EP1346143A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines

Info

Publication number
EP1346143A1
EP1346143A1 EP01270695A EP01270695A EP1346143A1 EP 1346143 A1 EP1346143 A1 EP 1346143A1 EP 01270695 A EP01270695 A EP 01270695A EP 01270695 A EP01270695 A EP 01270695A EP 1346143 A1 EP1346143 A1 EP 1346143A1
Authority
EP
European Patent Office
Prior art keywords
valve member
bore
combustion chamber
throttle
collar
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.)
Granted
Application number
EP01270695A
Other languages
German (de)
French (fr)
Other versions
EP1346143B1 (en
Inventor
Detlev Potz
Friedrich Moser
Thomas Kuegler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1346143A1 publication Critical patent/EP1346143A1/en
Application granted granted Critical
Publication of EP1346143B1 publication Critical patent/EP1346143B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

Definitions

  • the invention relates to a fuel injection valve for
  • a valve body has a bore in which a piston-shaped valve member is arranged to be longitudinally displaceable against a closing force. At its end on the combustion chamber side, the valve member merges into a valve sealing surface which interacts with a valve seat and thus controls the opening of at least one injection opening.
  • the valve member is guided in the bore in a sealing section facing away from the combustion chamber and in a guide section facing the combustion chamber in the bore.
  • the guide section is divided into an annular collar facing away from the combustion chamber, which is separated by an annular groove from lateral recesses formed on the valve member, so that fuel can flow through these recesses between the wall of the bore and the valve member.
  • the annular collar At its end facing the combustion chamber, the annular collar has a control edge which interacts with a sealing edge formed on the wall of the bore.
  • a bore is formed in the valve member, which runs obliquely to the longitudinal axis of the valve member and the pressure chamber, which faces away from the combustion chamber to the collar is formed between the valve member and the wall of the bore, connects to one of the recesses on the guide portion of the valve member.
  • the bore is designed as a throttle bore, so that fuel throttled from the pressure chamber 5 to the recesses and thus to a second pressure chamber, which is formed between the valve member and the wall of the bore between the guide section and the valve sealing surface.
  • the injection opening is injected into the combustion chamber of the internal combustion engine. As long as the control edge on the valve member faces the sealing edge of the combustion chamber, only a little fuel can get from the first into the second pressure chamber through the throttle bore. If in the course of the opening stroke movement of the valve
  • the first pressure chamber is connected to the second pressure chamber via the annular groove and the recesses in the guide section of the valve member, and fuel can flow from the first to the second pressure chamber almost unthrottled. This increases
  • the known fuel spray valve has the disadvantage that the necessary throttle bore is expensive to manufacture, which makes the production quite expensive. Furthermore, there is the disadvantage that the throttle bore has to be introduced at an early stage of the production process because of the necessary clamping of the valve member, which makes subsequent adjustment of the throttle bore to other tolerances that are impossible.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the throttle cross section between the first pressure chamber and the second pressure chamber by a
  • Throttle channel is realized, which connects both end faces of the ring collar with each other.
  • This throttle channel can be introduced after completion of the entire valve member, so that an adaptation to the other tolerances of the injection valve, for. B. the size of the annular gap between the collar and the bore of the valve body is possible.
  • the throttle duct is designed as a throttle bore which runs at least approximately parallel to the longitudinal axis of the valve member in the collar.
  • a throttle bore can advantageously be produced by laser drilling, which is a non-contact method, so that the throttle bore can be introduced without problems after the entire valve member has been completed. It can also be provided that a plurality of such throttle bores are arranged distributed over the circumference of the annular collar in order to ensure a uniform flow of fuel from the first into the second pressure chamber.
  • the throttle bores are preferably arranged in such a way that one of the recesses on the guide section of the valve member the combustion chamber-side extension of the throttle bore, so that there is free access to the combustion chamber-facing end face of the collar by a laser beam coming from the combustion chamber end of the valve member.
  • the throttle connection is formed by at least one side bevel on the collar. These cuts can be carried out over a large area, which is easy to produce and enables a very precise adjustment of the cross section of the throttle connection.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention with an uncut valve member
  • FIG. 2 shows an enlargement of FIG. 1 in the region of the guide section of the valve member
  • FIG. 3 shows a cross section along the line III-III of Figure 2, Figure 4 the same detail as Figure 2 of another
  • a fuel injection valve according to the invention is shown in longitudinal section in FIG.
  • a bore 3 is formed in a valve body 1, which is open at the end of the valve body 1 facing away from the combustion chamber and merges into an essentially conical valve seat 13 at the end on the combustion chamber side.
  • a piston-shaped valve member 5 is arranged in the bore 3 so as to be longitudinally displaceable. The valve member 5 is guided with a sealing section 105 in a bore sealing section 103 facing away from the combustion chamber in the bore 3 and, moreover, with a guide section 205 in a bore guide section 203 on the combustion chamber side.
  • valve member 5 merges into a valve sealing surface 15 which is essentially conical and cooperates with the valve seat 13 so that the injection openings 17 are closed when the valve sealing surface 15 abuts on the valve seat 13 and are released when the valve sealing surface 15 is lifted off the valve seat 13.
  • a first pressure chamber 9 is formed between the valve member 5 and the wall of the bore 3, which can be connected via a feed channel 7 running in the valve body 1 to a high-pressure fuel source, not shown in the drawing.
  • a second pressure chamber 19 is formed between the valve member 5 and the wall of the bore 3 by a radial enlargement of the bore 3. The pressure chamber 19 interacts with the valve sealing surface 15 and the valve seat 13 via the injection openings 17 Combustion chamber is connectable.
  • FIG. 2 shows an enlarged illustration of FIG. 1 in the area of the bore guide section 203.
  • FIG. 3 shows the corresponding cross section along the line III-III of FIG 1 and FIG. 2.
  • the guide section 205 is guided in the bore guide section 203 and has three planar grindings 28, so that fuel can flow past the guide section 205 in the axial direction of the valve member 5. Facing away from the combustion chamber, an annular groove 26 adjoins the guide section 205 and an annular collar 22 thereon.
  • the annular collar 22 is arranged in a radial plane of the valve member 5 and has an end surface 37 facing the combustion chamber and an end surface 36 facing away from the combustion chamber.
  • a control edge 34 is formed on the annular collar 22, which dips into the bore guide section 203 in the closed state of the fuel injection valve, that is, when the valve sealing surface 15 abuts the valve seat 13.
  • the bore guide section 203 is slightly reduced in diameter compared to the bore 3, so that an annular shoulder 30 is formed at the transition from the first pressure chamber 9 to the bore guide section 203, which is delimited by a sealing edge 32 which is formed at the start of the bore guide section 203.
  • the annular collar 22 has a diameter which is only slightly smaller than the diameter of the bore guide section 203, so that when the fuel injection valve is closed, practically no fuel from the first pressure chamber 9 past the annular collar 22 through the annular groove 26 and the recesses 28 into the second pressure chamber 19 can flow.
  • three throttle channels which are designed as throttle bores 40 and which connect the end face 36 of the collar 22 facing away from the combustion chamber to the end face 37 of the collar 22 facing the combustion chamber. It can also be provided to arrange more or less than three throttle channels.
  • the throttle bores 40 are arranged such that they run at least substantially parallel to the longitudinal axis 6 of the valve member 5 and that a bevel 28 is arranged in their extension on the combustion chamber side.
  • valve member 5 is acted upon by a device, not shown in the drawing, with a closing force which presses the valve member 5 with the valve sealing surface 15 against the valve seat 13. Since the valve member 5 tapers from the section guided in the sealing section 103 to the combustion chamber, a pressure shoulder 11 is formed on the valve member 5 and is arranged in the first pressure chamber 9. With a corresponding fuel pressure in the pressure chamber 9, there is a hydraulic force on the pressure shoulder 11, which has a component acting in the longitudinal direction of the valve member 5, which is opposite to the closing force. In this way, the valve member 5 can be moved in a pressure-controlled manner in the longitudinal direction counter to the closing force by the pressure in the first pressure chamber 9, and the injection openings 17 can thus be opened and closed.
  • the fuel injector works as follows: At the beginning of the injection, fuel is conducted under high pressure through the inlet channel 7 into the first pressure chamber 9. From there, the fuel flows through the throttle bores 40 into the second pressure chamber 19, so that the fuel pressure also increases there. If the fuel pressure in the first pressure chamber 9 reaches a certain level, the hydraulic force on the pressure shoulder 11 exerts a force against the closing force on the valve member 5, which force moves it away from the valve seat 13 in the axial direction. As a result, the valve sealing surface 15 lifts off the valve seat 13 and opens the injection openings 17.
  • the fuel can only pass through the throttle bores 40 from the first pressure chamber 9 into the second pressure chamber 19 and from there through the injection openings 17 into the combustion chamber of the internal combustion engine.
  • the throttle bores 40 only a low pressure is built up in the second pressure chamber 19 and so at the start of the injection only a little fuel per unit of time in the combustion injected space of the internal combustion engine.
  • the fuel supply through the inlet channel 7 is interrupted, and due to the falling fuel pressure in the first pressure chamber 9 and thus also in the second pressure chamber 19, the hydraulic force on the valve member 5 is reduced until the closing force becomes greater than the components of the hydraulic forces acting in the axial direction, and the valve member 5 moves back into the closed position.
  • FIG. 4 shows a further exemplary embodiment of the fuel injection valve according to the invention
  • FIG. 5 shows a cross section through the fuel injection valve shown in FIG. 4 along the line V-V.
  • the throttle channel between the first pressure chamber 9 and the second pressure chamber 19 is formed here by two throttle recesses 42 on the annular collar 22, which are designed as flat cuts parallel to the longitudinal axis 6 of the valve member 5. It can also be provided that more than two throttle recesses 42 are formed on the collar 22. These are preferably distributed uniformly over the circumference of the annular collar 22 in order to enable a uniform flow of fuel to the second pressure chamber 19.
  • the annular shoulder 30 is bevelled so that it encloses an angle with the longitudinal axis 6 of the valve member 5.
  • an annular shoulder 30, which is arranged in a radial plane of the valve member 5 a great deal of effort would be required to manufacture the radius required at the transition from the bore 3 to the annular shoulder 30 so small and with such a close tolerance that it would not reach into the Sealing edge 32 runs out.
  • such a radius would mean a sharp notch and thus a significant weakening of the valve body 1 combined with a reduced pressure threshold strength.
  • the position of the sealing edge 32 would be difficult to position exactly and to measure only with great effort.
  • a beveled annular shoulder 30, however, allows a larger radius with greater tolerance without running into the sealing edge 32. This enables the very important position of the sealing edge 32 to be easily manufactured and measured.

Abstract

The invention relates to a fuel injection valve comprising a valve body (1), with a piston-shaped valve member (5) which is arranged therein and which can be longitudinally displaced in a bore (3).. The valve member (5) is guided in the bore (3) with a tight section (105) facing the combustion chamber and a guide section (205) on the side of the combustion chamber. The valve member (5) is surrounded by a first pressure chamber (9) which can be filled by fuel between the tight section (105) and the guiding section (205), and by a second pressure chamber (19) between the guide section (205) and the end next to the combustion chamber. An annular collar (22) is formed on the guide section (205) of the valve member. Said collar (22) has a front surface which is orientated towards the combustion chamber (37) and a front surface opposite the combustion chamber (36). When the valve member (5) is raised in an opening direction, the annular collar (22) moves into a bore guide section (203) and opens or connects the first pressure chamber (9) to the second pressure chamber (19). A throttle connection (40) is embodied on the annular collar (22).

Description

Kraf stoffeinspritzventil für Brennkraf maschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil fürThe invention relates to a fuel injection valve for
Brennkraftmaschinen aus, vorzugsweise selbstzündender Brennkraftmaschinen, wie es aus der Schrift DE 198 57 244 AI bekannt ist. Ein Ventilkörper weist eine Bohrung auf, in der ein kolbenförmiges Ventilglied entgegen einer Schließkraft längsverschiebbar angeordnet ist. Das Ventilglied geht an seinem brennraumseitigen Ende in eine Ventildichtfläche ü- ber, die mit einem Ventilsitz zusammenwirkt und so die Öffnung wenigstens einer Einspritzöffnung steuert. Das Ventilglied ist in der Bohrung in einem brennraumabgewandten Dichtabschnitt und in einem brennraumzugewandten Führungsabschnitt in der Bohrung geführt. Der Führungsabschnitt unterteilt sich in einen brennraumabgewandten Ringbund, der durch eine Ringnut von am Ventilglied ausgebildeten seitlichen Ausnehmungen getrennt ist, so daß Kraftstoff durch diese Ausnehmungen zwischen der Wand der Bohrung und dem Ventilglied vorbeifließen kann. Der Ringbund weist an seinem brennraumzugewandten Ende eine Steuerkante auf, die mit einer an der Wand der Bohrung ausgebildeten Dichtkante zusammenwirkt. Darüber hinaus ist im Ventilglied eine Bohrung ausgebildet, die schräg zur Längsachse des Ventilglieds verläuft und den Druckraum, der brennraumabgewandt zum Ringbund zwischen dem Ventilglied und der Wand der Bohrung ausgebildet ist, mit einer der Ausnehmungen am Führungsabschnitt des Ventilgliedes verbindet. Die Bohrung ist als Drosselbohrung ausgebildet, so daß Kraftstoff aus dem Druckraum gedrosselt 5 zu den Ausnehmungen und damit zu einem zweiten Druckraum, der zwischen dem Ventilglied und der Wand der Bohrung zwischen dem Führungsabschnitt und der Ventildichtfläche ausgebildet ist, fließen kann. Im geschlossenen Zustand des Kraftstoffeinspritzventils liegt die Ventildichtfläche desInternal combustion engines, preferably self-igniting internal combustion engines, as is known from DE 198 57 244 AI. A valve body has a bore in which a piston-shaped valve member is arranged to be longitudinally displaceable against a closing force. At its end on the combustion chamber side, the valve member merges into a valve sealing surface which interacts with a valve seat and thus controls the opening of at least one injection opening. The valve member is guided in the bore in a sealing section facing away from the combustion chamber and in a guide section facing the combustion chamber in the bore. The guide section is divided into an annular collar facing away from the combustion chamber, which is separated by an annular groove from lateral recesses formed on the valve member, so that fuel can flow through these recesses between the wall of the bore and the valve member. At its end facing the combustion chamber, the annular collar has a control edge which interacts with a sealing edge formed on the wall of the bore. In addition, a bore is formed in the valve member, which runs obliquely to the longitudinal axis of the valve member and the pressure chamber, which faces away from the combustion chamber to the collar is formed between the valve member and the wall of the bore, connects to one of the recesses on the guide portion of the valve member. The bore is designed as a throttle bore, so that fuel throttled from the pressure chamber 5 to the recesses and thus to a second pressure chamber, which is formed between the valve member and the wall of the bore between the guide section and the valve sealing surface. In the closed state of the fuel injection valve, the valve sealing surface of the
L0 Ventilglieds am Ventilsitz an und die Steuerkante am Ringbund ist brennraumzugewandt zur Dichtkante angeordnet, so daß nur über die Drosselbohrung eine Verbindung vom ersten zum zweiten Druckraum besteht. Soll eine Einspritzung erfolgen, so wird Kraftstoff unter hohem Druck in den erstenL0 valve member on the valve seat and the control edge on the collar is arranged facing the sealing edge so that there is only a connection from the first to the second pressure chamber via the throttle bore. If an injection is to take place, fuel will be under high pressure in the first
L5 Druckraum eingeleitet und fließt von dort durch die Drossel- bohrung auch in den zweiten Druckraum. Reicht die hydraulische Kraft auf das Ventilglied aus, dieses entgegen der Schließkraft vom Ventilsitz wegzubewegen, so hebt die Ventildichtfläche vom Ventilsitz ab und Kraftstoff wird durchL5 pressure chamber initiated and from there flows through the throttle bore into the second pressure chamber. If the hydraulic force on the valve member is sufficient to move it away from the valve seat against the closing force, the valve sealing surface lifts off the valve seat and fuel is exhausted
20 die Einspritzöffnung in den Brennraum der Brennkraftmaschine eingespritzt. Solange die Steuerkante am Ventilglied brennraumzugewandt zur Dichtkante ist, kann nur wenig Kraftstoff durch die Drosselbohrung vom ersten in den zweiten Druckraum gelangen. Wenn im Zuge der Öffnungshubbewegung des Ventil-20 the injection opening is injected into the combustion chamber of the internal combustion engine. As long as the control edge on the valve member faces the sealing edge of the combustion chamber, only a little fuel can get from the first into the second pressure chamber through the throttle bore. If in the course of the opening stroke movement of the valve
25 glieds die Steuerkante die Dichtkante passiert, so wird der erste Druckraum über die Ringnut und die Ausnehmungen am Führungsabschnitt des Ventilgliedes mit dem zweiten Druckraum verbunden und Kraftstoff kann nahezu ungedrosselt vom ersten in den zweiten Druckraum fließen. Hierdurch erhöhtIf the control edge passes the sealing edge, the first pressure chamber is connected to the second pressure chamber via the annular groove and the recesses in the guide section of the valve member, and fuel can flow from the first to the second pressure chamber almost unthrottled. This increases
30 sich der Druck im zweiten Druckraum und somit die Rate der30 the pressure in the second pressure chamber and thus the rate of
Einspritzung, so daß insgesamt eine Einspritzverlaufsformung erreicht wird, bei der zu Beginn der Öffnungshubbewegung bedingt durch den relativ geringen Druck im zweiten Druckraum nur wenig Kraftstoff eingespritzt wird und die HauptmengeInjection, so that overall an injection profile is achieved in which at the beginning of the opening stroke movement, due to the relatively low pressure in the second pressure chamber, only a little fuel is injected and the main amount
35 des Kraftstoffs mit hohem Druck erst in der darauffolgenden Haupteinspritzung. Hierbei weist das bekannte Kraftstoffein- spritzventil jedoch den Nachteil auf, daß die notwendige Drosselbohrung aufwendig zu fertigen ist, was die Herstellung recht kostenintensiv macht. Weiterhin ergibt sich der Nachteil, daß die Drosselbohrung wegen der notwendigen Ein- Spannungen des Ventilglieds bereits in einem frühen Stadium des Herstellungsprozesses eingebracht werden muß, was eine spätere Anpassung der Drosselbohrung an sonstige auftretende Toleranzen unmöglich macht .35 of the fuel with high pressure only in the following main injection. Here, the known fuel spray valve, however, has the disadvantage that the necessary throttle bore is expensive to manufacture, which makes the production quite expensive. Furthermore, there is the disadvantage that the throttle bore has to be introduced at an early stage of the production process because of the necessary clamping of the valve member, which makes subsequent adjustment of the throttle bore to other tolerances that are impossible.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, daß der Drosselquerschnitt zwischen dem ersten Druckraum und dem zweiten Druckraum durch einenThe fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the throttle cross section between the first pressure chamber and the second pressure chamber by a
Drosselkanal realisiert ist, der beide Stirnseiten des Ringbundes miteinander verbinde . Dieser Drosselkanal läßt sich nach Fertigstellung des gesamten Ventilglieds einbringen, so daß eine Anpassung an die sonstigen Toleranzen des Ein- spritzventils, z. B. die Größe des Ringspalts zwischen dem Ringbund und der Bohrung des Ventilkörpers möglich ist.Throttle channel is realized, which connects both end faces of the ring collar with each other. This throttle channel can be introduced after completion of the entire valve member, so that an adaptation to the other tolerances of the injection valve, for. B. the size of the annular gap between the collar and the bore of the valve body is possible.
In einer ersten vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist der Drosselkanal als Drosselbohrung ausge- bildet, die zumindest annähernd parallel zur Längsachse des Ventilglieds im Ringbund verläuft. Eine solche Drosselbohrung läßt sich in vorteilhafter Weise durch Laserbohrung herstellen, was es ein berührungsloses Verfahren ist, so daß die Drosselbohrung problemlos nach Fertigstellung des gesam- ten Ventilglieds eingebracht werden kann. Dabei kann es auch vorgesehen sein, daß eine Vielzahl von solchen Drosselbohrungen über den Umfang des Ringbundes verteilt angeordnet ist, um einen gleichmäßigen Fluß des Kraftstoffs vom ersten in den zweiten Druckraum zu gewährleisten. Die Drosselboh- rungen sind dabei vorzugsweise so angeordnet, daß sich eine der Ausnehmungen am Führungsabschnitt des Ventilglieds in der brennraumseitigen Verlängerung der Drosselbohrung befindet, so daß eine freie Zugänglichkeit der brennraumzugewandten Stirnseite des Ringbunds durch einen vom brennraumseitigen Ende des Ventilglieds kommenden Laserstrahl gegeben ist.In a first advantageous embodiment of the subject matter of the invention, the throttle duct is designed as a throttle bore which runs at least approximately parallel to the longitudinal axis of the valve member in the collar. Such a throttle bore can advantageously be produced by laser drilling, which is a non-contact method, so that the throttle bore can be introduced without problems after the entire valve member has been completed. It can also be provided that a plurality of such throttle bores are arranged distributed over the circumference of the annular collar in order to ensure a uniform flow of fuel from the first into the second pressure chamber. The throttle bores are preferably arranged in such a way that one of the recesses on the guide section of the valve member the combustion chamber-side extension of the throttle bore, so that there is free access to the combustion chamber-facing end face of the collar by a laser beam coming from the combustion chamber end of the valve member.
In einem weiteren vorteilhaften Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils ist die Drosselverbindung durch wenigstens einen seitlichen Anschliff am Ringbund ausgebildet. Diese Anschliffe können flächenhaft ausgeführt werden, was einfach herstellbar ist und eine sehr genaue Einstellung des Querschnitts der Drosselverbindung möglich macht .In a further advantageous embodiment of the fuel injection valve according to the invention, the throttle connection is formed by at least one side bevel on the collar. These cuts can be carried out over a large area, which is easy to produce and enables a very precise adjustment of the cross section of the throttle connection.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Ge- genstandes der Erfindung sind der Zeichnung, der Beschreibung und den Ansprüchen entnehmbar.Further advantages and advantageous refinements of the object of the invention can be found in the drawing, the description and the claims.
Zeichnungdrawing
In der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils gezeigt . Es zeigtVarious exemplary embodiments of the fuel injection valve according to the invention are shown in the drawing. It shows
Figur 1 einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil mit einem ungeschnittenen Ven- tilglied,FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention with an uncut valve member,
Figur 2 eine Vergrößerung von Figur 1 im Bereich des Führungsabschnitts des Ventilglieds,FIG. 2 shows an enlargement of FIG. 1 in the region of the guide section of the valve member,
Figur 3 einen Querschnitt entlang der Linie III-III der Figur 2, - Figur 4 denselben Ausschnitt wie Figur 2 eines anderen3 shows a cross section along the line III-III of Figure 2, Figure 4 the same detail as Figure 2 of another
Ausführungsbeispiels undEmbodiment and
Figur 5 einen Querschnitt entlang der Linie V-V der Figur 4.5 shows a cross section along the line V-V of Figure 4.
Beschreibung des Ausführungsbeispiels In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzven- til im Längsschnitt dargestellt. In einem Ventilkörper 1 ist eine Bohrung 3 ausgebildet, die am brennraumabgewandten Ende des Ventilkörpers 1 offen ist und am brennraumseitigen Ende in einen im wesentlichen konischen Ventilsitz 13 übergeht. Am brennraumseitigen Ende der Bohrung 3 ist wenigstens eine Einspritzöffnung 17 ausgebildet, die die Bohrung 3 mit dem Brennraum der in der Zeichnung nicht dargestellten Brennkraftmaschine verbindet. In der Bohrung 3 ist ein kolbenför- miges Ventilglied 5 längsverschiebbar angeordnet. Das Ventilglied 5 wird mit einem Dichtungsabschnitt 105 in einem brennraumabgewandten Bohrungsdichtungsabschnitt 103 in der Bohrung 3 dichtend geführt und darüber hinaus mit einem Führungsabschnitt 205 in einem brennraumseitigen Bohrungsfüh- rungsabschnitt 203. An seinem brennraumseitigen Ende geht das Ventilglied 5 in eine Ventildichtfläche 15 über, die im wesentlichen konisch ausgebildet ist und mit dem Ventilsitz 13 zusammenwirkt, so daß die Einspritzöffnungen 17 bei Anlage der Ventildichtfläche 15 am Ventilsitz 13 verschlossen werden und bei vom Ventilsitz 13 abgehobener Ventildichtfläche 15 freigegeben werden. Zwischen dem Bohrungsdichtungsabschnitt 103 und dem Bohrungsführungsabschnitt 203 ist zwischen dem Ventilglied 5 und der Wand der Bohrung 3 ein erster Druckraum 9 ausgebildet, der über einen im Ventilkörper 1 verlaufenden Zulaufkanal 7 mit einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle verbindbar ist. Zwischen dem Bohrungsführungsabschnitt 203 und dem Ventilsitz 13 ist zwischen dem Ventilglied 5 und der Wand der Bohrung 3 durch eine radiale Erweiterung der Bohrung 3 ein zweiter Druckraum 19 ausgebildet, der über das Zusammenspiel von Ventildichtfläche 15 und Ventilsitz 13 über die Ein- spritzöffnungen 17 mit dem Brennraum verbindbar ist .Description of the embodiment A fuel injection valve according to the invention is shown in longitudinal section in FIG. A bore 3 is formed in a valve body 1, which is open at the end of the valve body 1 facing away from the combustion chamber and merges into an essentially conical valve seat 13 at the end on the combustion chamber side. At the combustion chamber end of the bore 3, at least one injection opening 17 is formed, which connects the bore 3 with the combustion chamber of the internal combustion engine, not shown in the drawing. A piston-shaped valve member 5 is arranged in the bore 3 so as to be longitudinally displaceable. The valve member 5 is guided with a sealing section 105 in a bore sealing section 103 facing away from the combustion chamber in the bore 3 and, moreover, with a guide section 205 in a bore guide section 203 on the combustion chamber side. At its combustion chamber end, the valve member 5 merges into a valve sealing surface 15 which is essentially conical and cooperates with the valve seat 13 so that the injection openings 17 are closed when the valve sealing surface 15 abuts on the valve seat 13 and are released when the valve sealing surface 15 is lifted off the valve seat 13. Between the bore sealing section 103 and the bore guide section 203, a first pressure chamber 9 is formed between the valve member 5 and the wall of the bore 3, which can be connected via a feed channel 7 running in the valve body 1 to a high-pressure fuel source, not shown in the drawing. Between the bore guide section 203 and the valve seat 13, a second pressure chamber 19 is formed between the valve member 5 and the wall of the bore 3 by a radial enlargement of the bore 3. The pressure chamber 19 interacts with the valve sealing surface 15 and the valve seat 13 via the injection openings 17 Combustion chamber is connectable.
Figur 2 zeigt eine vergrößerte Darstellung von Figur 1 im Bereich des Bohrungsführungsabschnitts 203. Figur 3 zeigt den entsprechenden Querschnitt entlang der Linie III-III der Figur 1 bzw. Figur 2. Der Führungsabschnitt 205 ist im Bohrungsführungsabschnitt 203 geführt und weist drei flächenhafte Anschliffe 28 auf, so daß Kraftstoff am Führungsabschnitt 205 vorbei in axialer Richtung des Ventilglieds 5 fließen kann. Brennraumabgewandt schließt sich an den Führungsabschnitt 205 eine Ringnut 26 an und an diese wiederum ein Ringbund 22. Der Ringbund 22 ist in einer Radialebene des Ventilglieds 5 angeordnet und weist eine brennraumzuge- wandte Stirnfläche 37 und eine brennraumabgewandte Stirnflä- ehe 36 auf. Am Übergang des Ringbunds 22 zur Ringnut 26 ist am Ringbund 22 eine Steuerkante 34 ausgebildet, die in geschlossenem Zustand des Kraftstoffeinspritzventils, das ist, wenn die Ventildichtfläche 15 am Ventilsitz 13 anliegt, in den Bohrungsführungsabschnitt 203 eintaucht. Der Bohrungs- führungsabschnitt 203 ist hierbei gegenüber der Bohrung 3 im Durchmesser etwas verringert, so daß am Übergang des ersten Druckraums 9 zum Bohrungsführungsabschnitt 203 eine Ringschulter 30 ausgebildet ist, die von einer Dichtkante 32 begrenzt wird, die am Beginn des Bohrungsführungsabschnitts 203 ausgebildet ist. Der Ringbund 22 weist einen Durchmesser auf, der nur geringfügig kleiner ist als der Durchmesser des Bohrungsführungsabschnitts 203, so daß bei geschlossenem Kraftstoffeinspritzventil praktisch kein Kraftstoff aus dem ersten Druckraum 9 am Ringbund 22 vorbei durch die Ringnut 26 und die Ausnehmungen 28 in den zweiten Druckraum 19 fließen kann. Im Ringbund 22 sind drei Drosselkanäle angeordnet, die als Drosselbohrungen 40 ausgebildet sind und die die brennraumabgewandte Stirnseite 36 des Ringbundes 22 mit der brennraumzugewandten Stirnseite 37 des Ringbundes 22 verbin- den. Dabei kann es auch vorgesehen sein, mehr oder weniger als drei Drosselkanäle anzuordnen. Die Drosselbohrungen 40 sind dabei so angeordnet, daß sie zumindest im wesentlichen parallel zur Längsachse 6 des Ventilglieds 5 verlaufen und daß in ihrer brennraumseitigen Verlängerung jeweils ein An- schliff 28 angeordnet ist. Das Ventilglied 5 wird durch eine in der Zeichnung nicht dargestellte Vorrichtung mit einer Schließkraft beaufschlagt, die das Ventilglied 5 mit der Ventildichtfläche 15 gegen den Ventilsitz 13 preßt. Da sich das Ventilglied 5 vom im Dichtungsabschnitt 103 geführten Abschnitt zum Brennraum hin verjüngt, ist am Ventilglied 5 eine Druckschulter 11 ausgebildet, die im ersten Druckraum 9 angeordnet ist. Bei einem entsprechenden Kraftstoffdruck im Druckraum 9 ergibt sich eine hydraulische Kraft auf die Druckschulter 11, die eine in Längsrichtung des Ventilglieds 5 wirkende Komponente hat, die der Schließkraft entgegengerichtet ist. Auf diese Weise läßt sich das Ventilglied 5 druckgesteuert durch den Druck im ersten Druckraum 9 in Längsrichtung entgegen der Schließkraft bewegen und so die Einspritzöffnungen 17 auf- und zusteuern.FIG. 2 shows an enlarged illustration of FIG. 1 in the area of the bore guide section 203. FIG. 3 shows the corresponding cross section along the line III-III of FIG 1 and FIG. 2. The guide section 205 is guided in the bore guide section 203 and has three planar grindings 28, so that fuel can flow past the guide section 205 in the axial direction of the valve member 5. Facing away from the combustion chamber, an annular groove 26 adjoins the guide section 205 and an annular collar 22 thereon. The annular collar 22 is arranged in a radial plane of the valve member 5 and has an end surface 37 facing the combustion chamber and an end surface 36 facing away from the combustion chamber. At the transition from the annular collar 22 to the annular groove 26, a control edge 34 is formed on the annular collar 22, which dips into the bore guide section 203 in the closed state of the fuel injection valve, that is, when the valve sealing surface 15 abuts the valve seat 13. The bore guide section 203 is slightly reduced in diameter compared to the bore 3, so that an annular shoulder 30 is formed at the transition from the first pressure chamber 9 to the bore guide section 203, which is delimited by a sealing edge 32 which is formed at the start of the bore guide section 203. The annular collar 22 has a diameter which is only slightly smaller than the diameter of the bore guide section 203, so that when the fuel injection valve is closed, practically no fuel from the first pressure chamber 9 past the annular collar 22 through the annular groove 26 and the recesses 28 into the second pressure chamber 19 can flow. Arranged in the collar 22 are three throttle channels which are designed as throttle bores 40 and which connect the end face 36 of the collar 22 facing away from the combustion chamber to the end face 37 of the collar 22 facing the combustion chamber. It can also be provided to arrange more or less than three throttle channels. The throttle bores 40 are arranged such that they run at least substantially parallel to the longitudinal axis 6 of the valve member 5 and that a bevel 28 is arranged in their extension on the combustion chamber side. The valve member 5 is acted upon by a device, not shown in the drawing, with a closing force which presses the valve member 5 with the valve sealing surface 15 against the valve seat 13. Since the valve member 5 tapers from the section guided in the sealing section 103 to the combustion chamber, a pressure shoulder 11 is formed on the valve member 5 and is arranged in the first pressure chamber 9. With a corresponding fuel pressure in the pressure chamber 9, there is a hydraulic force on the pressure shoulder 11, which has a component acting in the longitudinal direction of the valve member 5, which is opposite to the closing force. In this way, the valve member 5 can be moved in a pressure-controlled manner in the longitudinal direction counter to the closing force by the pressure in the first pressure chamber 9, and the injection openings 17 can thus be opened and closed.
Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Zu Beginn der Einspritzung wird Kraftstoff unter hohem Druck durch den Zulaufkanal 7 in den ersten Druckraum 9 geleitet. Von dort strömt der Kraftstoff durch die Drosselbohrungen 40 in den zweiten Druckraum 19, so daß auch dort der Kraftstoffdruck zunimmt. Erreicht der Kraftstoffdruck im ersten Druckraum 9 ein bestimmtes Niveau, so wird durch die hydraulische Kraft auf die Druckschulter 11 eine Kraft ent- gegen der Schließkraft auf das Ventilglied 5 ausgeübt, die dieses in axialer Richtung vom Ventilsitz 13 wegbewegt. Hierdurch hebt die Ventildichtfläche 15 vom Ventilsitz 13 ab und gibt die Einspritzöffnungen 17 frei. Solange sich die Steuerkante 34 des Ringbunds 22 innerhalb des Bohrungsfüh- rungsabschnitts 203 befindet, kann der Kraftstoff nur durch die Drosselbohrungen 40 vom ersten Druckraum 9 in den zweiten Druckraum 19 und von dort durch die Einspritzöffnungen 17 in den Brennraum der Brennkraftmaschine gelangen. Durch diese Drosselung des Zuflusses wird nur ein geringer Druck im zweiten Druckraum 19 aufgebaut und so zu Beginn der Einspritzung nur wenig Kraftstoff pro Zeiteinheit in den Brenn- räum der Brennkraftmaschine eingespritzt . Erreicht die Steuerkante 34 die Dichtkante 32 und passiert diese in Öffnungsrichtung des Ventilglieds 5, so wird zwischen dem Ringbund 22 und der Bohrung 3 ein Ringspalt auf esteuert , durch den der Kraftstoff jetzt nahezu ungedrosselt in die Ringnut 26 und durch die Anschliffe 28 in den zweiten Druckraum 19 fließen kann. Da jetzt erheblich mehr Kraftstoff in den zweiten Druckraum 19 fließt, steigt dort der Druck weiter an und Kraftstoff kann jetzt mit einem hohen Druck und damit hoher Rate in den Brennraum der Brennkraftmaschine eingespritzt werden. Soll die Einspritzung beendet werden, so wird die Kraftstoffzufuhr durch den Zulaufkanal 7 unterbrochen, und durch den abfallenden Kraftstoffdruck im ersten Druckraum 9 und somit auch im zweiten Druckraum 19 verrin- gert sich die hydraulische Kraft auf das Ventilglied 5, bis die Schließkraft größer wird als die in axialer Richtung wirkenden Komponenten der hydraulischen Kräfte, und das Ventilglied 5 fährt wieder in die Schließposition zurück.The fuel injector works as follows: At the beginning of the injection, fuel is conducted under high pressure through the inlet channel 7 into the first pressure chamber 9. From there, the fuel flows through the throttle bores 40 into the second pressure chamber 19, so that the fuel pressure also increases there. If the fuel pressure in the first pressure chamber 9 reaches a certain level, the hydraulic force on the pressure shoulder 11 exerts a force against the closing force on the valve member 5, which force moves it away from the valve seat 13 in the axial direction. As a result, the valve sealing surface 15 lifts off the valve seat 13 and opens the injection openings 17. As long as the control edge 34 of the collar 22 is located within the bore guide section 203, the fuel can only pass through the throttle bores 40 from the first pressure chamber 9 into the second pressure chamber 19 and from there through the injection openings 17 into the combustion chamber of the internal combustion engine. As a result of this throttling of the inflow, only a low pressure is built up in the second pressure chamber 19 and so at the start of the injection only a little fuel per unit of time in the combustion injected space of the internal combustion engine. When the control edge 34 reaches the sealing edge 32 and passes it in the opening direction of the valve member 5, an annular gap is opened between the annular collar 22 and the bore 3, through which the fuel is now almost unthrottled in the annular groove 26 and through the bevels 28 in the second Pressure chamber 19 can flow. Since considerably more fuel now flows into the second pressure chamber 19, the pressure there rises further and fuel can now be injected into the combustion chamber of the internal combustion engine at a high pressure and thus at a high rate. If the injection is to be ended, the fuel supply through the inlet channel 7 is interrupted, and due to the falling fuel pressure in the first pressure chamber 9 and thus also in the second pressure chamber 19, the hydraulic force on the valve member 5 is reduced until the closing force becomes greater than the components of the hydraulic forces acting in the axial direction, and the valve member 5 moves back into the closed position.
Figur 4 zeigt ein weiteres Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils und Figur 5 einen Querschnitt durch das in Figur 4 dargestellte Kraftstoffeinspritzventil entlang der Linie V-V. Der Drosselkanal zwischen dem ersten Druckraum 9 und dem zweiten Druckraum 19 ist hier durch zwei Drosselausnehmungen 42 am Ringbund 22 ausgebildet, die als flächenhafte Anschliffe parallel zur Längsachse 6 des Ventilglieds 5 ausgeführt sind. Es kann auch vorgesehen sein, daß mehr als zwei Drosselausnehmungen 42 am Ringbund 22 ausgebildet sind. Diese werden dabei vor- zugsweise gleichmäßig über den Umfang des Ringbunds 22 verteilt angeordnet, um einen gleichmäßigen Kraftstoff ufluß zum zweiten Druckraum 19 zu ermöglichen.FIG. 4 shows a further exemplary embodiment of the fuel injection valve according to the invention and FIG. 5 shows a cross section through the fuel injection valve shown in FIG. 4 along the line V-V. The throttle channel between the first pressure chamber 9 and the second pressure chamber 19 is formed here by two throttle recesses 42 on the annular collar 22, which are designed as flat cuts parallel to the longitudinal axis 6 of the valve member 5. It can also be provided that more than two throttle recesses 42 are formed on the collar 22. These are preferably distributed uniformly over the circumference of the annular collar 22 in order to enable a uniform flow of fuel to the second pressure chamber 19.
In den Ausführungsbeispielen der Figuren 2 und 4 ist die Ringschulter 30 abgeschrägt ausgebildet, so daß sie mit der Längsachse 6 des Ventilglieds 5 einen Winkel einschließt. Bei einer Ringschulter 30, die in einer Radialebene des Ventilglieds 5 angeordnet ist, wäre ein großer Aufwand nötig, um den fertigungstechnisch notwendigen Radius am Übergang der Bohrung 3 zur Ringschulter 30 so klein und in so enger Toleranz zu fertigen, daß er nicht bis in die Dichtkante 32 ausläuft . Zudem würde ein solcher Radius eine scharfe Kerbe bedeuten und damit eine signifikante Schwächung des Ventilkörpers 1 verbunden mit einer verminderten Druckschwellfestigkeit. In diesem Fall wäre die Lage der Dichtkante 32 nur schwer exakt zu positionieren und nur mit großem Aufwand zu vermessen. Eine angeschrägte Ringschulter 30 läßt hingegen einen größeren Radius mit größerer Toleranz zu, ohne in die Dichtkante 32 auszulaufen. Dies ermöglicht so eine gute Fer- tigbarkeit und Meßbarkeit der sehr wichtigen Lage der Dicht- kante 32. In the exemplary embodiments in FIGS. 2 and 4, the annular shoulder 30 is bevelled so that it encloses an angle with the longitudinal axis 6 of the valve member 5. With an annular shoulder 30, which is arranged in a radial plane of the valve member 5, a great deal of effort would be required to manufacture the radius required at the transition from the bore 3 to the annular shoulder 30 so small and with such a close tolerance that it would not reach into the Sealing edge 32 runs out. In addition, such a radius would mean a sharp notch and thus a significant weakening of the valve body 1 combined with a reduced pressure threshold strength. In this case, the position of the sealing edge 32 would be difficult to position exactly and to measure only with great effort. A beveled annular shoulder 30, however, allows a larger radius with greater tolerance without running into the sealing edge 32. This enables the very important position of the sealing edge 32 to be easily manufactured and measured.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkörper (1) , in dem in einer Bohrung (3) ein kolbenförmiges Ventilglied (5) längsverschiebbar angeordnet ist, welches Ventilglied (5) wenigstens eine am brennraumseitigen Ende der Bohrung (3) angeordnete Ein- spritzöffnung (17) steuert und das mit einem brennraumabgewandten Dichtungsabschnitt (105) in der Bohrung (3) geführt ist, und mit einem Ringbund (22) , der brennraumabgewandt zum Dichtungsabschnitt (105) am Ventilglied (5) angeordnet ist und eine brennraumzugewandte Stirnfläche (37) und eine brennraumabgewandte Stirnfläche (36) aufweist und welcher Ringbund (22) den Raum zwischen dem Ventilglied (5) und Bohrung (3) in einen ersten, brennraumabgewandten und mit Kraftstoff befüllbaren Druckraum (9) und einen zweiten, brennraumzugewandten Druckraum (19) unterteilt, und mit einem Bohrungsführungsabschnitt1. Fuel injection valve for internal combustion engines with a valve body (1), in which a piston-shaped valve member (5) is arranged so as to be longitudinally displaceable in a bore (3), which valve member (5) has at least one injection opening (at the combustion chamber end of the bore (3)) 17) and which is guided in the bore (3) with a sealing section (105) facing away from the combustion chamber, and with an annular collar (22) which is arranged on the valve member (5) facing away from the sealing section (105) and an end face (37) facing the combustion chamber. and has an end face (36) facing away from the combustion chamber and which annular collar (22) divides the space between the valve member (5) and the bore (3) into a first pressure chamber (9) facing away from the combustion chamber and fillable with fuel and a second pressure chamber (19) facing the combustion chamber , and with a bore guide section
(203) der Bohrung (3) , in den der Ringbund (22) in Schließstellung des Ventilglieds (5) eintaucht und so die beiden Druckräume (9,19) bis auf einen Drosselquerschnitt trennt und aus dem der Ringbund (22) bei der Öffnungshub- bewegung des Ventilglieds (5) austaucht und so die Druckräume (9,19) miteinander verbindet, dadurch gekennzeichnet, daß der Drosselquerschnitt wenigstens ein im Ringbund (22) ausgebildeter Drosselkanal (40,42) ist, der die beiden Stirnseiten (36, 37) des Ringbunds (22) miteinan- der verbindet. (203) the bore (3) into which the collar (22) dips in the closed position of the valve member (5) and thus separates the two pressure chambers (9, 19) except for a throttle cross-section and from which the collar (22) during the opening stroke - Movement of the valve member (5) emerges and thus connects the pressure chambers (9, 19) to one another, characterized in that the throttle cross section is at least one throttle channel (40, 42) formed in the annular collar (22), which connects the two end faces (36, 37 ) of the ring collar (22).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der wenigstens eine Drosselkanal (40) innerhalb des Ventilglieds (5) verläuft.2. Fuel injection valve according to claim 1, characterized in that the at least one throttle channel (40) extends within the valve member (5).
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch ge- kennzeichnet, daß der wenigstens eine Drosselkanal als3. Fuel injection valve according to claim 2, characterized in that the at least one throttle channel as
Drosselbohrung (40) ausgebildet ist, die zumindest annähernd parallel zur Längsachse (6) des Ventilglieds (5) verläuft .Throttle bore (40) is formed, which runs at least approximately parallel to the longitudinal axis (6) of the valve member (5).
4. Kraftstoffeinspritzventil nach Anspruch 3, dadurch ge- kennzeichnet, daß eine Vielzahl von Drosselbohrungen (40) vorzugsweise gleichmäßig über den Umfang des Ringbunds (22) verteilt angeordnet ist.4. Fuel injection valve according to claim 3, character- ized in that a plurality of throttle bores (40) is preferably distributed evenly over the circumference of the annular collar (22).
5. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der Drosselkanal durch wenigstens eine am Ringbund (22) ausgebildete flächige Drosselausnehmung5. Fuel injection valve according to claim 1, characterized in that the throttle channel through at least one on the annular collar (22) formed flat throttle recess
(42) ausgebildet ist, die zumindest näherungsweise parallel zur Längsachse (6) des Ventilglieds (5) ausgebildet ist .(42) is formed, which is at least approximately parallel to the longitudinal axis (6) of the valve member (5).
6. Kraftstoffeinspritzventil nach einem der vorstehenden An- Sprüche, dadurch gekennzeichnet, daß das Ventilglied (5) einen Führungsabschnitt (205) aufweist, mit dem das Ventilglied (5) im Bohrungsführungsabschnitt (203) geführt ist und der brennraumzugewandt zum Ringbund (22) angeordnet ist, wobei der Führungsabschnitt (205) wenigstens ei- nen seitlichen Anschliff (28) aufweist, der in Verlängerung des wenigstens einen Drosselkanals (40) liegt. 6. Fuel injection valve according to one of the preceding claims, characterized in that the valve member (5) has a guide section (205) with which the valve member (5) is guided in the bore guide section (203) and the combustion chamber facing the collar (22) the guide section (205) has at least one side bevel (28) which is in the extension of the at least one throttle channel (40).
EP01270695A 2000-12-16 2001-11-28 Fuel injection valve for internal combustion engines Expired - Lifetime EP1346143B1 (en)

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DE10062959A DE10062959A1 (en) 2000-12-16 2000-12-16 Fuel injection valve for internal combustion engines
DE10062959 2000-12-16
PCT/EP2001/013921 WO2002048536A1 (en) 2000-12-16 2001-11-28 Fuel injection valve for internal combustion engines

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DE10346212A1 (en) * 2003-10-06 2005-04-21 Bosch Gmbh Robert Fuel injection valve for IC engines has fuel feed channel with throttle to form smallest flow profile from the feed channel to injection apertures
DE102004025729A1 (en) * 2004-05-26 2005-12-15 Robert Bosch Gmbh Fuel injection valve for an internal combustion engine
US7472844B2 (en) * 2005-12-21 2009-01-06 Caterpillar Inc. Fuel injector nozzle with tip alignment apparatus
JP4296519B2 (en) * 2006-12-19 2009-07-15 株式会社日立製作所 Fuel injection valve
JP2009138614A (en) * 2007-12-05 2009-06-25 Mitsubishi Heavy Ind Ltd Fuel injection valve of pressure accumulation-type fuel injection device
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DE102009046452A1 (en) * 2009-11-06 2011-05-12 Robert Bosch Gmbh Injector for a leak-free fuel injector
EP2568157A1 (en) * 2011-09-08 2013-03-13 Delphi Technologies Holding S.à.r.l. Injection Nozzle
CN104061101A (en) * 2014-07-14 2014-09-24 北京亚新科天纬油泵油嘴股份有限公司 Fuel feed system oil sprayer and oil spray nozzle thereof
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DE10062959A1 (en) 2002-06-20
JP2004515706A (en) 2004-05-27

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