkraft der Ventilfeder 45 in Öffnungshubrichtung. In Folge dessen hebt die Ventildichtfläche 9 vom Ventilsitz 11 ab und gibt den Durchströmquerschnitt zur Einspritzöffnung 13 frei, so daß der im untenliegenden Druckraum 31 anstehende Kraftstoff über die Einspritzöffnung 13 in den Brennraum der Brennkraftmaschine eingespritzt wird. Dabei bricht der Kraftstoffdruck im untenliegenden Druckraum 31 sehr rasch zusammen, da der Einspritzquerschnitt an der Einspritzöffnung 13 größer ausgebildet ist als der kleinste Durchmesser der Drosselbohrung 41. In dieser ersten Öffnungshubphase des Ventilgliedes 7 strömt somit mehr Kraftstoff durch die Einspritzöffnung 13 aus dem untenliegenden Druckraum 31 ab als durch die Drosselbohrung 41 in diesen nachfließen kann. Auf diese Weise stellt sich nunmehr am Ringbund 25 ein Druckgefälle ein, durch das der im Ringspalt 29 anstehende Kraftstoffhochdruck eine zusätzliche Schließkraft auf den Querschnittsübergang zum Ringbund 25 aufbringt. Infolge dieses zusätzlichen Schließdruckes wird die Öffnungshubbewegung des Ventilgliedes abgebremst bis der sich weiter im Druckraum 21 aufbauende Kraftstoffhochdruck ausreichend ist, diese zusätzliche Schließkraft zu überwinden und das Ventilglied 7 bis an seinen Öffnungshubanschlag weiter nach oben zu verschieben. Während dieses weiteren Öffnungshubweges des Ventilgliedes 7 taucht nun der Ringbund 25 aus der Überdeckung mit dem Bohrungsabsatz 27 aus und gibt so einen ungedrosselten Überströmquerschnitt zwischen dem Ringspalt 29 und dem untenliegenden Druckraum 31 frei, so daß die Kraftstoffhochdruckeinspritzung an der Einspritzöffnung 13 des Kraftstoffeinspritzventils fortgesetzt wird. Dabei ist der Zeitpunkt des Aufsteuerns dieses Verbindungsquerschnittes durch das Überfahren der Steuerkante 33 am Ringbund 25 über die Bohrungsabsatzkante 35 festgelegt. Über die Auslegung des Ringbundes 25 und insbesondere den axialen Abstand h zwischen der Steuerkante 33 und der Bohrungsabsatzkante 35 läßt sich nunmehr der Öffnungszeitpunkt des ungedrosselten Überströmens zwischen dem Ringspalt 29 und dem untenliegenden Druckraum 31 und somit der ersten Öffnungshubphase in einfacher Weise einstellen. Desweiteren läßt sich über den Drosselquerschnitt der Drosselbohrung 41 die Einspritzverlaufsformung auch graduell einstellen.The high-pressure fuel injection at the injection valve is by supplying high pressure Fuel from the injection pump via the High-pressure fuel inlet channel 23 in the overhead Pressure chamber 21 initiated. The now moves on the pressure shoulder 17 engaging in the opening direction High fuel pressure, the valve member 7 against Closing force of the valve spring 45 in the opening stroke direction. In As a result, the valve sealing surface 9 lifts from the valve seat 11 and gives the flow cross-section to the injection opening 13 free, so that the pressure chamber 31 pending fuel via the injection opening 13 in the Combustion chamber of the internal combustion engine is injected. there breaks the fuel pressure in the pressure chamber 31 below together very quickly since the injection cross section at the Injection opening 13 is formed larger than the smallest Diameter of the throttle bore 41. In this first Opening stroke phase of the valve member 7 thus flows more Fuel through the injection opening 13 from the pressure chamber 31 below than through the throttle bore 41 can flow into this. This way it turns out now on the collar 25 a pressure drop through which the High fuel pressure present in the annular gap 29 additional closing force on the cross-section transition to Ring collar 25 applies. As a result of this additional Closing pressure is the opening stroke movement of the Valve member braked until it continues in pressure chamber 21 building up high fuel pressure is sufficient to overcome additional closing force and the valve member 7 up to its opening stroke stop move. During this further opening stroke of the Valve member 7 now emerges from the collar 25 Overlap with the bore paragraph 27 and there is one unrestricted overflow cross-section between the annular gap 29 and the underlying pressure chamber 31 free, so that the High-pressure fuel injection at the injection opening 13 of the fuel injector is continued. It is the time of heading up this Connection cross-section by driving over the Control edge 33 on the collar 25 over the edge of the bore shoulder 35 set. About the design of the collar 25 and in particular the axial distance h between the control edge 33 and the bore shoulder edge 35 can now be the Opening time of the unthrottled overflow between the annular gap 29 and the pressure chamber 31 and thus the first opening stroke phase in a simple manner to adjust. Furthermore, can be Throttle cross section of the throttle bore 41 die Gradually adjust the injection course shaping.

Mit Austauchen des Ringbundes 25 aus der Überdeckung mit dem Bohrungsabsatz 27 erfolgt nunmehr das vollständige Aufsteuern des Kraftstoffeinspritzventils in gewohnter Weise bis zur Anlage des Ventilgliedes 7 an einem Öffnungshubanschlag.When the collar 25 emerges from the overlap with the Hole paragraph 27 is now complete Open the fuel injector in the usual way until the valve member 7 abuts on one Öffnungshubanschlag.

Das Schließen des Kraftstoffeinspritzventils erfolgt in bekannter Weise durch die Unterbrechung der Kraftstoffhochdruckzufuhr in den oberen Druckraum 21, in dessen Folge der am Einspritzventil anstehende Druck wieder unter den notwendigen Öffnungsdruck sinkt, so daß die Ventilfeder 45 nunmehr das Ventilglied 7 in Anlage an die Ventilsitzfläche 11 zurückbewegt, wobei sich nunmehr über die Drosselbohrung 41 der eingangs beschriebene Druckaufbau erneut einstellt.The fuel injector closes in known way by interrupting the High-pressure fuel supply in the upper pressure chamber 21, in the consequence of which is the pressure present at the injection valve falls below the necessary opening pressure so that the Valve spring 45 now the valve member 7 in contact with the Valve seat 11 moves back, now over the throttle bore 41 of the pressure build-up described at the beginning again.

Dabei ist es mit dem erfindungsgemäßen Kraftstoffeinspritzventil nunmehr in konstruktiv einfacher Weise möglich, einen zweistufigen Öffnungshubverlauf des Ventilgliedes 7 einstellen zu können, ohne dabei auf eine zweite zusätzliche Ventilschließfeder zurückgreifen zu müssen.It is with the invention Fuel injector now in a simpler design Way possible, a two-stage opening stroke of the To be able to adjust valve member 7 without doing so access second additional valve closing spring have to.

Claims (8)

  1. Fuel injection valve for internal combustion engines having a valve element (7) which can be displaced axially in a guide hole (5) of a valve body (1) and has a valve sealing face (9) at its combustion-chamber end, using which valve sealing face (11) it interacts with a stationary valve seat face (11), and having at least one injection opening (13), adjoining the sealing cross section between the valve seat face (11) and valve sealing face (9) in the downstream direction, into the combustion chamber of the internal combustion engine to be supplied, the valve element (7) having two guide regions with which it is guided in the guide hole (5) in a slidably displaceable manner, of which a first upper guide region (15) is provided at the end of the guide element (7) remote from the combustion chamber and a second lower guide region (25) is provided in a region of the valve element (7) facing the combustion chamber, the lower guide region (25), when the fuel injection valve is closed, separating an annular gap (29), which is formed between the valve-element shank (19) and the wall of the guide hole (5) and is connected to a fuel high-pressure feed duct (23), from a lower pressure space (31) which opens into the valve seat surface (11) and opening the said connection during the opening stroke movement of the valve element (7), and having a restrictor connection cross section between the annular gap (29) and the lower pressure space (31), the restrictor cross section being configured as a restrictor hole (41) which is arranged in the lower guide region (25), characterized in that the upper guide region (15) and the lower guide region (25) are designed in such a way that the result, owing to the fuel pressure in the annular gap (29), is a resultant force on the valve element (7) which is directed away from the valve seat (11).
  2. Fuel injection valve according to Claim 1, characterized in that the restrictor hole (41) is configured as an oblique hole in the valve element (7), whose inlet opening opens into the annular gap (29) above the second guide region (25) and whose outlet opening opens into the lower pressure space (31) below the second guide region (25).
  3. Fuel injection valve according to Claim 1, characterized in that the restrictor hole (41) is configured as a stepped hole having preferably two different diameters.
  4. Fuel injection valve according to Claim 1, characterized in that the lower second guide region (25) is configured on the valve element (7) as an annular collar (25).
  5. Fuel injection valve according to Claim 4, characterized in that an annular groove (37) is provided at the transition between the annular collar (25) and the valve-element-shank part projecting into the lower pressure space (31).
  6. Fuel injection valve according to Claim 4, characterized in that the lower edge facing the combustion chamber of the annular collar (25) forms a control edge (33) which interacts with an extension (27) of the hole formed at a diameter reduction of the guide hole (5).
  7. Fuel injection valve according to Claim 1, characterized in that a reduction in cross section is provided on the valve-element shank in the region of the lower pressure space (31).
  8. Fuel injection valve according to Claim 1, characterized in that a recess, preferably a ground surface portion (39), is provided on the valve-element shank in the region of the lower pressure space (31).
EP99957931A 1998-12-11 1999-10-21 Fuel injection valve for internal combustion engines Expired - Lifetime EP1055062B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19857244A DE19857244A1 (en) 1998-12-11 1998-12-11 Fuel injection valve for internal combustion engines
DE19857244 1998-12-11
PCT/DE1999/003371 WO2000036294A1 (en) 1998-12-11 1999-10-21 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1055062A1 EP1055062A1 (en) 2000-11-29
EP1055062B1 true EP1055062B1 (en) 2004-09-29

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Application Number Title Priority Date Filing Date
EP99957931A Expired - Lifetime EP1055062B1 (en) 1998-12-11 1999-10-21 Fuel injection valve for internal combustion engines

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US (1) US6422208B1 (en)
EP (1) EP1055062B1 (en)
JP (1) JP2002532652A (en)
KR (1) KR20010040841A (en)
DE (2) DE19857244A1 (en)
ES (1) ES2229794T3 (en)
WO (1) WO2000036294A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10062959A1 (en) * 2000-12-16 2002-06-20 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
US7100577B2 (en) * 2004-06-14 2006-09-05 Westport Research Inc. Common rail directly actuated fuel injection valve with a pressurized hydraulic transmission device and a method of operating same
DE102004060552A1 (en) * 2004-12-16 2006-06-22 Robert Bosch Gmbh Fuel injection valve for an internal combustion engine
DE102005015735A1 (en) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Fuel injector
US7415969B2 (en) * 2006-02-28 2008-08-26 Caterpillar Inc. Fuel injector having recessed check top
EP2083165A1 (en) * 2008-01-22 2009-07-29 Delphi Technologies, Inc. Injection nozzle
EP2568157A1 (en) * 2011-09-08 2013-03-13 Delphi Technologies Holding S.à.r.l. Injection Nozzle
DE102017202310A1 (en) * 2017-02-14 2018-08-16 Robert Bosch Gmbh Throttle element and low-pressure circuit of a fuel injection system with a throttle element

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4417694A (en) * 1980-10-22 1983-11-29 The Bendix Corporation Injector valve with contoured valve seat and needle valve interface
US4987887A (en) 1990-03-28 1991-01-29 Stanadyne Automotive Corp. Fuel injector method and apparatus
US5299919A (en) * 1991-11-01 1994-04-05 Paul Marius A Fuel injector system
US5647536A (en) * 1995-01-23 1997-07-15 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
DE19529375A1 (en) * 1995-08-10 1997-02-13 Bosch Gmbh Robert Fuel injector
USRE37633E1 (en) * 1995-08-29 2002-04-09 Isuzu Motors Limited Accumulating fuel injection apparatus
DE19821768C2 (en) * 1998-05-14 2000-09-07 Siemens Ag Dosing device and dosing method

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DE59910654D1 (en) 2004-11-04
DE19857244A1 (en) 2000-06-15
WO2000036294A1 (en) 2000-06-22
EP1055062A1 (en) 2000-11-29
US6422208B1 (en) 2002-07-23
KR20010040841A (en) 2001-05-15
ES2229794T3 (en) 2005-04-16
JP2002532652A (en) 2002-10-02

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