EP1891324B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1891324B1
EP1891324B1 EP06743259.1A EP06743259A EP1891324B1 EP 1891324 B1 EP1891324 B1 EP 1891324B1 EP 06743259 A EP06743259 A EP 06743259A EP 1891324 B1 EP1891324 B1 EP 1891324B1
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EP
European Patent Office
Prior art keywords
valve
needle
body seat
fuel injection
injection
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EP06743259.1A
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German (de)
French (fr)
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EP1891324A1 (en
Inventor
Andreas Kerst
Gerhard Suenderhauf
Roland Schulz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1891324A1 publication Critical patent/EP1891324A1/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
    • F02M61/1806—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
    • 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
    • F02M61/1873—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
    • 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
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188

Definitions

  • a plurality of injection openings which are used for the direct fuel injection into the combustion chamber of an internal combustion engine
  • the fuel injection valves in this case control the injection of compressed and thus pressurized fuel by the longitudinal movement of a valve needle, which has a valve sealing surface and cooperates with a body seat.
  • a valve needle which has a valve sealing surface and cooperates with a body seat.
  • two basic types are distinguished: on the one hand so-called seat hole nozzles in which the injection openings emanate directly from a conical body seat, and on the other hand so-called blind hole nozzles in which the injection openings start from a blind hole.
  • the blind-hole nozzles have the advantage over the seat-hole nozzles that the distribution of the fuel to the individual injection openings takes place uniformly, as a result of which a more uniform spray pattern is generally achieved than with seat-hole nozzles.
  • the problem arises that the fuel which passes between the valve sealing surface and the body seat, is swirled when passing into the blind hole, so that the effective, applied to the injection openings injection pressure is reduced.
  • a fuel injection valve that works on the principle of the blind hole nozzle.
  • a needle tip is formed on the valve needle, which also in the open position of the valve needle, so if this from the Body seat has lifted, protrudes into the blind hole.
  • the needle tip has a conical sealing surface with which the valve needle is seated on the body seat. This sealing surface is adjoined by a convex, ie outwardly arched region, which in turn merges into a concave region, that is to say inwardly curved region.
  • the end of the valve needle then forms a dome, which is also curved outward and connects tangentially in the concave area.
  • the fuel flow should be deflected into the blind hole without detachment from the needle point in order to avoid turbulence.
  • this has the disadvantage that the shape of the needle tip can not be adapted equally well to all spray holes, since they usually include different angles with the longitudinal axis of the valve needle.
  • only at some of the holes results in an optimized inlet, while other injection openings are rather unfavorably flowed through the applied flow.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the inlet of the fuel into the blind hole and thus the effective injection pressure at the injection openings are optimized.
  • the valve needle on a conical valve sealing surface and an adjoining valve needle tip wherein the valve needle tip is concave directly adjacent to the conical valve sealing surface and adjoins the concave needle tip an outwardly curved dome or a flat end face.
  • the fuel flow dissolves when entering the blind hole of the valve needle, but is then redirected from the farther downstream part of the needle tip, so that the fuel leaves the injection openings at high speed and thus with a high effective injection pressure.
  • an edge is formed at the transition of the conical body seat to the blind hole, which, in combination with the configuration of the needle tip, ensures that the inlet of the fuel into the blind hole is further optimized.
  • This embodiment is particularly advantageous when the blind hole has a conical wall from which the injection openings emanate.
  • the needle tip extends so far into the blind hole that the concave needle tip, even when the valve needle is in its open position, reaches up to the height of the injection openings.
  • the concave needle tip is adjoined by a curved dome which forms the end of the valve needle. Depending on how far the valve needle protrudes into the blind hole, turbulence in the blind hole can be reduced.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section, with only the essential components are shown.
  • the fuel injection valve has a valve body 1, in which a bore 3 is formed with a longitudinal axis 8, wherein the bore 3 is delimited at its combustion chamber end by a body seat 9.
  • the body seat 9 is adjoined by a blind hole 10, from which at least one injection opening 7 originates, wherein a plurality of injection openings 7 are usually provided which are distributed over the circumference of the blind hole 10. It can also be provided that the individual injection openings 7 different inclination angle with respect to the Have bore 3.
  • a piston-shaped valve needle 5 is arranged, which is longitudinally displaceable and which is sealingly guided in a guide portion 15 in the bore 3.
  • valve needle 5 tapers the body seat 9 to form a pressure shoulder 13 and finally goes over into a valve sealing surface 11 at its body-side end.
  • the end of the valve needle 5 finally forms a needle tip 30, which then, when the valve needle 5 rests on the body seat 9, projects into the blind hole 10.
  • a pressure chamber 19 is formed which is radially expanded at the level of the pressure shoulder 13. In the radial extension of the pressure chamber 19 opens an extending in the valve body 1 inlet channel 25 through which the pressure chamber 19 can be filled with fuel under high pressure.
  • valve needle 5 is acted upon at its body seat facing away from the end of a closing force which points in the direction of the body seat 9 and which is generated for example by a spring element or by hydraulic means. Depending on the ratio of this closing force to the hydraulic opening force, which arises essentially by the pressurization of the pressure shoulder 13, the valve needle 5 moves longitudinally within the bore 3. If the valve needle 5 on the body seat 9, the blind hole 10 is opposite the pressure chamber 19 closed. If, however, an injection of fuel take place, the valve needle 5 is moved away either by an increase in pressure in the pressure chamber 19 or by a reduction in the closing force of the body seat 9. As a result, fuel flows between the valve sealing surface 11 and the body seat 9 into the blind hole 10, from where the fuel is ejected via the injection openings 7.
  • FIG. 2 shows an enlarged view of the designated II section of FIG. 1 in the region of the body seat 9.
  • the valve sealing surface 11 is conical, wherein it may also be provided to provide two or more conical surfaces with slightly different angles instead of a conical surface, wherein all opening angles of these conical surfaces, as well as the opening angle of the valve sealing surface 11, are substantially equal to the opening angle of the likewise conical body seat 9.
  • the conical valve sealing surface 11 is followed by a needle tip 30, which is also in the open position of the valve needle 5, the in of the FIG. 2 is shown in the blind hole 10 projects.
  • the needle tip 30 is concave directly following the valve sealing surface 11, ie curved inwards, so that an edge 34 is formed between the valve sealing surface 11 and the needle tip 30.
  • To the needle tip 30 can either, as in FIG. 2 shown, connect a flat face 32, or a dome 36, the in FIG. 2 is indicated by a dashed line. This depends on how far the needle tip 30 protrudes into the blind hole 10, so that a certain calming of the flow in the blind hole 10 can be achieved by the tip 36.
  • the effect described by the needle tip 30 can be further optimized by the fact that between the body seat 9 and the blind hole 10, an inlet edge 38 is formed on the to a certain extent also a detachment of the fuel flow from the wall of the valve body 1.
  • the inlet edge 38 is particularly formed when the wall of the blind hole 10 is conical, as well as in FIG. 2 shown.
  • the separation of the flow does not mean that the other areas in the blind hole 10 and the valve sealing surface 11 form dead water areas in which no flow takes place. Rather, the above description of the flow separation means that the main flow with the highest flow rates the described course, which is determined by this highest flow rate of the injection pressure substantially.
  • the needle tip 30 can also be provided to form the needle tip 30 so long that it extends to the height of the injection openings 7. Depending on the dimensions of the blind hole 10 and the injection pressure used, this can contribute to a better deflection of the fuel into the injection openings 7.

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

Description

Stand der TechnikState of the art

Bei Kraftstoffeinspritzventilen, die für die direkte Kraftstoffeinspritzung in den Brennraum einer Brennkraftmaschine verwendet werden, sind im allgemeinen mehrere Einspritzöffnungen, wenigstens aber eine Einspritzöffnung vorgesehen. Die Kraftstoffeinspritzventile steuern hierbei die Einspritzung von komprimierten und damit unter Druck stehendem Kraftstoff durch die Längsbewegung einer Ventilnadel, die eine Ventildichtfläche aufweist und mit einem Körpersitz zusammenwirkt. Hierbei unterscheidet man im wesentlichen zwei Grundtypen: Zum einen sogenannte Sitzlochdüsen, bei denen die Einspritzöffnungen direkt von einem konischen Körpersitz ausgehen, und zum anderen sogenannte Sacklochdüsen, bei denen die Einspritzöffnungen von einem Sackloch ausgehen. Die Sacklochdüsen weisen dabei gegenüber den Sitzlochdüsen den Vorteil auf, dass die Verteilung des Kraftstoffs auf die einzelnen Einspritzöffnungen gleichmäßig geschieht, wodurch im allgemeinen ein gleichförmigeres Spritzbild als bei Sitzlochdüsen erreicht wird. Bei solchen Sacklochdüsen ergibt sich jedoch die Problematik, dass der Kraftstoff, der zwischen der Ventildichtfläche und dem Körpersitz hindurchtritt, beim Übertritt in das Sackloch verwirbelt wird, so dass der effektive, an den Einspritzöffnungen anliegende Einspritzdruck gemindert wird.In fuel injection valves, which are used for the direct fuel injection into the combustion chamber of an internal combustion engine, a plurality of injection openings, but at least one injection opening are generally provided. The fuel injection valves in this case control the injection of compressed and thus pressurized fuel by the longitudinal movement of a valve needle, which has a valve sealing surface and cooperates with a body seat. Essentially, two basic types are distinguished: on the one hand so-called seat hole nozzles in which the injection openings emanate directly from a conical body seat, and on the other hand so-called blind hole nozzles in which the injection openings start from a blind hole. In this case, the blind-hole nozzles have the advantage over the seat-hole nozzles that the distribution of the fuel to the individual injection openings takes place uniformly, as a result of which a more uniform spray pattern is generally achieved than with seat-hole nozzles. In such blind-hole nozzles, however, the problem arises that the fuel which passes between the valve sealing surface and the body seat, is swirled when passing into the blind hole, so that the effective, applied to the injection openings injection pressure is reduced.

Aus der DE 36 05 082 A1 sowie WO 01/18387 A1 ist ein Kraftstoffeinspritzventil bekannt, dass nach dem Prinzip der Sacklochdüse arbeitet. Hierbei ist an der Ventilnadel eine Nadelspitze ausgebildet, die auch in Öffnungsstellung der Ventilnadel, also wenn diese vom Körpersitz abgehoben hat, in das Sackloch hineinragt. Die Nadelspitze weist eine konische Dichtfläche auf, mit der die Ventilnadel auf dem Körpersitz aufsitzt. An diese Dichtfläche schließt sich ein konvexer, also nach außen gewölbter Bereich an, der wiederum in einen konkaven, also nach innen gewölbten Bereich übergeht. Das Ende der Ventilnadel bildet dann eine Kuppe, die ebenfalls nach außen gewölbt ist und sich tangential in den konkaven Bereich anschließt. Durch diese Form der Ventildichtfläche soll der Kraftstoffstrom ohne Ablösung von der Nadelspitze in das Sackloch eingelenkt werden, um Verwirbelungen zu vermeiden. Hierbei tritt jedoch der Nachteil auf, dass die Form der Nadelspitze nicht an alle Spritzlöcher gleich gut angepasst werden kann, da diese in der Regel unterschiedliche Winkel mit der Längsachse der Ventilnadel einschließen. Somit ergibt sich nur an einigen der Löcher ein optimierter Einlauf, während andere Einspritzöffnungen durch die anliegende Strömung eher ungünstig angeströmt werden.From the DE 36 05 082 A1 such as WO 01/18387 A1 a fuel injection valve is known that works on the principle of the blind hole nozzle. Here, a needle tip is formed on the valve needle, which also in the open position of the valve needle, so if this from the Body seat has lifted, protrudes into the blind hole. The needle tip has a conical sealing surface with which the valve needle is seated on the body seat. This sealing surface is adjoined by a convex, ie outwardly arched region, which in turn merges into a concave region, that is to say inwardly curved region. The end of the valve needle then forms a dome, which is also curved outward and connects tangentially in the concave area. Due to this shape of the valve sealing surface, the fuel flow should be deflected into the blind hole without detachment from the needle point in order to avoid turbulence. However, this has the disadvantage that the shape of the needle tip can not be adapted equally well to all spray holes, since they usually include different angles with the longitudinal axis of the valve needle. Thus, only at some of the holes results in an optimized inlet, while other injection openings are rather unfavorably flowed through the applied flow.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass der Einlauf des Kraftstoffs in das Sackloch und damit der effektive Einspritzdruck an den Einspritzöffnungen optimiert werden. Hierzu weist die Ventilnadel eine konische Ventildichtfläche und eine sich daran anschließende Ventilnadelspitze auf, wobei die Ventilnadelspitze direkt anschließend an die konische Ventildichtfläche konkav gewölbt ist und sich an die konkave Nadelspitze eine nach außen gewölbte Kuppe oder eine ebene Stirnfläche anschließt. Hierdurch löst sich die Kraftstoffströmung beim Einlauf in das Sackloch von der Ventilnadel ab, wird dann aber vom weiter stromabwärts liegenden Teil der Nadelspitze umgelenkt, so dass der Kraftstoff mit hoher Geschwindigkeit und damit mit einem hohen effektiven Einspritzdruck die Einspritzöffnungen verlässt.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the inlet of the fuel into the blind hole and thus the effective injection pressure at the injection openings are optimized. For this purpose, the valve needle on a conical valve sealing surface and an adjoining valve needle tip, wherein the valve needle tip is concave directly adjacent to the conical valve sealing surface and adjoins the concave needle tip an outwardly curved dome or a flat end face. As a result, the fuel flow dissolves when entering the blind hole of the valve needle, but is then redirected from the farther downstream part of the needle tip, so that the fuel leaves the injection openings at high speed and thus with a high effective injection pressure.

Durch die abhängigen Ansprüche sind vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung möglich. In einer ersten vorteilhaften Ausgestaltung ist am Übergang des konischen Körpersitzes zum Sackloch eine Kante ausgebildet, die in Kombination mit der Ausgestaltung der Nadelspitze dafür sorgt, dass der Einlauf des Kraftstoffs in das Sackloch weiter optimiert wird. Besonders vorteilhaft ist diese Ausgestaltung dann, wenn das Sackloch eine konische Wandung aufweist, von der die Einspritzöffnungen ausgehen.By the dependent claims advantageous embodiments of the subject invention are possible. In a first advantageous embodiment, an edge is formed at the transition of the conical body seat to the blind hole, which, in combination with the configuration of the needle tip, ensures that the inlet of the fuel into the blind hole is further optimized. This embodiment is particularly advantageous when the blind hole has a conical wall from which the injection openings emanate.

In einer weiteren vorteilhaften Ausgestaltung erstreckt sich die Nadelspitze soweit in das Sackloch, dass die konkave Nadelspitze auch dann, wenn die Ventilnadel in ihrer Öffnungsstellung ist, bis zur Höhe der Einspritzöffnungen reicht. Dadurch kann die Einlenkung weiter optimiert werden, wenn dies durch entsprechende Größen- und Druckverhältnisse im Sackloch angezeigt ist.In a further advantageous embodiment, the needle tip extends so far into the blind hole that the concave needle tip, even when the valve needle is in its open position, reaches up to the height of the injection openings. As a result, the deflection can be further optimized if this is indicated by appropriate size and pressure conditions in the blind hole.

In einer weiteren vorteilhaften Ausgestaltung schließt sich an die konkave Nadelspitze eine gewölbte Kuppe an, die den Abschluss der Ventilnadel bildet. Je nachdem, wie weit die Ventilnadel in das Sackloch hineinragt, können dadurch Turbulenzen im Sackloch gemindert werden.In a further advantageous embodiment, the concave needle tip is adjoined by a curved dome which forms the end of the valve needle. Depending on how far the valve needle protrudes into the blind hole, turbulence in the blind hole can be reduced.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be taken from the description and the drawing.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt

Figur 1
ein Kraftstoffeinspritzventil im Längsschnitt mit seinen wesentlichen Komponenten und
Figur 2
eine vergrößerte Darstellung des mit II bezeichneten Ausschnitts der Figur 1 im Bereich des Körpersitzes.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a fuel injection valve in longitudinal section with its essential components and
FIG. 2
an enlarged view of the designated II section of the FIG. 1 in the area of the body seat.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In der Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt, wobei nur die wesentlichen Komponenten gezeigt sind. Das Kraftstoffeinspritzventil weist einen Ventilkörper 1 auf, in dem eine Bohrung 3 mit einer Längsachse 8 ausgebildet ist, wobei die Bohrung 3 an ihrem brennraumseitigen Ende von einem Körpersitz 9 begrenzt wird. An den Körpersitz 9 schließt sich ein Sackloch 10 an, von dem wenigstens eine Einspritzöffnung 7 ausgeht, wobei meist mehrere Einspritzöffnungen 7 vorgesehen sind, die über den Umfang des Sacklochs 10 verteilt angeordnet sind. Hierbei kann es auch vorgesehen sein, dass die einzelnen Einspritzöffnungen 7 unterschiedliche Neigungswinkel bezüglich der Bohrung 3 aufweisen. In der Bohrung 3 ist ein kolbenförmige Ventilnadel 5 angeordnet, die längsverschiebbar ist und die in einem Führungsabschnitt 15 in der Bohrung 3 dichtend geführt ist. Ausgehend vom Führungsabschnitt 15 verjüngt sich die Ventilnadel 5 dem Körpersitz 9 zu unter Bildung einer Druckschulter 13 und geht an ihrem körpersitzseitigen Ende schließlich in eine Ventildichtfläche 11 über. Das Ende der Ventilnadel 5 bildet schließlich eine Nadelspitze 30, die dann, wenn die Ventilnadel 5 auf dem Körpersitz 9 aufliegt, in das Sackloch 10 hineinragt. Zwischen der Wand der Bohrung 3 und der Ventilnadel 5 ist ein Druckraum 19 ausgebildet, der auf Höhe der Druckschulter 13 radial erweitert ist. In die radiale Erweiterung des Druckraums 19 mündet ein im Ventilkörper 1 verlaufender Zulaufkanal 25, über den der Druckraum 19 mit Kraftstoff unter hohem Druck befüllt werden kann.In the FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section, with only the essential components are shown. The fuel injection valve has a valve body 1, in which a bore 3 is formed with a longitudinal axis 8, wherein the bore 3 is delimited at its combustion chamber end by a body seat 9. The body seat 9 is adjoined by a blind hole 10, from which at least one injection opening 7 originates, wherein a plurality of injection openings 7 are usually provided which are distributed over the circumference of the blind hole 10. It can also be provided that the individual injection openings 7 different inclination angle with respect to the Have bore 3. In the bore 3, a piston-shaped valve needle 5 is arranged, which is longitudinally displaceable and which is sealingly guided in a guide portion 15 in the bore 3. Starting from the guide section 15, the valve needle 5 tapers the body seat 9 to form a pressure shoulder 13 and finally goes over into a valve sealing surface 11 at its body-side end. The end of the valve needle 5 finally forms a needle tip 30, which then, when the valve needle 5 rests on the body seat 9, projects into the blind hole 10. Between the wall of the bore 3 and the valve needle 5, a pressure chamber 19 is formed which is radially expanded at the level of the pressure shoulder 13. In the radial extension of the pressure chamber 19 opens an extending in the valve body 1 inlet channel 25 through which the pressure chamber 19 can be filled with fuel under high pressure.

Die Ventilnadel 5 wird an ihrem körpersitzabgewandten Ende von einer Schließkraft beaufschlagt, die in Richtung des Körpersitzes 9 weist und die beispielsweise durch ein Federelement oder mit hydraulischen Mitteln erzeugt wird. Je nach Verhältnis dieser Schließkraft zur hydraulischen Öffnungskraft, die im wesentlichen durch die Druckbeaufschlagung der Druckschulter 13 entsteht, bewegt sich die Ventilnadel 5 in Längsrichtung innerhalb der Bohrung 3. Liegt die Ventilnadel 5 auf dem Körpersitz 9 auf, so wird das Sackloch 10 gegenüber dem Druckraum 19 verschlossen. Soll hingegen eine Einspritzung von Kraftstoff stattfinden, so wird die Ventilnadel 5 entweder durch eine Druckerhöhung im Druckraum 19 oder durch eine Minderung der Schließkraft vom Körpersitz 9 wegbewegt. Dadurch fließt Kraftstoff zwischen der Ventildichtfläche 11 und dem Körpersitz 9 hindurch in das Sackloch 10, von wo der Kraftstoff über die Einspritzöffnungen 7 ausgespritzt wird.The valve needle 5 is acted upon at its body seat facing away from the end of a closing force which points in the direction of the body seat 9 and which is generated for example by a spring element or by hydraulic means. Depending on the ratio of this closing force to the hydraulic opening force, which arises essentially by the pressurization of the pressure shoulder 13, the valve needle 5 moves longitudinally within the bore 3. If the valve needle 5 on the body seat 9, the blind hole 10 is opposite the pressure chamber 19 closed. If, however, an injection of fuel take place, the valve needle 5 is moved away either by an increase in pressure in the pressure chamber 19 or by a reduction in the closing force of the body seat 9. As a result, fuel flows between the valve sealing surface 11 and the body seat 9 into the blind hole 10, from where the fuel is ejected via the injection openings 7.

Figur 2 zeigt eine vergrößerte Darstellung des mit II bezeichneten Ausschnitts von Figur 1 im Bereich des Körpersitzes 9. Die Ventildichtfläche 11 ist konisch ausgebildet, wobei es auch vorgesehen sein kann, statt einer konischen Fläche zwei oder mehr konische Flächen mit leicht unterschiedlichen Winkeln vorzusehen, wobei sämtliche Öffnungswinkel dieser konischen Flächen, ebenso wie der Öffnungswinkel der Ventildichtfläche 11, im wesentlichen gleich dem Öffnungswinkel des ebenfalls konischen Körpersitzes 9 sind. An die konische Ventildichtfläche 11 schließt sich eine Nadelspitze 30 an, die auch in Öffnungsstellung der Ventilnadel 5, die in der Figur 2 dargestellt ist, in das Sackloch 10 ragt. Die Nadelspitze 30 ist direkt anschließend an die Ventildichtfläche 11 konkav, also nach innen gewölbt, so dass zwischen der Ventildichtfläche 11 und der Nadelspitze 30 eine Kante 34 gebildet wird. An die Nadelspitze 30 kann sich entweder, wie in Figur 2 dargestellt, eine ebene Stirnfläche 32 anschließen, oder eine Kuppe 36, die in Figur 2 mit einer gestrichelten Linie angedeutet ist. Dies hängt davon ab, wie weit die Nadelspitze 30 in das Sackloch 10 hineinragt, so dass durch die Kuppe 36 eine gewisse Beruhigung der Strömung im Sackloch 10 erreicht werden kann. FIG. 2 shows an enlarged view of the designated II section of FIG. 1 in the region of the body seat 9. The valve sealing surface 11 is conical, wherein it may also be provided to provide two or more conical surfaces with slightly different angles instead of a conical surface, wherein all opening angles of these conical surfaces, as well as the opening angle of the valve sealing surface 11, are substantially equal to the opening angle of the likewise conical body seat 9. The conical valve sealing surface 11 is followed by a needle tip 30, which is also in the open position of the valve needle 5, the in of the FIG. 2 is shown in the blind hole 10 projects. The needle tip 30 is concave directly following the valve sealing surface 11, ie curved inwards, so that an edge 34 is formed between the valve sealing surface 11 and the needle tip 30. To the needle tip 30 can either, as in FIG. 2 shown, connect a flat face 32, or a dome 36, the in FIG. 2 is indicated by a dashed line. This depends on how far the needle tip 30 protrudes into the blind hole 10, so that a certain calming of the flow in the blind hole 10 can be achieved by the tip 36.

Fließt Kraftstoff bei einer Einspritzung aus dem Druckraum 19 zwischen der Ventildichtfläche 11 und dem Körpersitz 9 hindurch in das Sackloch 10, so beschleunigt sich die Strömung auf ihrem Weg in das Sackloch 10, da sich der zur Verfügung stehende Strömungsquerschnitt kontinuierlich verringert. Der Kraftstoff fließt dabei an der Kante 34 vorbei, wobei sich die Strömung hier durch die konkave Formung der Nadelspitze an der Kante 34 von der Ventilnadel 5 löst. Dies ist in Figur 2 durch kleine Pfeile angedeutet. Der Kraftstoffstrom trifft dann innerhalb des Sacklochs 10 wieder auf die Nadelspitze 30 und wird durch diese effektiv in Richtung der Einspritzöffnungen 7 umgelenkt. Hierdurch wird der Energieverlust bei der Umlenkung minimiert, was einen höheren effektiven Einspritzdruck ergibt, der letztendlich innerhalb der Einspritzöffnung 7 zur Verfügung steht. Darüber hinaus wird die Strömung innerhalb des Sacklochs 10 beruhigt, was eine weitere Erhöhung des effektiven Einspritzdrucks bewirkt.If fuel flows during an injection from the pressure chamber 19 between the valve sealing surface 11 and the body seat 9 into the blind hole 10, the flow accelerates on its way into the blind hole 10, since the available flow cross section is reduced continuously. The fuel flows past the edge 34, wherein the flow is released here by the concave shaping of the needle tip at the edge 34 of the valve needle 5. This is in FIG. 2 indicated by small arrows. The fuel flow then hits within the blind hole 10 again on the needle tip 30 and is effectively deflected by this in the direction of the injection openings 7. As a result, the energy loss is minimized during the deflection, resulting in a higher effective injection pressure, which is ultimately available within the injection port 7. In addition, the flow within the blind hole 10 is calmed, causing a further increase in the effective injection pressure.

Der beschriebene Effekt durch die Nadelspitze 30 kann noch dadurch optimiert werden, dass zwischen dem Körpersitz 9 und dem Sackloch 10 eine Einlaufkante 38 ausgebildet ist, an der in gewissem Umfang ebenfalls eine Ablösung des Kraft-stoffstroms von der Wand des Ventilkörpers 1 geschieht. Die Einlaufkante 38 ist besonders dann ausgebildet, wenn die Wandung des Sacklochs 10 konisch ausgebildet ist, wie auch in Figur 2 dargestellt.The effect described by the needle tip 30 can be further optimized by the fact that between the body seat 9 and the blind hole 10, an inlet edge 38 is formed on the to a certain extent also a detachment of the fuel flow from the wall of the valve body 1. The inlet edge 38 is particularly formed when the wall of the blind hole 10 is conical, as well as in FIG. 2 shown.

Die Ablösung der Strömung bedeutet nicht, dass die sonstigen Bereiche im Sackloch 10 und an der Ventildichtfläche 11 Totwasserbereiche bilden, in denen keine Strömung stattfindet. Die obige Beschreibung der Strömungsablösung bedeutet vielmehr, dass die Hauptströmung mit den höchsten Fließgeschwindigkeiten den beschriebenen Verlauf nimmt, wobei durch diese höchste Fließgeschwindigkeit der Einspritzdruck im wesentlichen bestimmt wird.The separation of the flow does not mean that the other areas in the blind hole 10 and the valve sealing surface 11 form dead water areas in which no flow takes place. Rather, the above description of the flow separation means that the main flow with the highest flow rates the described course, which is determined by this highest flow rate of the injection pressure substantially.

Es kann auch vorgesehen sein, die Nadelspitze 30 so lang auszubilden, dass sich diese bis zur Höhe der Einspritzöffnungen 7 erstreckt. Je nach den Abmessungen des Sacklochs 10 und des verwendeten Einspritzdrucks kann dies zu einer besseren Einlenkung des Kraftstoffs in die Einspritzöffnungen 7 beitragen.It can also be provided to form the needle tip 30 so long that it extends to the height of the injection openings 7. Depending on the dimensions of the blind hole 10 and the injection pressure used, this can contribute to a better deflection of the fuel into the injection openings 7.

Claims (5)

  1. Fuel injection valve for internal combustion engines, having a valve body (1) in which there is formed a blind bore (10) from which at least one injection opening (7) extends, and having a valve needle (5) which is longitudinally displaceable in the valve body (1) and at whose end facing toward the blind bore (10) there is formed a valve sealing surface (11) by means of which the valve needle (5) interacts with a body seat (9) for the purposes of controlling a flow of fuel to the at least one injection opening (7), and having a needle tip (30) which adjoins the valve sealing surface (11) and which protrudes into the blind bore (10) when the valve needle (5) bears against the body seat (9), wherein the needle tip (30) is, adjacent to the valve sealing surface (11), of concavely curved form, characterized in that multiple injection openings (7) are formed which extend from the blind bore (10), and the concave needle tip (30) is adjoined by an outwardly curved dome (36) or a planar face surface (32).
  2. Fuel injection valve according to Claim 1, characterized in that, at the transition from the body seat (9) to the blind bore (10), there is formed an edge (38) which, when the valve needle (5) is lifted off the body seat (9), is situated at the level of the needle tip (30).
  3. Fuel injection valve according to Claim 1, characterized in that the opening stroke of the valve needle (5) is dimensioned such that, when the valve needle (5) is lifted off the body seat (9), the injection openings (7) are arranged at the level of the concave section of the needle tip (30).
  4. Fuel injection valve according to Claim 1, 2 or 3, characterized in that the blind bore (10) has a conical wall which directly adjoins the body seat (9).
  5. Fuel injection valve according to Claim 1, characterized in that the valve sealing surface (11) is formed from a conical surface or multiple conical surfaces.
EP06743259.1A 2005-06-01 2006-04-06 Fuel injection valve for internal combustion engines Active EP1891324B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005025135A DE102005025135A1 (en) 2005-06-01 2005-06-01 Fuel injection valve for internal combustion engines
PCT/EP2006/061400 WO2006128756A1 (en) 2005-06-01 2006-04-06 Fuel injection valve for internal combustion engines

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EP1891324A1 EP1891324A1 (en) 2008-02-27
EP1891324B1 true EP1891324B1 (en) 2017-06-14

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US (1) US8720802B2 (en)
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CN (1) CN101184916B (en)
DE (1) DE102005025135A1 (en)
WO (1) WO2006128756A1 (en)

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CN101184916A (en) 2008-05-21
US20080142621A1 (en) 2008-06-19
US8720802B2 (en) 2014-05-13
EP1891324A1 (en) 2008-02-27
CN101184916B (en) 2011-03-09
WO2006128756A1 (en) 2006-12-07
DE102005025135A1 (en) 2006-12-07

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