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EP1644636B2 - Fuel injection valve for combustion engines - Google Patents

Fuel injection valve for combustion engines Download PDF

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Publication number
EP1644636B2
EP1644636B2 EP04730825.9A EP04730825A EP1644636B2 EP 1644636 B2 EP1644636 B2 EP 1644636B2 EP 04730825 A EP04730825 A EP 04730825A EP 1644636 B2 EP1644636 B2 EP 1644636B2
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EP
European Patent Office
Prior art keywords
bulge
fuel injection
injection valve
basic shape
bulges
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04730825.9A
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German (de)
French (fr)
Other versions
EP1644636A1 (en
EP1644636B1 (en
Inventor
Heribert Duetsch
Guillermo Urzua
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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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
    • F02M61/184—Discharge orifices having non circular sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1846—Dimensional characteristics of discharge orifices

Definitions

  • the invention is based on a fuel injection valve, as it corresponds to the preamble of claim 1.
  • a fuel injection valve is for example from the document JP 11-117833 known and has a valve body in which a blind hole is formed.
  • a valve seat is formed, with which cooperates arranged in the blind bore valve needle.
  • at least one injection channel is formed, which connects the interior formed by the blind bore with the combustion chamber of the internal combustion engine and which has an inlet opening and an outlet opening. Through this injection channel, controlled by the valve needle, which cooperates with the valve seat, fuel injected from the blind bore into the combustion chamber of the internal combustion engine.
  • the injection channel is usually formed substantially cylindrical, in particular, the inlet opening can be modified. From the Scriptures JP 11-117833 However, other forms are known in which the injection channel has a star shape, cross shape, club shape or rectangular shape.
  • the cross-sectional shape of the injection channel affects the injection characteristic of the fuel injection valve and may - depending on the type of fuel injection valve - lead to an improvement of the combustion process. However, all of the shapes shown there have in common that they do not sufficiently take into account the inflow conditions from the valve seat into the injection channel.
  • the fuel flowing into the injection channel is forced into a flow profile, which is determined by the cross section of the injection channel, which does not correspond to the inflow profile of the fuel into the injection hole, thus resulting in pressure losses in the injection channel, the spray of the fuel in the injection can affect the combustion chamber.
  • document DE 199 31 890 A discloses a fuel injection valve having an injection channel having an entrance opening with an elliptical basic shape.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the inlet cross-section of the injection channel is such that a low-loss introduction of the fuel from the blind bore in the injection channel is possible, what the feasible injection pressure and the atomization of the fuel Injection process influenced positively.
  • the inlet openings seen in cross-section a circular basic shape with a radius, wherein over a first angular range of the circumference of the circular basic shape, a first protrusion is formed, whose angular range is less than 180 °.
  • a second bulge is provided in the circular basic shape, which is formed mirror-symmetrically to the first bulge, wherein the mirror plane passes through the center of the circular basic shape.
  • Both lobes are arranged to each other so that the two connecting lines of the farthest points of the recesses with the center enclose an angle with the mirror plane of less than 180 °. Due to flow tests it has been shown that such recesses optimally support the inflow of the fuel and lead to a maximization of the speed and thus to an improvement of the injection conditions.
  • the injection channel can first be formed as a hole with a circular cross-section during production, into which the bulges are then introduced.
  • the bulges starting from the inlet opening to the outlet opening, decrease continuously such that the outlet opening advantageously corresponds at least approximately to a circular shape. This reduces the passage cross-section of the injection channel in its longitudinal extent, which leads to an acceleration of the fuel in the injection channel.
  • the bore reduces its circular cross-section from the inlet opening to the outlet opening, ie has a conical shape, which results in a further acceleration of the fuel flow.
  • the orientation of the mirror plane between the two bulges is oriented in an advantageous manner in a common plane with the longitudinal axis of the blind bore, so that with respect to the mirror plane symmetrical inflow of fuel into the injection channel takes place.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section.
  • a blind bore 3 is formed, which has a longitudinal axis 8 and at the bottom of a substantially conical valve seat 11 is formed.
  • the valve seat 11 is followed by a blind bore 9, from which several injection channels 7 go out.
  • the injection channels 7 open into the installation position of the fuel injection valve in the combustion chamber of the internal combustion engine.
  • a piston-shaped valve needle 5 is arranged longitudinally displaceable, which is guided in a guided portion 15 in the blind bore 3. Starting from the guided section 15, the valve needle 5 tapers to form a pressure shoulder 13 and merges at its valve seat-side end in a substantially conical valve sealing surface 17, which cooperates with the valve seat 11.
  • the blind bore 3 is radially expanded and thus forms a pressure chamber 19, which continues as an annular channel between the valve needle 5 and the blind bore 3 to the valve seat 11.
  • the pressure chamber 19 opens an extending in the valve body 1 inlet channel 25, via which the pressure chamber 19 can be filled with fuel.
  • the valve needle 5 is acted upon by a device, not shown, with a closing force in the direction of the valve seat 11 so that a longitudinal movement of the valve needle 5 in the blind bore 3 can be achieved via the interplay of the hydraulic forces on the pressure shoulder 13 and the closing force. If the valve needle 5 rests on the valve seat 11, the pressure chamber 19 is sealed. On the other hand, if the valve needle 5 is lifted off the valve seat, fuel flows from the pressure chamber 19 into the blind hole 9 and is injected from there through the injection channels 7 into the combustion chamber.
  • FIG. 2 shows an enlargement of FIG. 1 in the area of the blind hole, this area being in FIG. 1 marked with II.
  • the injection channels 7, which emanate from the blind hole, have a substantially cylindrical shape.
  • the inlet opening 20 of the injection channels 7 is arranged in the blind hole 9 and the outlet opening 22, from which the fuel exits and is injected into the combustion chamber, on the outer wall of the valve body 1.
  • the right edge of the FIG. 2 is shown, five sectional planes A, B, C, D and E are drawn, which are equidistant from each other, wherein the sectional plane A of the inlet opening 20 and the sectional plane E of the outlet opening 22 corresponds. These cutting planes will be discussed later.
  • FIG. 3 shows an enlarged view of the inner wall of the blind hole 9 with an injection channel 7.
  • the inlet opening 20 of the injection channel 7 is not circular, but has an optimized for the inlet of the fuel mold. Over the length of the injection channel 7, the shape of the cross section - starting from the inlet opening 20 - more and more approaches the circle, so that the outlet opening 22 is circular. In this way, the total cross section of the Einspitzkanals is reduced over the length, which accelerates the flow of the fuel in the injection channel 7.
  • FIG. 4 again shows the inlet opening 20 of an injection channel 7 in an enlarged view.
  • the inlet opening 20 has a circular basic shape 27 in cross section, which has a center point 28 and a radius R.
  • a first bulge 30 is formed, which has approximately a parabolic shape in the illustration shown here.
  • the bulge 30 has a point of greatest distance 130, the distance from the center point 28 in the FIG. 4 is denoted by A.
  • the angle range a 1 here is smaller than 180 °
  • the connecting line 35 which connects the point largest distance 130 with the center 28, includes with a mirror plane 33 an angle b, which is smaller than 180 °.
  • the mirror plane 33 in this case runs through the center 28 and is preferably arranged in the same plane as the longitudinal axis 8 of the blind bore 3.
  • the circular basic shape 27 has, over a second angular range a 2, a second bulge 39, which is mirror-symmetrical to the first bulge 30 with respect to the mirror plane 33.
  • the second bulge 31 has a point greatest distance 131, the connecting line with the center 28 with the mirror plane 33 also includes the angle b.
  • the bulges 30, 31 extend as channel-like recesses on the wall of the injection channel 7 symmetrically on both sides.
  • the depth of the bulges 30, 31 may change or remain constant over the entire length of the injection channel 7.
  • FIGS. 5A to 5E are cross sections through an embodiment of an injection channel 7, wherein the cross sections in their position the planes A, B, C, D and E of FIG. 2 correspond.
  • FIG. 5A which represents the shape of the injection channel 7 in the sectional plane A, so the inlet opening 20, the bulges 30, 31 are still clearly pronounced.
  • FIG. 5B and FIG. 5C these bulges 30, 31 are already significantly reduced, and in the sectional plane D and E, in the Figures 5D and 5E are shown, the bulges 30, 31 are gone.
  • the inlet opening 20 of the injection channel 7 is oriented in the embodiment described above so that the bulges 30, 31 point in the direction of the open end of the blind bore 3.
  • the inlet opening 20 is arranged rotated by 180 ° about the center 28, so that the bulges 30, 31 form channel-like recesses on the side of the injection channel 7, which is directed away from the valve needle 5.
  • this orientation of the bulges 30, 31 can lead to Einström opposition in the injection channel 7, which are advantageous and lead to improved spray formation and combustion.
  • the diameter of the basic shape of the inlet opening 20 to the outlet opening 22 is continuously reduced, so that, for example, results in a tapered basic shape whose walls the bulges 30, 31 are provided.

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

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil aus, wie es dem Oberbegriff des Anspruchs 1 entspricht. Ein solches Kraftstoffeinspritzventil ist beispielsweise aus der Schrift JP 11-117833 bekannt und weist einen Ventilkörper auf, in dem eine Sackbohrung ausgebildet ist. Am Grund der Sackbohrung ist ein Ventilsitz ausgebildet, mit dem eine in der Sackbohrung angeordnete Ventilnadel zusammenwirkt. Am Grund der Sackbohrung ist darüber hinaus wenigstens ein Einspritzkanal ausgebildet, der den durch die Sackbohrung gebildeten Innenraum mit dem Brennraum der Brennkraftmaschine verbindet und der eine Eintrittsöffnung und eine Austrittsöffnung aufweist. Durch diesen Einspritzkanal wird, gesteuert durch die Ventilnadel, die mit dem Ventilsitz zusammenwirkt, Kraftstoff aus der Sackbohrung in den Brennraum der Brennkraftmaschine eingespritzt.The invention is based on a fuel injection valve, as it corresponds to the preamble of claim 1. Such a fuel injection valve is for example from the document JP 11-117833 known and has a valve body in which a blind hole is formed. At the bottom of the blind bore, a valve seat is formed, with which cooperates arranged in the blind bore valve needle. At the bottom of the blind bore, moreover, at least one injection channel is formed, which connects the interior formed by the blind bore with the combustion chamber of the internal combustion engine and which has an inlet opening and an outlet opening. Through this injection channel, controlled by the valve needle, which cooperates with the valve seat, fuel injected from the blind bore into the combustion chamber of the internal combustion engine.

Der Einspritzkanal ist meist im wesentlichen zylindrisch ausgebildet, wobei insbesondere die Eintrittsöffnung modifiziert werden kann. Aus der Schrift JP 11-117833 sind aber auch andere Formen bekannt, bei denen der Einspritzkanal eine Sternform, Kreuzform, Keulenform oder Rechteckform aufweist. Die Querschnittsform des Einspritzkanals wirkt sich auf die Einspritzcharakteristik des Kraftstoffeinspritzventils aus und kann - je nach Typ des Kraftstoffeinspritzventils - zu einer Verbesserung des Verbrennungsvorgangs führen. Allen dort gezeigten Formen ist jedoch gemein, dass sie die Einströmverhältnisse vom Ventilsitz in den Einspritzkanal hinein nicht ausreichend berücksichtigen. Der in den Einspritzkanal einströmende Kraftstoff wird in ein Strömungsprofil, das durch den Querschnitt des Einspritzkanals bestimmt wird, gezwungen, das nicht dem Einströmungsprofil des Kraftstoffs in das Spritzloch entspricht, so dass folglich Druckverluste im Einspritzkanal auftreten, die die Spraybildung des Kraftstoffs bei der Einspritzung in den Brennraum beeinträchtigen können.The injection channel is usually formed substantially cylindrical, in particular, the inlet opening can be modified. From the Scriptures JP 11-117833 However, other forms are known in which the injection channel has a star shape, cross shape, club shape or rectangular shape. The cross-sectional shape of the injection channel affects the injection characteristic of the fuel injection valve and may - depending on the type of fuel injection valve - lead to an improvement of the combustion process. However, all of the shapes shown there have in common that they do not sufficiently take into account the inflow conditions from the valve seat into the injection channel. The fuel flowing into the injection channel is forced into a flow profile, which is determined by the cross section of the injection channel, which does not correspond to the inflow profile of the fuel into the injection hole, thus resulting in pressure losses in the injection channel, the spray of the fuel in the injection can affect the combustion chamber.

Dokument DE 199 31 890 A offenbart ein Kraftstoffeinspritzventil mit einem Einspritzkanal, der eine Eintrittsöffnung mit einer elliptischen Grundform aufweist.document DE 199 31 890 A discloses a fuel injection valve having an injection channel having an entrance opening with an elliptical basic shape.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass der Eintrittsquerschnitt des Einspritzkanals so beschaffen ist, dass ein verlustarmes Einleiten des Kraftstoffs aus der Sackbohrung in den Einspritzkanal möglich ist, was den umsetzbaren Einspritzdruck und die Zerstäubung des Kraftstoffs beim Einspritzvorgang positiv beeinflusst. Hierzu weist die Eintrittsöffnungen im Querschnitt gesehen eine kreisrunde Grundform mit einem Radius auf, wobei über einem ersten Winkelbereich des Umfangs der kreisförmigen Grundform eine erste Ausbuchtung gebildet ist, deren Winkelbereich weniger als 180° beträgt. Darüber hinaus ist in der kreisrunden Grundform eine zweite Ausbuchtung vorgesehen, die spiegelsymmetrisch zur ersten Ausbuchtung ausgebildet ist, wobei die Spiegelebene durch den Mittelpunkt der kreisrunden Grundform geht. Beide Ausbuchtungen sind so zueinander angeordnet, dass die beiden Verbindungslinien der fernsten Punkte der Ausnehmungen mit dem Mittelpunkt einen Winkel mit der Spiegelebene von weniger als 180° einschließen. Aufgrund von Strömungsversuchen konnte gezeigt werden, dass derartige Ausnehmungen die Einströmungen des Kraftstoffs optimal unterstützen und zu einer Maximierung der Geschwindigkeit und damit zu einer Verbesserung der Einspritzbedingungen führen.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the inlet cross-section of the injection channel is such that a low-loss introduction of the fuel from the blind bore in the injection channel is possible, what the feasible injection pressure and the atomization of the fuel Injection process influenced positively. For this purpose, the inlet openings seen in cross-section a circular basic shape with a radius, wherein over a first angular range of the circumference of the circular basic shape, a first protrusion is formed, whose angular range is less than 180 °. In addition, a second bulge is provided in the circular basic shape, which is formed mirror-symmetrically to the first bulge, wherein the mirror plane passes through the center of the circular basic shape. Both lobes are arranged to each other so that the two connecting lines of the farthest points of the recesses with the center enclose an angle with the mirror plane of less than 180 °. Due to flow tests it has been shown that such recesses optimally support the inflow of the fuel and lead to a maximization of the speed and thus to an improvement of the injection conditions.

Durch die Ausgestaltung der Eintrittsöffnung als Kreisform außerhalb der ersten und zweiten Ausbuchtung lässt sich bei der Fertigung der Einspritzkanal zuerst als Bohrung mit kreisrundem Querschnitt ausbilden, in die anschließend die Ausbuchtungen eingebracht werden. Erfindungsgemäß verkleinern sich die Ausbuchtungen ausgehend von der Eintritsöffnung zur Austrittsöffnung stetig so dass die Austrittsöffnung vorteilhafterweise zumindest näherungsweise einer Kreisform entspricht. Dadurch vermindert sich der Durchgangsquerschnitt des Einspritzkanals in seiner Längserstreckung, was zu einer Beschleunigung des Kraftstoffs im Einspritzkanal führt. Zusätzlich kann es vorgesehen sein, dass die Bohrung ihren kreisrunden Querschnitt von der Eintrittsöffnung zur Austrittsöffnung vermindert, also eine konische Form aufweist, was eine weitere Beschleunigung des Kraftstoffstroms ergibt.Due to the design of the inlet opening as a circular shape outside the first and second bulge, the injection channel can first be formed as a hole with a circular cross-section during production, into which the bulges are then introduced. According to the invention, the bulges, starting from the inlet opening to the outlet opening, decrease continuously such that the outlet opening advantageously corresponds at least approximately to a circular shape. This reduces the passage cross-section of the injection channel in its longitudinal extent, which leads to an acceleration of the fuel in the injection channel. In addition, it can be provided that the bore reduces its circular cross-section from the inlet opening to the outlet opening, ie has a conical shape, which results in a further acceleration of the fuel flow.

Die Orientierung der Spiegelebene zwischen den beiden Ausbuchtungen ist in vorteilhafter Weise in einer gemeinsamen Ebene mit der Längsachse der Sackbohrung orientiert, so dass bezüglich der Spiegelebene ein symmetrisches Einströmen eines Kraftstoffs in den Einspritzkanal erfolgt.The orientation of the mirror plane between the two bulges is oriented in an advantageous manner in a common plane with the longitudinal axis of the blind bore, so that with respect to the mirror plane symmetrical inflow of fuel into the injection channel takes place.

Zeichnungdrawing

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

Figur 1
einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
Figur 2
eine Vergrößerung von Figur 1 im Bereich des Sacklochs,
Figur 3
eine vergrößerte Darstellung der Innenwand des Sacklochs mit einem Einspritzkanal,
Figur 4
die Eintrittsöffnung des Einspritzkanals und
Figur 5A bis Figur 5E
zeigen jeweils Querschnitte durch den Einspritzkanal in äquidistanten Abständen, wie sie in Figur 2 eingezeichnet sind.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a longitudinal section through a fuel injection valve according to the invention,
FIG. 2
an enlargement of FIG. 1 in the area of the blind hole,
FIG. 3
an enlarged view of the inner wall of the blind hole with an injection channel,
FIG. 4
the inlet opening of the injection channel and
Figure 5A to Figure 5E
each show cross sections through the injection channel at equidistant intervals, as in FIG. 2 are drawn.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt. In einem Ventilkörper 1 ist eine Sackbohrung 3 ausgebildet, die eine Längsachse 8 aufweist und an deren Grund ein im wesentlichen konischer Ventilsitz 11 ausgebildet ist. An den Ventilsitz 11 schließt sich eine Sackbohrung 9 an, von der mehrere Einspritzkanäle 7 ausgehen. Die Einspritzkanäle 7 münden in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraftmaschine. In der Sackbohrung 3 ist eine kolbenförmige Ventilnadel 5 längsverschiebbar angeordnet, die in einem geführten Abschnitt 15 in der Sackbohrung 3 geführt ist. Ausgehend vom geführten Abschnitt 15 verjüngt sich die Ventilnadel 5 unter Bildung einer Druckschulter 13 und geht an ihrem ventilsitzseitigen Ende in eine im wesentlichen konische Ventildichtfläche 17 über, die mit dem Ventilsitz 11 zusammenwirkt. Auf Höhe der Druckschulter 13 ist die Sackbohrung 3 radial erweitert und bildet so einen Druckraum 19, der sich als Ringkanal zwischen der Ventilnadel 5 und der Sackbohrung 3 bis zum Ventilsitz 11 fortsetzt. In die radiale Erweiterung des Druckraums 19 mündet ein im Ventilkörper 1 verlaufender Zulaufkanal 25, über den der Druckraum 19 mit Kraftstoff befüllt werden kann. Die Ventilnadel 5 wird von einer nicht dargestellten Vorrichtung mit einer Schließkraft in Richtung des Ventilsitzes 11 beaufschlagt, so dass sich über das Zusammenspiel der hydraulischen Kräfte auf die Druckschulter 13 und der Schließkraft eine Längsbewegung der Ventilnadel 5 in der Sackbohrung 3 erreichen lässt. Liegt die Ventilnadel 5 auf dem Ventilsitz 11 auf, so wird der Druckraum 19 abgedichtet. Hebt die Ventilnadel 5 hingegen vom Ventilsitz ab, so strömt Kraftstoff aus dem Druckraum 19 in das Sackloch 9 und wird von dort durch die Einspritzkanäle 7 in den Brennraum eingespritzt.In FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section. In a valve body 1, a blind bore 3 is formed, which has a longitudinal axis 8 and at the bottom of a substantially conical valve seat 11 is formed. The valve seat 11 is followed by a blind bore 9, from which several injection channels 7 go out. The injection channels 7 open into the installation position of the fuel injection valve in the combustion chamber of the internal combustion engine. In the blind bore 3, a piston-shaped valve needle 5 is arranged longitudinally displaceable, which is guided in a guided portion 15 in the blind bore 3. Starting from the guided section 15, the valve needle 5 tapers to form a pressure shoulder 13 and merges at its valve seat-side end in a substantially conical valve sealing surface 17, which cooperates with the valve seat 11. At the level of the pressure shoulder 13, the blind bore 3 is radially expanded and thus forms a pressure chamber 19, which continues as an annular channel between the valve needle 5 and the blind bore 3 to the valve seat 11. In the radial extension of the pressure chamber 19 opens an extending in the valve body 1 inlet channel 25, via which the pressure chamber 19 can be filled with fuel. The valve needle 5 is acted upon by a device, not shown, with a closing force in the direction of the valve seat 11 so that a longitudinal movement of the valve needle 5 in the blind bore 3 can be achieved via the interplay of the hydraulic forces on the pressure shoulder 13 and the closing force. If the valve needle 5 rests on the valve seat 11, the pressure chamber 19 is sealed. On the other hand, if the valve needle 5 is lifted off the valve seat, fuel flows from the pressure chamber 19 into the blind hole 9 and is injected from there through the injection channels 7 into the combustion chamber.

Figur 2 zeigt eine Vergrößerung von Figur 1 im Bereich des Sacklochs, wobei dieser Bereich in Figur 1 mit II gekennzeichnet ist. Die Einspritzkanäle 7, die vom Sackloch ausgehen, weisen eine im wesentlichen zylindrische Form auf. Die Eintrittsöffnung 20 der Einspritzkanäle 7 ist im Sackloch 9 angeordnet und die Austrittsöffnung 22, aus der der Kraftstoff austritt und in den Brennraum eingespritzt wird, an der Außenwand des Ventilkörpers 1. Für den Einspritzkanal 7, der am rechten Rand der Figur 2 dargestellt ist, sind fünf Schnittebenen A, B, C, D und E eingezeichnet, die äquidistant zueinander sind, wobei die Schnittebene A der Eintrittsöffnung 20 und die Schnittebene E der Austrittsöffnung 22 entspricht. Auf diese Schnittebenen wird später noch näher eingegangen. FIG. 2 shows an enlargement of FIG. 1 in the area of the blind hole, this area being in FIG. 1 marked with II. The injection channels 7, which emanate from the blind hole, have a substantially cylindrical shape. The inlet opening 20 of the injection channels 7 is arranged in the blind hole 9 and the outlet opening 22, from which the fuel exits and is injected into the combustion chamber, on the outer wall of the valve body 1. For the injection channel 7, the right edge of the FIG. 2 is shown, five sectional planes A, B, C, D and E are drawn, which are equidistant from each other, wherein the sectional plane A of the inlet opening 20 and the sectional plane E of the outlet opening 22 corresponds. These cutting planes will be discussed later.

Figur 3 zeigt eine vergrößerte Darstellung der Innenwand des Sacklochs 9 mit einem Einspritzkanal 7. Die Eintrittsöffnung 20 des Einspritzkanals 7 ist nicht kreisrund ausgebildet, sondern weist eine für den Einlauf des Kraftstoffs optimierte Form auf. Über die Länge des Einspritzkanals 7 nähert sich die Form des Querschnitts - ausgehend von der Eintrittsöffnung 20 - immer mehr dem Kreis an, so dass die Austrittsöffnung 22 kreisrund ist. Auf diese Weise wird der Gesamtquerschnitt des Einspitzkanals über die Länge verringert, was die Strömung des Kraftstoffs im Einspritzkanal 7 beschleunigt. FIG. 3 shows an enlarged view of the inner wall of the blind hole 9 with an injection channel 7. The inlet opening 20 of the injection channel 7 is not circular, but has an optimized for the inlet of the fuel mold. Over the length of the injection channel 7, the shape of the cross section - starting from the inlet opening 20 - more and more approaches the circle, so that the outlet opening 22 is circular. In this way, the total cross section of the Einspitzkanals is reduced over the length, which accelerates the flow of the fuel in the injection channel 7.

Figur 4 zeigt nochmals die Eintrittsöffnung 20 eines Einspritzkanals 7 in vergrößerter Darstellung. Die Eintrittsöffnung 20 weist im Querschnitt eine kreisrunde Grundform 27 auf, die einen Mittelpunkt 28 und einen Radius R aufweist. Über einen ersten Winkelbereich a1 der kreisförmigen Grundform 27 ist eine erste Ausbuchtung 30 ausgebildet, die in der hier gezeigten Darstellung näherungsweise eine Parabelform aufweist. Die Ausbuchtung 30 weist einen Punkt größten Abstands 130 auf, dessen Abstand vom Mittelpunkt 28 in der Figur 4 mit A bezeichnet ist. Der Winkelbereich a1 ist hierbei kleiner als 180°, und die Verbindungslinie 35, die den Punkt größten Abstand 130 mit dem Mittelpunkt 28 verbindet, schließt mit einer Spiegelebene 33 einen Winkel b ein, der kleiner als 180° ist. Die Spiegelebene 33 verläuft hierbei durch den Mittelpunkt 28 und ist vorzugsweise in derselben Ebene wie die Längsachse 8 der Sackbohrung 3 angeordnet. Die kreisrunde Grundform 27 weist über einem zweiten Winkelbereich a2 eine zweite Ausbuchtung 39 auf, die bezüglich der Spiegelebene 33 spiegelsymmetrisch zur ersten Ausbuchtung 30 ausgebildet ist. Auch die zweite Ausbuchtung 31 weist einen Punkt größten Abstand 131 auf, dessen Verbindungslinie mit dem Mittelpunkt 28 mit der Spiegelebene 33 ebenfalls den Winkel b einschließt. FIG. 4 again shows the inlet opening 20 of an injection channel 7 in an enlarged view. The inlet opening 20 has a circular basic shape 27 in cross section, which has a center point 28 and a radius R. Over a first angular range a 1 of the circular basic shape 27, a first bulge 30 is formed, which has approximately a parabolic shape in the illustration shown here. The bulge 30 has a point of greatest distance 130, the distance from the center point 28 in the FIG. 4 is denoted by A. The angle range a 1 here is smaller than 180 °, and the connecting line 35, which connects the point largest distance 130 with the center 28, includes with a mirror plane 33 an angle b, which is smaller than 180 °. The mirror plane 33 in this case runs through the center 28 and is preferably arranged in the same plane as the longitudinal axis 8 of the blind bore 3. The circular basic shape 27 has, over a second angular range a 2, a second bulge 39, which is mirror-symmetrical to the first bulge 30 with respect to the mirror plane 33. Also, the second bulge 31 has a point greatest distance 131, the connecting line with the center 28 with the mirror plane 33 also includes the angle b.

Die Ausbuchtungen 30, 31 verlaufen als kanalartige Ausnehmungen an der Wand des Einspritzkanals 7 symmetrisch auf beiden Seiten. Hierbei kann sich die Tiefe der Ausbuchtungen 30, 31 ändern oder auch über die gesamte Länge des Einspritzkanals 7 konstant bleiben. Es hat sich aber als vorteilhaft erwiesen, wenn sich die Tiefe der Ausbuchtungen 30, 31 über die Länge des Einspritzkanals 7 verkleinert, also der Abstand A der Punkte größten Abstands 130 bzw. 131 zum Mittelpunkt 28 kleiner werden.The bulges 30, 31 extend as channel-like recesses on the wall of the injection channel 7 symmetrically on both sides. Here, the depth of the bulges 30, 31 may change or remain constant over the entire length of the injection channel 7. However, it has proven to be advantageous if the depth of the bulges 30, 31 decreases over the length of the injection channel 7, so the distance A of the points largest distance 130 and 131 to the center 28 are smaller.

In Figur 5A bis 5E sind Querschnitte durch ein Ausführungsbeispiel eines Einspritzkanals 7 dargestellt, wobei die Querschnitte in ihrer Position den Ebenen A, B, C, D und E der Figur 2 entsprechen. In Figur 5A, die die Form des Einspritzkanals 7 in der Schnittebene A, also die Eintrittsöffnung 20 darstellt, sind die Ausbuchtungen 30, 31 noch deutlich ausgeprägt. In Figur 5B und Figur 5C sind diese Ausbuchtungen 30, 31 bereits deutlich vermindert, und in der Schnittebene D und E, die in den Figuren 5D und 5E dargestellt sind, sind die Ausbuchtungen 30, 31 verschwunden. Somit ergibt sich ein Einspritzkanal 7, der eine Eintrittsöffnung 20 mit den deutlich ausgebildeten Ausbuchtungen 30, 31 aufweist und der in seinem Verlauf bis zur Austrittsöffnung 22 in eine kreisrunde Form übergeht.In FIGS. 5A to 5E are cross sections through an embodiment of an injection channel 7, wherein the cross sections in their position the planes A, B, C, D and E of FIG. 2 correspond. In FIG. 5A , which represents the shape of the injection channel 7 in the sectional plane A, so the inlet opening 20, the bulges 30, 31 are still clearly pronounced. In FIG. 5B and FIG. 5C these bulges 30, 31 are already significantly reduced, and in the sectional plane D and E, in the Figures 5D and 5E are shown, the bulges 30, 31 are gone. This results in an injection channel 7, which has an inlet opening 20 with the clearly formed bulges 30, 31 and which merges in its course up to the outlet opening 22 in a circular shape.

Die Eintrittsöffnung 20 des Einspritzkanals 7 ist in dem oben beschriebenen Ausführungsbeispiel so orientiert, dass die Ausbuchtungen 30, 31 in Richtung des offenen Endes der Sackbohrung 3 weisen. Es kann jedoch auch vorgesehen sein, dass die Eintrittsöffnung 20 um 180° um den Mittelpunkt 28 gedreht angeordnet ist, so dass die Ausbuchtungen 30, 31 kanalartige Ausnehmungen an der Seite des Einspritzkanals 7 bilden, die von der Ventilnadel 5 weggerichtet ist. Je nach Strömungsbedingungen im Sackloch 9, die von dessen Form und Volumen abhängen, und der Ausgestaltung der Ventilnadel 5 kann auch diese Orientierung der Ausbuchtungen 30, 31 zu Einströmbedingungen im Einspritzkanal 7 führen, die vorteilhaft sind und zu einer verbesserten Spraybildung und damit Verbrennung führen.The inlet opening 20 of the injection channel 7 is oriented in the embodiment described above so that the bulges 30, 31 point in the direction of the open end of the blind bore 3. However, it can also be provided that the inlet opening 20 is arranged rotated by 180 ° about the center 28, so that the bulges 30, 31 form channel-like recesses on the side of the injection channel 7, which is directed away from the valve needle 5. Depending on the flow conditions in the blind hole 9, which depend on its shape and volume, and the configuration of the valve needle 5, this orientation of the bulges 30, 31 can lead to Einströmbedingungen in the injection channel 7, which are advantageous and lead to improved spray formation and combustion.

Es kann auch vorgesehen sein, dass statt einer kreisrunden Grundform, deren Durchmesser über die gesamte Länge des Einspritzkanals 7 konstant bleibt, sich der Durchmesser der Grundform von der Eintrittsöffnung 20 zur Austrittsöffnung 22 kontinuierlich vermindert, so dass sich beispielsweise eine konisch zulaufende Grundform ergibt, an deren Wänden die Ausbuchtungen 30, 31 vorgesehen sind.It can also be provided that instead of a circular basic shape whose diameter remains constant over the entire length of the injection channel 7, the diameter of the basic shape of the inlet opening 20 to the outlet opening 22 is continuously reduced, so that, for example, results in a tapered basic shape whose walls the bulges 30, 31 are provided.

Claims (6)

  1. Fuel injection valve for internal combustion engines, with a valve body (1) in which is formed a blind bore (3) which can be filled with fuel and at the bottom of which a valve seat (11) is formed, from which bottom emanates at least one injection duct (7) which has an inlet port (20) and an outlet port (22), characterized in that the inlet port (20), as seen in cross section,
    - has a circular basic shape with a radius (R) and with a centre point (28), and
    - a first bulge (30) is formed over a first angular sector (a1) of the circumference of the circular basic shape,
    - the first angular sector (a1) amounting to less than 180°, and
    - the first bulge (30) being such that the wall region of the bulge (30) has a point of greatest distance (130) from the centre point (28),
    - and with a second bulge (31) which is formed mirror-symmetrically to the first bulge (30) over a second angular sector (a2), the mirror plane (33) passing through the centre point (28) of the circular basic shape, and
    - the two bulges (30; 31) being arranged with respect to one another such that the two connecting lines (35, 36) of the points of greatest distance (130; 131) to the centre point (28) in each case form an angle (b) with the mirror plane (33) of less than 180° and
    - the mirror plane (33) lying in a common plane with the longitudinal axis (8) of the blind bore (3) and
    - the bulges (30; 31) being oriented towards the open end of the blind bore (3) and
    - the distance between the points of greatest distance (130; 131) of the bulges (30; 31) decreasing continuously in the longitudinal direction of the injection duct (7).
  2. Fuel injection valve according to Claim 1, characterized in that the circumference of the inlet port (20) has a circular shape outside the first bulge (30) and the second bulge (31).
  3. Fuel injection valve according to Claim 1, characterized in that the distance between the points of greatest distance (130; 131) and the centre point (28) decreases from the inlet port (20) as far as the outlet port (22), with the exception of the radius (R) of the circular basic shape, so that the outlet port (22) has a circular design.
  4. Fuel injection valve according to Claim 1, characterized in that the radius (R) of the circular basic shape decreases continuously from the inlet port (20) to the outlet port (22).
  5. Fuel injection valve according to Claim 1, characterized in that the transition of the bulges (30; 31) to the circular basic shape is rounded.
  6. Fuel injection valve according to Claim 1, characterized in that the entry edge at the inlet port (20) of the injection duct (7) is rounded.
EP04730825.9A 2003-07-04 2004-05-03 Fuel injection valve for combustion engines Expired - Lifetime EP1644636B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003130256 DE10330256A1 (en) 2003-07-04 2003-07-04 Fuel injection valve for internal combustion engine, comprises bulges arranged such that the two connecting lines of points of largest distance to the center form an angle of less than 180 degrees with the mirror plane
PCT/DE2004/000932 WO2005010350A1 (en) 2003-07-04 2004-05-03 Fuel injection valve for combustion engines

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EP1644636A1 EP1644636A1 (en) 2006-04-12
EP1644636B1 EP1644636B1 (en) 2007-04-11
EP1644636B2 true EP1644636B2 (en) 2016-08-03

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051365B4 (en) 2008-10-15 2010-07-01 L'orange Gmbh Fuel injection valve for internal combustion engines
DE102011007885A1 (en) * 2011-04-21 2012-10-25 Continental Automotive Gmbh Nozzle assembly for an injection valve and injection valve
EP2808533B1 (en) * 2013-05-29 2019-08-14 Delphi Technologies IP Limited Fuel injector

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0370659A1 (en) † 1988-11-19 1990-05-30 Lucas Industries Public Limited Company Fuel injection nozzle
DE19507171C1 (en) † 1995-03-02 1996-08-14 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
EP0890735B1 (en) † 1997-07-11 2006-10-18 Robert Bosch Gmbh Fuel injection valve

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0326096A (en) * 1989-06-22 1991-02-04 Fujitsu Ltd Cpu resetting system for controller to be supervised
JPH109095A (en) * 1996-06-21 1998-01-13 Zexel Corp Fuel injection nozzle
DE19815918A1 (en) * 1998-04-09 1999-10-21 Man B & W Diesel As Fuel injector
DE19914719C2 (en) * 1999-03-31 2001-05-03 Siemens Ag Device for hydroerosive rounding of inlet edges of the spray hole channels in a nozzle body
DE19931890A1 (en) * 1999-07-08 2001-01-18 Siemens Ag Edge rounding method for combustion engine fuel injection nozzle injection orifice channel
DE10132449A1 (en) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0370659A1 (en) † 1988-11-19 1990-05-30 Lucas Industries Public Limited Company Fuel injection nozzle
DE19507171C1 (en) † 1995-03-02 1996-08-14 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
EP0890735B1 (en) † 1997-07-11 2006-10-18 Robert Bosch Gmbh Fuel injection valve

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
"Diesel- und Benzindirekteeinspritzung", 3. TAGUNG †
"Hydro-erosives Schleifen von Diesel-Einspritzdüsen" †
TSCHÖKE, LEYH ET AL.: "Diesel- und Benzindirekteinspritzung II", HAUS DER TECHNIK FACHBUCH BAND 20, EXPERT-VERLAG, 1., December 2002 (2002-12-01), ESSEN, pages 68 - 77 †

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WO2005010350A1 (en) 2005-02-03
EP1644636A1 (en) 2006-04-12
DE10330256A1 (en) 2005-01-20
EP1644636B1 (en) 2007-04-11

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