EP1446571B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1446571B1
EP1446571B1 EP02767066A EP02767066A EP1446571B1 EP 1446571 B1 EP1446571 B1 EP 1446571B1 EP 02767066 A EP02767066 A EP 02767066A EP 02767066 A EP02767066 A EP 02767066A EP 1446571 B1 EP1446571 B1 EP 1446571B1
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EP
European Patent Office
Prior art keywords
valve needle
valve
external
internal
sealing edge
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
EP02767066A
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German (de)
French (fr)
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EP1446571A1 (en
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1446571A1 publication Critical patent/EP1446571A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention is based on a fuel injection valve for Internal combustion engine, as it is the type of claim 1 corresponds.
  • a fuel injection valve is for example from the published patent application DE 30 36 583 A1 known. That known from the prior art Fuel injection valve has a valve body with a formed therein bore. In the hole is an outer one Valve needle out and turn in the outer valve needle an inner valve needle. Both valve needles work with a valve seat together, the bore on the combustion chamber side End closes. In the valve seat are an outer and formed an inner injection opening row, wherein the Inner injection port row from the inner valve needle and the outer injection port row from the outer valve needle -controlled.
  • a longitudinal movement of the valve pins in the bore against a closing force either turned on only the outer injection opening row or both injection port rows simultaneously, so that Fuel can flow to the injection ports, from where he is injected into the combustion chamber of the internal combustion engine.
  • Both the outer valve needle and the inner valve needle have on their valve sealing surfaces, with which they on Abut valve seat, each having a sealing edge, the one Sealing of the pressure chamber against the respective injection opening row ensures.
  • this results in the Disadvantage that the injection valve during the closed Phase in which no fuel through the injection openings should escape, the two Einspritzötechnischsschn not sufficiently sealed against each other.
  • This can on the one hand Combustion gases from the combustion chamber as so-called back-blowing in the space between the two valve pins is present, penetrate.
  • fuel the is also located between the valve pins during operation, as leakage into the combustion chamber flow and there to one Increase in hydrocarbon emissions.
  • the fuel injection valve according to the invention with the characterizing Features of claim 1 has in contrast the advantage that no leakage and thus no leakage of Fuel between the injections is possible and that from the combustion chamber of the internal combustion engine no combustion gases through the injection openings in the fuel injection valve can penetrate.
  • the outer valve needle an inwardly cantilevered sealing lip, the one having inner sealing edge. This inner sealing edge comes in Closed position of the outer valve needle on the valve seat for Plant and seals so the outer injection hole row against the inner injection port row.
  • annular space formed with fuel can be filled under high pressure.
  • the fuel in the annulus acts on the formed on the inner valve needle Pressure surface, so that a directed away from the valve seat force is exerted on the inner valve needle.
  • the inner valve needle can hydraulically in a simple manner be controlled, with the annulus with little effort can be realized.
  • the outer Valve needle formed substantially hollow cylindrical, and the pressure chamber is through a groove in the inner circumferential surface formed the outer valve needle.
  • the Sealing lip on a seat facing away from the valve, on the the inner valve needle with a sealing surface in the closed position comes to the plant. This will cause the inner sealing edge, which is formed on the sealing lip, by the closing force the inner valve needle additionally against the valve seat pressed, so that the sealing effect of the inner sealing edge is significantly improved.
  • the outer Valve needle next to the inner sealing edge an additional outer sealing edge, which upstream to the inner Sealing edge and also upstream to the outer injection port row is arranged.
  • the seal inner and outer sealing edge the outer injection port row completely, so no fuel through the outer injection opening row uncontrolled into the combustion chamber can get. There can be no other way around Combustion gases from the combustion chamber into the fuel injection valve penetration.
  • the sealing lip designed so that during the closing movement of the outer Valve needle first the inner sealing edge on the valve seat to Plant comes and only with the further closing movement under elastic deformation of the sealing lip and the outer sealing edge. Due to the elastic deformation of the sealing lip is the contact pressure on the inner sealing edge increases, so that in the case where only the inner valve needle from the valve seat lifts and thereby the inner injection port row releases, still a secure seal on the inner Sealing edge of the outer valve needle is given.
  • a fuel injection valve in longitudinal section shown in Figure 1, a fuel injection valve in longitudinal section shown.
  • a valve body 1 a bore 3 is formed, wherein the bore 3 is closed by a valve seat 10 is, which is formed substantially conical.
  • this valve seat 10 is on the combustion chamber side End of the bore 3 is arranged.
  • an outer Valve needle 5 is arranged, which is longitudinally displaceable there is and in a brennraumabgewandten section of the bore 3 is guided.
  • the outer valve needle 5 is a piston-shaped inner valve needle 7 guided longitudinally displaceable, the a longitudinal axis 2, which with the longitudinal axis of outer valve needle 5 coincides.
  • the outer valve needle 5 has at its the valve seat 10 end facing a in essential conical valve sealing surface 6, which in Closed position of the outer valve needle 5 on the valve seat 10th comes to the plant.
  • the inner valve needle 7 also has one essentially conical sealing surface 8, which in the closed position also comes to the valve seat 10 to the plant.
  • a Pressure shoulder 11 formed between the outer valve needle 5 and the wall of the bore 3, a pressure chamber 16 is formed, the via a formed in the valve body 1 inlet channel 18 can be filled with fuel under high pressure.
  • the pressure chamber 16 is radial extended, so that the inlet channel 18 in the valve body.
  • valve 1 can train without the leadership of the outer valve needle. 5 in the hole 3 by a too small wall thickness between to weaken the bore 3 and the inlet channel 18.
  • a longitudinal movement of Valve needles 5, 7 in the bore 3 takes place thereby, that either the opening force on the outer valve needle 5, by the hydraulic force on the pressure shoulder 11th is generated by the increasing pressure in the pressure chamber 16th exceeds the closing force or that at least one approximately constant fuel pressure in the pressure chamber 16 reduces the closing force on the outer valve needle 5 becomes.
  • FIG. 2 shows an enlargement of the designated II section of Figure 1.
  • the valve seat 10 In the valve seat 10 are a plurality of injection openings formed, the valve seat 10 with the Combust combustion chamber of the internal combustion engine.
  • the injection openings are arranged in two rows of injection openings 12, 14, wherein the inner injection opening row 12 closer the longitudinal axis 2 is located as the outer injection opening row 14.
  • the inner valve needle 7 has at its combustion chamber facing End a sequence of a cone surface 107, one adjoining first cylindrical surface 117, one following second cone surface 207, a subsequent second cylindrical surface 217 and an adjacent thereto third cone surface 307 on.
  • the opening angle of the third Cone surface 307 is larger than the opening angle of the conical Valve seat 10, so that at the transition of the second cylindrical surface 217 to the third cone surface 307 a sealing edge 27 is formed, in the closed position of the inner valve needle 7 comes to the valve seat 10 to the plant.
  • the sealing edge 27 comes here upstream of the inner row of injection openings 12 at the valve seat 10 to the plant, so that the sealing edge 27 can close the inner injection opening 12 series.
  • the outer valve needle 5 has near its combustion chamber side End a groove 19 on, so that between the inner Valve needle 7 and the outer valve needle 5, an annular space 20th is formed.
  • the annulus 20 is over several over the circumference the outer valve needle 5 distributed connecting bores 22 connected to the pressure chamber 16, and thus prevails in the annular space 20 always the same fuel pressure as in the pressure chamber 16.
  • the combustion chamber-side end surface of the outer Valve needle 5 is approximately conical and has an outer ring formed by an annular bead formed thereon Sealing edge 32, which when attached to the valve seat 10 the Pressure chamber 16 against the outer injection opening row 14 closes.
  • the inner one Sealing edge 30 and the outer sealing edge 32 are here arranged so that the outer sealing edge 32 upstream and the inner sealing edge 30 downstream of the outer injection opening row 14 are arranged so that at the plant the two sealing edges 30, 32 on the valve seat 10, the outer Injection opening row 14 is sealingly closed.
  • the sealing lip 25 is elastically deformable and designed to that in the closing movement of the lifted off the valve seat 10th outer valve needle 5 first, the inner sealing edge 30 comes to the valve seat 10 to the plant and only then by an elastic deformation of the sealing lip 25 and the outer Sealing edge 32.
  • the valve seat 10 remote from the side of the sealing lip 25 is formed as a seat 26, which, when the inner Ventilnader7 is in the closed position, at the as Sealing surface serving second cone surface 207 is applied. hereby results in an additional closing force on the Sealing lip 25 and thus on the inner sealing edge 30, what the sealing effect of the inner sealing edge 30 reinforced.
  • FIG 3 is an enlargement in the region of the valve seat 10 of Figure 2 shown.
  • the reinforcement of the sealing effect on the inner sealing edge 30 of the sealing lip 25 is only then indicated when the sealing lip 25 sufficiently far inward protrudes, leaving them in the closed position of the inner valve needle 7 abuts against the second cone surface 207. Is this Reinforcement of the sealing effect on the inner sealing edge 30 not desired, it may also be provided, the sealing lip 25 to shorten accordingly, so that no more investment takes place on the inner valve needle 7.
  • the extension of the Sealing lip 25 by the distance h thus allows the contact force and thus to adjust the sealing effect on the inner sealing edge 30.
  • the operation of the fuel injection valve is like follows: Should an injection only through part of the injection openings take place, in this construction example through the inner row of injection ports 12, so does fuel introduced under high pressure in the pressure chamber 16.
  • By reducing the closing force on the inner valve needle 7 results from the hydraulic force on the first cone surface 107, which is formed as a pressure surface, an opening force on the inner valve needle 7 from the valve seat 10 away, so that the sealing edge 27 lifts off the valve seat 10 and the annulus 20 with the inner injection port row 12 connects.
  • By a correspondingly high closing force on the outer valve needle 5 remain both the inner Sealing edge 30 and the outer sealing edge 32 in abutment on Valve seat 10 and hold so the outer row of injection openings 14 closed.
  • the inner valve needle 7 sets its opening movement Continue until you get to one in the drawing shown stop comes to the plant. Shall go through the whole Injection cross section are injected, so will also reduces the closing force on the outer valve needle 5, and the outer valve needle 5 lifts first with the outer one Sealing edge 32 and then with the inner sealing edge 30 from the valve seat 10, so now fuel through both Injection opening rows 12, 14 is injected.
  • the Closing of the fuel injection valve takes place in analogue Way by increasing the closing force on the inner Valve needle 7 and the outer valve needle 5, wherein it may be provided, at the same time the pressure in the pressure chamber 16th to reduce.

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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)

Abstract

The invention relates to a fuel injection valve comprising a valve body (1) inside of which an outer valve needle (5) and an inner needle (7), which is guided inside the outer valve needle (5), are situated inside a boring (3). The valve needles (5; 7) interact with a valve seat (10), which is provided at the combustion chamber-side end of the boring (3) and in which an outer row of injection orifices (14) and in inner row of injection orifices (12) are arranged. The inner valve needle (7) controls the opening of the inner row of injection orifices (12), and the outer valve needle (5) controls the opening of the outer row of injection orifices (14). The outer valve needle (5) comprises an inward projecting, encircling sealing lip (25) having an inner sealing edge (30), whereby the inner sealing edge (30) rests against the valve seat (10) when the outer valve needle (7) is in a closed position.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es der Gattung des Patentanspruchs 1 entspricht. Ein derartiges Kraftstoffeinspritzventil ist beispielsweise aus der Offenlegungsschrift DE 30 36 583 A1 bekannt. Das aus dem Stand der Technik bekannte Kraftstoffeinspritzventil weist einen Ventilkörper mit einer darin ausgebildeten Bohrung auf. In der Bohrung ist eine äußere Ventilnadel geführt und in der äußeren Ventilnadel wiederum eine innere Ventilnadel. Beide Ventilnadeln wirken mit einem Ventilsitz zusammen, der die Bohrung am brennraumseitigen Ende abschließt. Im Ventilsitz sind eine äußere und eine innere Einspritzöffnungsreihe ausgebildet, wobei die innere Einspritzöffnungsreihe von der inneren Ventilnadel und die äußere Einspritzöffnungsreihe von der äußeren Ventilnadel gesteuert-wird. Durch eine Längsbewegung der Ventilnadeln in der Bohrung entgegen einer Schließkraft wird entweder nur die äußere Einspritzöffnungsreihe aufgesteuert oder beide Einspritzöffnungsreihen gleichzeitig, so dass Kraftstoff zu den Einspritzöffnungen fließen kann, von wo er in den Brennraum der Brennkraftmaschine eingespritzt wird.The invention is based on a fuel injection valve for Internal combustion engine, as it is the type of claim 1 corresponds. Such a fuel injection valve is for example from the published patent application DE 30 36 583 A1 known. That known from the prior art Fuel injection valve has a valve body with a formed therein bore. In the hole is an outer one Valve needle out and turn in the outer valve needle an inner valve needle. Both valve needles work with a valve seat together, the bore on the combustion chamber side End closes. In the valve seat are an outer and formed an inner injection opening row, wherein the Inner injection port row from the inner valve needle and the outer injection port row from the outer valve needle -controlled. By a longitudinal movement of the valve pins in the bore against a closing force either turned on only the outer injection opening row or both injection port rows simultaneously, so that Fuel can flow to the injection ports, from where he is injected into the combustion chamber of the internal combustion engine.

Sowohl die äußere Ventilnadel als auch die innere Ventilnadel weisen an ihren Ventildichtflächen, mit denen sie am Ventilsitz anliegen, jeweils eine Dichtkante auf, die eine Abdichtung des Druckraums gegen die jeweilige Einspritzöffnungsreihe sicherstellt. Hierbei ergibt sich jedoch der Nachteil, dass das Einspritzventil während der geschlossenen Phase, in der kein Kraftstoff durch die Einspritzöffnungen austreten soll, die beiden Einspritzöffnungsreihen nicht ausreichend gegeneinander abdichtet. Dadurch können zum einen Verbrennungsgase aus dem Brennraum als sogenanntes Rückblasen in den Raum, der zwischen den beiden Ventilnadeln vorhanden ist, eindringen. Zum anderen kann Kraftstoff, der sich durch den Betrieb auch zwischen den Ventilnadeln befindet, als Leckage in den Brennraum fließen und dort zu einer Erhöhung der Kohlenwasserstoff-Emissionen führen.Both the outer valve needle and the inner valve needle have on their valve sealing surfaces, with which they on Abut valve seat, each having a sealing edge, the one Sealing of the pressure chamber against the respective injection opening row ensures. However, this results in the Disadvantage that the injection valve during the closed Phase in which no fuel through the injection openings should escape, the two Einspritzöffnungsreihen not sufficiently sealed against each other. This can on the one hand Combustion gases from the combustion chamber as so-called back-blowing in the space between the two valve pins is present, penetrate. On the other hand, fuel, the is also located between the valve pins during operation, as leakage into the combustion chamber flow and there to one Increase in hydrocarbon emissions.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, dass keine Leckage und damit kein Austritt von Kraftstoff zwischen den Einspritzungen möglich ist und dass aus dem Brennraum der Brennkraftmaschine keine Verbrennungsgase durch die Einspritzöffnungen in das Kraftstoffeinspritzventil eindringen können. Hierzu weist die äußere Ventilnadel eine nach innen kragende Dichtlippe auf, die eine innere Dichtkante aufweist. Diese innere Dichtkante kommt in Schließstellung der äußeren Ventilnadel am Ventilsitz zur Anlage und dichtet so die äußere Einspritzöffnungsreihe gegen die innere Einspritzöffnungsreihe ab. Durch die an der Dichtlippe ausgebildete innere Dichtkante kann zwischen den Einspritzungen kein Kraftstoff aus dem Ringraum durch die Einspritzöffnungen und damit unkontrolliert in den Brennraum gelangen.The fuel injection valve according to the invention with the characterizing Features of claim 1 has in contrast the advantage that no leakage and thus no leakage of Fuel between the injections is possible and that from the combustion chamber of the internal combustion engine no combustion gases through the injection openings in the fuel injection valve can penetrate. For this purpose, the outer valve needle an inwardly cantilevered sealing lip, the one having inner sealing edge. This inner sealing edge comes in Closed position of the outer valve needle on the valve seat for Plant and seals so the outer injection hole row against the inner injection port row. By the at the Sealing lip formed inner sealing edge can between the Injections no fuel from the annulus through the Injection openings and thus uncontrolled in the combustion chamber reach.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist zwischen der äußeren Ventilnadel und der inneren Ventilnadel ein Ringraum ausgebildet, der mit Kraftstoff unter hohem Druck befüllbar ist. Der Kraftstoff im Ringraum beaufschlagt die an der inneren Ventilnadel ausgebildete Druckfläche, so dass eine vom Ventilsitz weggerichtete Kraft auf die innere Ventilnadel ausgeübt wird. Auf diese Weise kann die innere Ventilnadel in einfacher Weise hydraulisch gesteuert werden, wobei sich der Ringraum mit nur wenig Aufwand realisieren lässt.In an advantageous embodiment of the subject of the Invention is between the outer valve needle and the inner Valve needle an annular space formed with fuel can be filled under high pressure. The fuel in the annulus acts on the formed on the inner valve needle Pressure surface, so that a directed away from the valve seat force is exerted on the inner valve needle. In this way the inner valve needle can hydraulically in a simple manner be controlled, with the annulus with little effort can be realized.

In einer weiteren vorteilhaften Ausgestaltung ist die äußere Ventilnadel im wesentlichen hohlzylinderförmig ausgebildet, und der Druckraum ist durch eine Auskehlung in der Innenmantelfläche der äußeren Ventilnadel gebildet. Diese Ausbildung des Ringraums ist einfach zu fertigen und erlaubt eine beliebige Gestaltung des Ringraums was Volumen und Lage anbelangt. Darüber hinaus kann es in vorteilhafter Weise vorgesehen sein, den Ringraum über wenigstens eine in der äußeren Ventilnadel ausgebildete Bohrung mit einem Druckraum zu verbinden, um so den Ringraum mit Kraftstoff unter hohem Druck zu befüllen.In a further advantageous embodiment, the outer Valve needle formed substantially hollow cylindrical, and the pressure chamber is through a groove in the inner circumferential surface formed the outer valve needle. This training The annulus is easy to manufacture and allows any Design of the annulus in terms of volume and location. In addition, it can be provided in an advantageous manner be, the annulus over at least one in the outer Valve needle trained bore to connect with a pressure chamber around the annulus with fuel under high pressure to fill.

In einer weiteren vorteilhaften Ausgestaltung weist die Dichtlippe eine vom Ventil abgewandte Sitzfläche auf, an der die innere Ventilnadel mit einer Dichtfläche in Schließstellung zur Anlage kommt. Hierdurch wird die innere Dichtkante, die an der Dichtlippe ausgebildet ist, durch die Schließkraft der inneren Ventilnadel zusätzlich gegen den Ventilsitz gepresst, so dass die Dichtwirkung der inneren Dichtkante deutlich verbessert wird.In a further advantageous embodiment, the Sealing lip on a seat facing away from the valve, on the the inner valve needle with a sealing surface in the closed position comes to the plant. This will cause the inner sealing edge, which is formed on the sealing lip, by the closing force the inner valve needle additionally against the valve seat pressed, so that the sealing effect of the inner sealing edge is significantly improved.

In einer weiteren vorteilhaften Ausgestaltung weist die äußere Ventilnadel neben der inneren Dichtkante eine zusätzliche äußere Dichtkante auf, welche stromaufwärts zur inneren Dichtkante und auch stromaufwärts zur äußeren Einspritzöffnungsreihe angeordnet ist. Auf diese Weise verschließen die innere und die äußere Dichtkante die äußere Einspritzöffnungsreihe vollständig, so dass kein Kraftstoff durch die äußere Einspritzöffnungsreihe unkontrolliert in den Brennraum gelangen kann. Es können auch auf umgekehrtem Weg keine Verbrennungsgase aus dem Brennraum in das Kraftstoffeinspritzventil eindringen.In a further advantageous embodiment, the outer Valve needle next to the inner sealing edge an additional outer sealing edge, which upstream to the inner Sealing edge and also upstream to the outer injection port row is arranged. In this way, the seal inner and outer sealing edge the outer injection port row completely, so no fuel through the outer injection opening row uncontrolled into the combustion chamber can get. There can be no other way around Combustion gases from the combustion chamber into the fuel injection valve penetration.

In einer weiteren vorteilhaften Ausgestaltung ist die Dichtlippe so gestaltet, dass bei der Schließbewegung der äußeren Ventilnadel zuerst die innere Dichtkante am Ventilsitz zur Anlage kommt und erst mit der weiteren Schließbewegung unter elastischer Verformung der Dichtlippe auch die äußere Dichtkante. Durch die elastische Verformung der Dichtlippe wird die Anpresskraft an der inneren Dichtkante erhöht, so dass in dem Fall, in dem nur die innere Ventilnadel vom Ventilsitz abhebt und dadurch die innere Einspritzöffnungsreihe freigibt, nach wie vor eine sichere Abdichtung an der inneren Dichtkante der äußeren Ventilnadel gegeben ist.In a further advantageous embodiment, the sealing lip designed so that during the closing movement of the outer Valve needle first the inner sealing edge on the valve seat to Plant comes and only with the further closing movement under elastic deformation of the sealing lip and the outer sealing edge. Due to the elastic deformation of the sealing lip is the contact pressure on the inner sealing edge increases, so that in the case where only the inner valve needle from the valve seat lifts and thereby the inner injection port row releases, still a secure seal on the inner Sealing edge of the outer valve needle is given.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject The invention are the drawing, the description and the claims.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt:

  • Figur 1 zeigt im Längsschnitt ein Kraftstoffeinspritzventil im wesentlichen Bereich,
  • Figur 2 eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1 und
  • Figur 3 eine Vergrößerung von Figur 2 im Bereich des Ventilsitzes.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown:
  • FIG. 1 shows a longitudinal section through a fuel injection valve in the essential area,
  • Figure 2 shows an enlargement of the designated II section of Figure 1 and
  • 3 shows an enlargement of Figure 2 in the region of the valve seat.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Kraftstoffeinspritzventil im Längsschnitt dargestellt. In einem Ventilkörper 1 ist eine Bohrung 3 ausgebildet, wobei die Bohrung 3 durch einen Ventilsitz 10 verschlossen wird, der im wesentlichen konisch ausgebildet ist. In Einbaulage des Kraftstoffeinspritzventils in der Brennkraftmaschine ist dieser Ventilsitz 10 am brennraumseitigen Ende der Bohrung 3 angeordnet. In der Bohrung 3 ist eine äußere Ventilnadel 5 angeordnet, die dort längsverschiebbar ist und in einem brennraumabgewandten Abschnitt der Bohrung 3 geführt ist. In der äußeren Ventilnadel 5 ist eine kolbenförmig innere Ventilnadel 7 längsverschiebbar geführt, die eine Längsachse 2 aufweist, welche mit der Längsachse der äußeren Ventilnadel 5 zusammenfällt. Die äußere Ventilnadel 5 weist an ihrem dem Ventilsitz 10 zugewandten Ende eine im wesentlichen konische Ventildichtfläche 6 auf, die in Schließstellung der äußeren Ventilnadel 5 am Ventilsitz 10 zur Anlage kommt. Die innere Ventilnadel 7 weist ebenso eine im wesentlichen konische Dichtfläche 8 auf, die in Schließstellung ebenfalls am Ventilsitz 10 zur Anlage kommt. Durch eine Verjüngung der äußeren Ventilnadel 5 ist brennraumzugewandt zum geführten Abschnitt der äußeren Venilnadel 5 eine Druckschulter 11 ausgebildet. Zwischen der äußeren Ventilnadel 5 und der Wand der Bohrung 3 ist ein Druckraum 16 ausgebildet, der über einen im Ventilkörper 1 ausgebildeten Zulaufkanal 18 mit Kraftstoff unter hohem Druck befüllbar ist. Auf Höhe der Druckschulter 11 ist der Druckraum 16 radial erweitert, so dass sich der Zulaufkanal 18 im Ventilkörper 1 ausbilden lässt, ohne die Führung der äußeren Ventilnadel 5 in der Bohrung 3 durch eine zu geringe Wandstärke zwischen der Bohrung 3 und dem Zulaufkanal 18 zu schwächen. Durch eine in der Zeichnung nicht dargestellte Vorrichtung kann eine Schließkraft auf die äußere Ventilnadel 5 und unabhängig davon auf die innere Ventilnadel 7 ausgeübt werden, wobei die jeweilige Schließkraft beide Ventilnadeln 5, 7 in Richtung des Ventilsitzes 10 beaufschlagt. Eine Längsbewegung der Ventilnadeln 5, 7 in der Bohrung 3 findet dadurch statt, dass entweder die öffnende Kraft auf die äußere Ventilnadel 5, die durch die hydraulische Kraft auf die Druckschulter 11 erzeugt wird, durch den ansteigenden Druck im Druckraum 16 die Schließkraft übersteigt oder dass bei einem zumindest näherungsweise gleichbleibenden Kraftstoffdruck im Druckraum 16 die Schließkraft auf die äußere Ventilnadel 5 vermindert wird. Nach dem gleichen Prinzip lässt sich auch die Längsbewegung der inneren Ventilnadel 7 steuern.In Figure 1, a fuel injection valve in longitudinal section shown. In a valve body 1, a bore 3 is formed, wherein the bore 3 is closed by a valve seat 10 is, which is formed substantially conical. In installation position of the fuel injection valve in the internal combustion engine this valve seat 10 is on the combustion chamber side End of the bore 3 is arranged. In the hole 3 is an outer Valve needle 5 is arranged, which is longitudinally displaceable there is and in a brennraumabgewandten section of the bore 3 is guided. In the outer valve needle 5 is a piston-shaped inner valve needle 7 guided longitudinally displaceable, the a longitudinal axis 2, which with the longitudinal axis of outer valve needle 5 coincides. The outer valve needle 5 has at its the valve seat 10 end facing a in essential conical valve sealing surface 6, which in Closed position of the outer valve needle 5 on the valve seat 10th comes to the plant. The inner valve needle 7 also has one essentially conical sealing surface 8, which in the closed position also comes to the valve seat 10 to the plant. By a taper of the outer valve needle 5 is facing the combustion chamber to the guided portion of the outer Venilnadel 5 a Pressure shoulder 11 formed. Between the outer valve needle 5 and the wall of the bore 3, a pressure chamber 16 is formed, the via a formed in the valve body 1 inlet channel 18 can be filled with fuel under high pressure. At the level of the pressure shoulder 11, the pressure chamber 16 is radial extended, so that the inlet channel 18 in the valve body. 1 can train without the leadership of the outer valve needle. 5 in the hole 3 by a too small wall thickness between to weaken the bore 3 and the inlet channel 18. By a in the drawing, not shown, a device Closing force on the outer valve needle 5 and independently be exerted on the inner valve needle 7, wherein the respective closing force both valve needles 5, 7 in the direction the valve seat 10 acted upon. A longitudinal movement of Valve needles 5, 7 in the bore 3 takes place thereby, that either the opening force on the outer valve needle 5, by the hydraulic force on the pressure shoulder 11th is generated by the increasing pressure in the pressure chamber 16th exceeds the closing force or that at least one approximately constant fuel pressure in the pressure chamber 16 reduces the closing force on the outer valve needle 5 becomes. The same principle is followed by longitudinal movement control the inner valve needle 7.

Figur 2 zeigt eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1. Im Ventilsitz 10 sind mehrere Einspritzöffnungen ausgebildet, die den Ventilsitz 10 mit dem Brennraum der Brennkraftmaschine verbinden. Die Einspritzöffnungen sind in zwei Einspritzöffnungsreihen 12;14 angeordnet, wobei die innere Einspritzöffnungsreihe 12 näher an der Längsachse 2 liegt als die äußere Einspritzöffnungsreihe 14. Die innere Ventilnadel 7 weist an ihrem brennraumzugewandten Ende eine Abfolge aus einer Konusfläche 107, einer sich daran anschließenden ersten Zylinderfläche 117, einer darauf folgenden zweiten Konusfläche 207, einer darauf folgenden zweiten Zylinderfläche 217 und einer daran grenzenden dritten Konusfläche 307 auf. Der Öffnungswinkel der dritten Konusfläche 307 ist größer als der Öffnungswinkel des konischen Ventilsitzes 10, so dass am Übergang der zweiten Zylinderfläche 217 zur dritten Konusfläche 307 eine Dichtkante 27 gebildet ist, die in Schließstellung der inneren Ventilnadel 7 am Ventilsitz 10 zur Anlage kommt. Die Dichtkante 27 kommt hierbei stromaufwärts der inneren Einspritzöffnungsreihe 12 am Ventilsitz 10 zur Anlage, so dass die Dichtkante 27 die innere Einspritzöffnungsreihe 12 verschließen kann.Figure 2 shows an enlargement of the designated II section of Figure 1. In the valve seat 10 are a plurality of injection openings formed, the valve seat 10 with the Combust combustion chamber of the internal combustion engine. The injection openings are arranged in two rows of injection openings 12, 14, wherein the inner injection opening row 12 closer the longitudinal axis 2 is located as the outer injection opening row 14. The inner valve needle 7 has at its combustion chamber facing End a sequence of a cone surface 107, one adjoining first cylindrical surface 117, one following second cone surface 207, a subsequent second cylindrical surface 217 and an adjacent thereto third cone surface 307 on. The opening angle of the third Cone surface 307 is larger than the opening angle of the conical Valve seat 10, so that at the transition of the second cylindrical surface 217 to the third cone surface 307 a sealing edge 27 is formed, in the closed position of the inner valve needle 7 comes to the valve seat 10 to the plant. The sealing edge 27 comes here upstream of the inner row of injection openings 12 at the valve seat 10 to the plant, so that the sealing edge 27 can close the inner injection opening 12 series.

Die äußere Ventilnadel 5 weist nahe ihres brennraumseitigen Endes eine Auskehlung 19 auf, so dass zwischen der inneren Ventilnadel 7 und der äußeren Ventilnadel 5 ein Ringraum 20 gebildet ist. Der Ringraum 20 ist über mehrere über den Umfang der äußeren Ventilnadel 5 verteilt angeordneten Verbindungsbohrungen 22 mit dem Druckraum 16 verbunden, und somit herrscht im Ringraum 20 stets der gleiche Kraftstoffdruck wie im Druckraum 16. Die brennraumseitige Endfläche der äußeren Ventilnadel 5 ist näherungsweise konisch ausgebildet und weist durch einen daran ausgebildeten Ringwulst eine äußere Dichtkante 32 auf, die bei Anlage am Ventilsitz 10 den Druckraum 16 gegen die äußere Einspritzöffnungsreihe 14 verschließt. Am brennraumseitigen Ende der äußeren Ventilnadel 5 ist eine nach innen kragende Dichtlippe 25 ausgebildet, an der durch einen ringfömigen Wulst eine innere Dichtkante 30 ausgebildet ist, die in Schließstellung der äußeren Ventilnadel 5 ebenfalls am Ventilsitz 10 zur Anlage kommt. Die innere Dichtkante 30 und die äußere Dichtkante 32 sind hierbei so angeordnet, dass die äußere Dichtkante 32 stromaufwärts und die innere Dichtkante 30 stromabwärts der äußeren Einspritzöffnungsreihe 14 angeordnet sind, so dass bei der Anlage der beiden Dichtkanten 30, 32 am Ventilsitz 10 die äußere Einspritzöffnungsreihe 14 dichtend verschlossen wird.The outer valve needle 5 has near its combustion chamber side End a groove 19 on, so that between the inner Valve needle 7 and the outer valve needle 5, an annular space 20th is formed. The annulus 20 is over several over the circumference the outer valve needle 5 distributed connecting bores 22 connected to the pressure chamber 16, and thus prevails in the annular space 20 always the same fuel pressure as in the pressure chamber 16. The combustion chamber-side end surface of the outer Valve needle 5 is approximately conical and has an outer ring formed by an annular bead formed thereon Sealing edge 32, which when attached to the valve seat 10 the Pressure chamber 16 against the outer injection opening row 14 closes. At the combustion chamber end of the outer valve needle 5 is formed an inwardly cantilevered sealing lip 25 at the by an annular bead an inner sealing edge 30th is formed, in the closed position of the outer valve needle 5 also comes to the valve seat 10 to the plant. The inner one Sealing edge 30 and the outer sealing edge 32 are here arranged so that the outer sealing edge 32 upstream and the inner sealing edge 30 downstream of the outer injection opening row 14 are arranged so that at the plant the two sealing edges 30, 32 on the valve seat 10, the outer Injection opening row 14 is sealingly closed.

Die Dichtlippe 25 ist elastisch verformbar und so ausgebildet, dass bei der Schließbewegung der vom Ventilsitz 10 abgehobenen äußeren Ventilnadel 5 zuerst die innere Dichtkante 30 am Ventilsitz 10 zur Anlage kommt und erst danach durch eine elastische Verformung der Dichtlippe 25 auch die äußere Dichtkante 32. Um die Dichtwirkung der inneren Dichtkante 30 zu verbessern ist es in diesem Ausführungsbeispiel vorgesehen, dass die dem Ventilsitz 10 abgewandte Seite der Dichtlippe 25 als Sitzfläche 26 ausgebildet ist, die, wenn die innere Ventilnader7 in Schließstellung ist, an der als Dichtfläche dienenden zweiten Konusfläche 207 anliegt. Hierdurch ergibt sich eine zusätzliche Schließkraft auf die Dichtlippe 25 und damit auf die innere Dichtkante 30, was die Dichtwirkung der inneren Dichtkante 30 verstärkt.The sealing lip 25 is elastically deformable and designed to that in the closing movement of the lifted off the valve seat 10th outer valve needle 5 first, the inner sealing edge 30 comes to the valve seat 10 to the plant and only then by an elastic deformation of the sealing lip 25 and the outer Sealing edge 32. To the sealing effect of the inner sealing edge 30th to improve it is provided in this embodiment that the valve seat 10 remote from the side of the sealing lip 25 is formed as a seat 26, which, when the inner Ventilnader7 is in the closed position, at the as Sealing surface serving second cone surface 207 is applied. hereby results in an additional closing force on the Sealing lip 25 and thus on the inner sealing edge 30, what the sealing effect of the inner sealing edge 30 reinforced.

In Figur 3 ist eine Vergrößerung im Bereich des Ventilsitzes 10 der Figur 2 dargestellt. Die Verstärkung der Dichtwirkung an der inneren Dichtkante 30 der Dichtlippe 25 ist nur dann angegeben, wenn die Dichtlippe 25 ausreichend weit nach innen ragt, so dass sie in Schließstellung der inneren Ventilnadel 7 an der zweiten Konusfläche 207 anliegt. Ist diese Verstärkung der Dichtwirkung an der inneren Dichtkante 30 nicht gewünscht, kann es auch vorgesehen sein, die Dichtlippe 25 entsprechend zu verkürzen, so dass keine Anlage mehr an der inneren Ventilnadel 7 erfolgt. Die Verlängerung der Dichtlippe 25 um die Strecke h erlaubt also die Anlagekraft und damit die Dichtwirkung an der inneren Dichtkante 30 einzustellen.In Figure 3 is an enlargement in the region of the valve seat 10 of Figure 2 shown. The reinforcement of the sealing effect on the inner sealing edge 30 of the sealing lip 25 is only then indicated when the sealing lip 25 sufficiently far inward protrudes, leaving them in the closed position of the inner valve needle 7 abuts against the second cone surface 207. Is this Reinforcement of the sealing effect on the inner sealing edge 30 not desired, it may also be provided, the sealing lip 25 to shorten accordingly, so that no more investment takes place on the inner valve needle 7. The extension of the Sealing lip 25 by the distance h thus allows the contact force and thus to adjust the sealing effect on the inner sealing edge 30.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Soll eine Einspritzung nur durch einen Teil der Einspritzöffnungen erfolgen, in diesem Konstruktionsbeispiel durch die innere Einspritzöffnungsreihe 12, so wird Kraftstoff unter hohem Druck in den Druckraum 16 eingeführt. Durch eine Verringerung der Schließkraft auf die innere Ventilnadel 7 ergibt sich über die hydraulische Kraft auf die erste Konusfläche 107, die als Druckfläche ausgebildet ist, eine Öffnungskraft auf die innere Ventilnadel 7 vom Ventilsitz 10 weg, so dass die Dichtkante 27 vom Ventilsitz 10 abhebt und den Ringraum 20 mit der inneren Einspritzöffnungsreihe 12 verbindet. Durch eine entsprechend hohe Schließkraft auf die äußere Ventilnadel 5 bleiben sowohl die innere Dichtkante 30 als auch die äußere Dichtkante 32 in Anlage am Ventilsitz 10 und halten so die äußere Einspritzöffnungsreihe 14 verschlossen. Die innere Ventilnadel 7 setzt ihre Öffnungsbewegung fort, bis sie an einem in der Zeichnung nicht dargestellten Anschlag zur Anlage kommt. Soll durch den gesamten Einspritzquerschnitt eingespritzt werden, so wird auch die Schließkraft auf die äußere Ventilnadel 5 reduziert, und die äußere Ventilnadel 5 hebt zuerst mit der äußeren Dichtkante 32 und dann auch mit der inneren Dichtkante 30 vom Ventilsitz 10 ab, so dass nun Kraftstoff durch beide Einspritzöffnungsreihen 12, 14 eingespritzt wird. Das Schließen des Kraftstoffeinspritzventils erfolgt in analoger Weise durch eine Erhöhung der Schließkraft auf die innere Ventilnadel 7 und auf die äußere Ventilnadel 5, wobei es vorgesehen sein kann, gleichzeitig den Druck im Druckraum 16 zu reduzieren. Hierdurch bewegen sich beide Ventilnadeln wieder auf den Ventilsitz 10 zu, bis sie mit der Dichtkante 27 bzw. mit der inneren Dichtkante 30 und der äußeren Dichtkante 32 am Ventilsitz 10 anliegen. Durch die Anlage der inneren Ventilnadel 7 mit der Konusfläche 207 an der Sitzfläche 26 wird die Dichtlippe 25 und damit auch die innere Dichtkante 30 am Ventilsitz 10 zusätzlich angepresst.The operation of the fuel injection valve is like follows: Should an injection only through part of the injection openings take place, in this construction example through the inner row of injection ports 12, so does fuel introduced under high pressure in the pressure chamber 16. By reducing the closing force on the inner valve needle 7 results from the hydraulic force on the first cone surface 107, which is formed as a pressure surface, an opening force on the inner valve needle 7 from the valve seat 10 away, so that the sealing edge 27 lifts off the valve seat 10 and the annulus 20 with the inner injection port row 12 connects. By a correspondingly high closing force on the outer valve needle 5 remain both the inner Sealing edge 30 and the outer sealing edge 32 in abutment on Valve seat 10 and hold so the outer row of injection openings 14 closed. The inner valve needle 7 sets its opening movement Continue until you get to one in the drawing shown stop comes to the plant. Shall go through the whole Injection cross section are injected, so will also reduces the closing force on the outer valve needle 5, and the outer valve needle 5 lifts first with the outer one Sealing edge 32 and then with the inner sealing edge 30 from the valve seat 10, so now fuel through both Injection opening rows 12, 14 is injected. The Closing of the fuel injection valve takes place in analogue Way by increasing the closing force on the inner Valve needle 7 and the outer valve needle 5, wherein it may be provided, at the same time the pressure in the pressure chamber 16th to reduce. This causes both valve pins to move back to the valve seat 10 until it reaches the sealing edge 27 or with the inner sealing edge 30 and the outer sealing edge 32 abut the valve seat 10. By the plant of the inner Valve needle 7 with the conical surface 207 on the seat 26, the sealing lip 25 and thus the inner Sealing edge 30 additionally pressed on the valve seat 10.

Zwischen den einzelnen Einspritzungen herrscht im Brennraum ein zum Teil sehr hoher Druck, so dass Verbrennungsgase durch die Einspritzöffnungen in das Kraftstoffeinspritzventil eindringen können. Dies wird bei dem vorliegenden Einspritzventil dadurch wirkungsvoll verhindert, dass die innere Einspritzöffnungsreihe 12 durch die innere Ventilnadel 7 sicher abgedichtet wird und die äußere Einspritzöffnungsreihe 14 durch zwei Dichtkanten, nämlich die innere Dichtkante 30 und die äußere Dichtkante 32, abgedichtet wird. Brennraumgase können so weder in den Druckraum 16 noch in den Ringraum 20 gelangen. Umgekehrt ist es auch nicht möglich, dass Kraftstoff aus dem Ringraum 20 durch die Einspritzöffnungen unkontrolliert in den Brennraum der Brennkraftmaschine gelangt und dort zu erhöhten Kohlenwasserstoff-Emissionen führt.Between the individual injections prevails in the combustion chamber a sometimes very high pressure, allowing combustion gases through the injection openings in the fuel injection valve can penetrate. This is in the present injection valve This effectively prevents the inner Injection opening 12 through the inner valve needle. 7 is securely sealed and the outer injection port row 14 by two sealing edges, namely the inner sealing edge 30 and the outer sealing edge 32, is sealed. Combustion chamber gases can neither in the pressure chamber 16 still in the Annulus 20 arrive. Conversely, it is not possible that fuel from the annulus 20 through the injection ports uncontrolled in the combustion chamber of the internal combustion engine and there to increased hydrocarbon emissions leads.

Claims (7)

  1. Fuel injection valve for internal combustion engines having a valve body (1) in which an external valve needle (5) and an internal valve needle (7), which is guided in the external valve needle (5), are arranged in a bore (3), at least one of which valve needles (5; 7) interacts with a valve seat (10) which is formed at the combustion chamber end of the bore (3) and in which an external row (14) of injection openings and an internal row (12) of injection openings are formed, the internal valve needle (7) controlling the opening of the internal row (12) of injection openings and the external valve needle (5) controlling the opening of the external row (14) of injection openings, and having pressure faces (11; 107) which are formed on the internal valve needle (7) and the external valve needle (5) and to which pressure is applied by the supplied fuel in the opening direction counter to a closing force, characterized in that the external valve needle (5) has a circumferential sealing lip (25) which protrudes inwards and has an internal sealing edge (30), the internal sealing edge (30) coming to bear against the valve seat (10) in the closed position of the external valve needle (7).
  2. Fuel injection valve according to Claim 1, characterized in that an annular space (20) which can be filled with fuel at high pressure is formed between the external valve needle (5) and the internal valve needle (7).
  3. Fuel injection valve according to Claim 2, characterized in that the external valve needle (5) is embodied essentially in the form of a hollow cylinder, and in that the annular space (20) is formed by a recess on the internal lateral face of the external valve needle (5).
  4. Fuel injection valve according to Claim 3, characterized in that the annular space (20) is connected via at least one connecting bore (22) formed in the external valve needle (5) to a pressure space (16) which can be filled with fuel at high pressure.
  5. Fuel injection valve according to Claim 1, characterized in that the sealing lip (25) has a seating face (26) which is directed away from the valve seat (10) and against which the internal valve needle (7) comes to bear with a sealing face (207) in the closed position under the effect of the closing force.
  6. Fuel injection valve according to Claim 1, characterized in that the external valve needle (5) has, in addition to the internal sealing edge (30), an additional external sealing edge (32) which is arranged upstream of the internal sealing edge (30) so that the external sealing edge (32) and the internal sealing edge (30) close off the external row (14) of injection openings.
  7. Fuel injection valve according to Claim 6, characterized in that, during the closing movement of the external valve needle (5), the internal sealing edge (30) first comes to bear against the valve seat (10) and the external sealing edge (32) also comes to bear only after the further closing movement accompanied by elastic deformation of the sealing lip (25).
EP02767066A 2001-11-09 2002-07-27 Fuel injection valve for internal combustion engines Expired - Lifetime EP1446571B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10155227A DE10155227A1 (en) 2001-11-09 2001-11-09 Fuel injection valve for internal combustion engines
DE10155227 2001-11-09
PCT/DE2002/002776 WO2003040543A1 (en) 2001-11-09 2002-07-27 Fuel injection valve for internal combustion engines

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EP1446571A1 EP1446571A1 (en) 2004-08-18
EP1446571B1 true EP1446571B1 (en) 2005-04-06

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EP (1) EP1446571B1 (en)
JP (1) JP4191606B2 (en)
DE (2) DE10155227A1 (en)
WO (1) WO2003040543A1 (en)

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JP2005508474A (en) 2005-03-31
DE10155227A1 (en) 2003-05-22
DE50202740D1 (en) 2005-05-12
WO2003040543A1 (en) 2003-05-15
JP4191606B2 (en) 2008-12-03
EP1446571A1 (en) 2004-08-18

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