EP1880100B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1880100B1
EP1880100B1 EP06708697.5A EP06708697A EP1880100B1 EP 1880100 B1 EP1880100 B1 EP 1880100B1 EP 06708697 A EP06708697 A EP 06708697A EP 1880100 B1 EP1880100 B1 EP 1880100B1
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EP
European Patent Office
Prior art keywords
valve
cylindrical section
fuel injection
undercut
valve body
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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.)
Not-in-force
Application number
EP06708697.5A
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German (de)
French (fr)
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EP1880100A1 (en
Inventor
Andreas Koeninger
Guenther Kubalik
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1880100A1 publication Critical patent/EP1880100A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing 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
    • F02M61/16—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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations

Definitions

  • the invention is based on a fuel injection valve, as for example from the published patent application DE 100 24 703 A1 is known.
  • a fuel injection valve As for example from the published patent application DE 100 24 703 A1 is known.
  • Such fuel injection valves have a housing which consists of several parts.
  • the part which has the injection openings, through which the fuel is ultimately injected into the corresponding combustion chamber of the internal combustion engine, is usually referred to as a valve body or nozzle body, which is formed substantially rotationally symmetrical.
  • a clamping nut is provided which surrounds the valve body over part of its length and which comes into contact with a valve shoulder.
  • the valve shoulder is formed by at least two different cylindrical portions of the valve body, wherein the first cylindrical portion, which faces the holding body, has a larger diameter than the second cylindrical portion.
  • the clamping nut is screwed onto an external thread of the holding body and acts on this valve shoulder, so that an axial force is exerted on the valve body in the direction of the holding body.
  • Another fuel injection valve is off JPS6326770U known. Since in modern fuel injection valves ever higher pressures are used to achieve a good atomization of the fuel, correspondingly high axial forces are necessary to securely connect the valve body with the holding body and to achieve the necessary tightness at the transition surface.
  • the high axial forces on the valve shoulder lead in the area between the first cylindrical portion and the second cylindrical section to tensile stresses, so that high notch stresses arise because there is usually a right-angled transition between the first and the second cylindrical section. If the notch stresses exceed a critical value, a crack in the valve body can occur at this point, through which fuel can escape from the interior of the valve body. In the worst case, it could also lead to a complete mechanical failure of the valve body.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that even with high axial tension forces and high internal pressures, the mechanical stability of the valve body is given.
  • the notch stresses are minimized at the transition from the first cylindrical portion to the second cylindrical portion.
  • an undercut is provided at the transition, which preferably has a flowing, rounded transition to the valve shoulder and the second cylindrical portion.
  • a circumferential annular groove is provided on the inside of the second cylindrical portion, which makes the valve body specifically flexibilized in this area and thus makes it more elastically deformable.
  • the notch stresses at the transition from the first to the second cylindrical section are also reduced, thus preventing a crack in this area.
  • this annular groove and a flowing, rounded transition to the adjacent inner side of the second cylindrical portion is provided.
  • the undercut is formed with a circular segment-shaped cross section, so that a smooth transition from the valve shoulder to the annular groove and from the annular groove to the second cylindrical portion is achieved. This minimizes remaining notch stresses and further increases strength.
  • the undercut may in this case be an axial undercut, in which a rear engagement with respect to the longitudinal axis of the valve body is formed. It is also possible to design the undercut so that a rear engagement is also present in the radial direction, ie in the direction of the valve shoulder. Which of the variants in the individual case is the better, must be determined by experiments or with simulation calculations.
  • the valve body has a bore in which the valve needle is guided. Between the valve needle and the wall of the bore, a pressure chamber is formed, which is radially expanded in the region of the valve shoulder.
  • the valve needle is guided in a guide portion of the bore, wherein the guide portion is located in the first cylindrical portion of the valve body.
  • the annular groove in the second cylindrical portion is spaced from this pressure chamber, so that further fuel can be introduced freely into the pressure chamber.
  • the annular groove in the second cylindrical portion may in this case also be formed in addition to the undercut at the transition from the first to the second cylindrical portion. The effects overlap in this case, so that the effects essentially add up.
  • FIG. 1 is a non-inventive fuel injection valve shown in longitudinal section.
  • the fuel injection valve has a housing 1 which, inter alia, comprises a valve body 3 and a holding body 5.
  • the valve body 3 has a longitudinal axis 6 and is formed on its outer surface substantially rotationally symmetrical.
  • the outer circumferential surface of the valve body 3 is formed by a first cylindrical portion 103 and an adjoining second cylindrical portion 203, wherein the second cylindrical portion 203 has a smaller diameter than the first cylindrical portion 103.
  • the third cylindrical portion is followed by a third cylindrical portion 303, which in turn has a relation to the second cylindrical portion 203 has slightly reduced outer diameter.
  • a valve shoulder 30 is formed on the outside of the valve body 3, which is oriented in a radial plane to the longitudinal axis 6 of the valve body 3.
  • the valve body 3 is surrounded in the region of the first cylindrical portion 103 and in the region of the second cylindrical portion 203 of a clamping nut 7 having an inner shoulder 8, with the clamping nut 7 on the valve shoulder 30 comes to the plant.
  • the clamping nut 7 engages in a formed on the holding body 5 and not shown in the drawing external thread, so that by screwing the clamping nut 7, an axial clamping force on the valve body 3 is formed, with which this is pressed against the holding body 5.
  • the amount of axial clamping force can be adjusted via the tightening torque of the clamping nut 7.
  • the valve body 3 has a bore 9 which is delimited at its combustion chamber end by a substantially conical valve seat 16, in whose region one or more injection openings 18 are formed, which open in installation position of the fuel injection valve in a combustion chamber of the internal combustion engine.
  • the valve needle 12 is sealingly guided with a guide portion 112 in a guide portion 11 of the bore 3, tapers the valve seat 16 to form a pressure shoulder 21 and finally goes into a shaft area 212.
  • a valve sealing surface 14 is formed, with which the valve needle 12 cooperates with the valve seat 16.
  • a pressure chamber 20 is formed which expands radially at the level of the pressure shoulder 21 and thus forms a pressure chamber 22.
  • the pressure chamber 22 can be filled with fuel under high pressure via an inlet channel 25 extending in the valve body 3 and in the holding body 5.
  • a control chamber 17 is formed on its valve seat side facing away in the valve body 3, which is bounded on the one hand by the bore 3 and on the other hand by the valve seat facing away from the end face of the valve needle 12. Facing away from the valve needle 12, the control chamber 17 is delimited by the holding body 5, wherein in the holding body 5 at least one inlet throttle 19 is formed, via which the control chamber 17 can be filled with fuel. In addition, there is still at least one outlet throttle in the holding body 5, via which the control chamber 17 can be relieved.
  • a high fuel pressure is always maintained in the pressure chamber 20, which corresponds to the injection pressure.
  • the valve needle 12 is pressed against the valve seat 16 and closes the injection ports 18. If injection take place, the pressure in the control chamber 17 is reduced, and the valve needle 12 lifts from the valve seat 16 and thus releases the injection openings 18. As a result, fuel flows from the pressure chamber 20 between the valve sealing surface 14 and the valve seat 16 to the injection openings 18 and is injected through them into the combustion chamber. By subsequently increasing the fuel pressure in the control chamber 17, the valve needle 12 moves back to its closed position and the injection is completed.
  • FIG. 2 shows an enlarged view of the designated II section of FIG. 1 ,
  • the undercut 35 has a tangential transition to the valve shoulder 30, so that the undercut 35 in longitudinal section, as in FIG. 2 can be subdivided into a concave area 40 and an adjoining convex area 42. This results in respect to the longitudinal axis 6 of the valve body 3, an undercut, which leads to a minimization of the stresses in the region of the undercut 35 when an axial force is exerted on the valve body 3 via the clamping nut 7.
  • FIG. 3 shows an enlarged view of the designated III section of FIG. 1
  • the alternative embodiment shown here of the undercut 35 surrounds as well as in FIG. 2 illustrated undercut 35 the valve body 3 on its entire circumference.
  • the in FIG. 3 shown undercut 35 has an undercut seen both in the direction of the longitudinal axis 6 of the valve body 3 and in the direction of the valve shoulder 30.
  • the undercut 35 shows a first convex portion 45, a concave portion 46 adjoining thereto, and a second convex portion 47 adjoining thereon.
  • such a shape of the undercut 35 may be cheaper than the undercut 35 after FIG. 2 to minimize the stresses in this area.
  • FIG. 4 shows a fuel injection valve according to the invention, in which case only the valve body 3 is shown.
  • the structure of the valve body 3 is substantially identical to that in FIG. 1 is shown, with the valve needle here for the sake of clarity was omitted.
  • an annular groove 50 is formed on the inside of the bore 9 in the region of the second cylindrical portion 203 here.
  • the annular groove 50 is spaced from the pressure chamber 22 and causes in this area a greater elastic deformability. Thereby, the notch stresses are reduced at the transition of the first 103 to the second cylindrical portion 203, since the second cylindrical portion degrades by elastic deformation of a portion of the voltage in this area.
  • the correct positioning with respect to the undercut 35 is important. That is, the appropriate axial distance must be found. This can easily be achieved by experiments or calculations, for example with the finite element method.
  • the transition from the inside of the bore 9 in the region of the second cylindrical section to the annular groove 50 should also be rounded here so that the notch stresses in the annular groove 50 are not too great.
  • FIG. 5 shows another example, wherein only the right half of the valve body 3 is shown.
  • the second cylindrical portion 203 is here also an annular groove 50 'is formed, but on the outside of the valve body 3.
  • the effect with respect to the voltage reduction is comparable to those in a formed on the inside of the valve body 3 annular groove 50, but the outer annular groove 50' easier to manufacture than an annular groove 50 on the hard to reach inside of the valve body 3.
  • the outer annular groove 50 ' can be with an undercut 35th combine that in FIG. 5 indicated by dashed lines. In this case, the effects of the undercut 35 and the annular groove 50 'are superimposed and reinforced.
  • the depth of the undercut 35 is determined depending on the requirement for the voltage reduction and is in the range of preferably 0.1 to 1 mm, with a range of 0.4 to 0.6 mm has been found to be particularly advantageous.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil aus, wie es beispielsweise aus der Offenlegungsschrift DE 100 24 703 A1 bekannt ist. Solche Kraftstoffeinspritzventile weisen ein Gehäuse auf, das aus mehreren Teilen besteht. Der Teil, der die Einspritzöffnungen aufweist, durch die der Kraftstoff letztendlich in den entsprechenden Brennraum der Brennkraftmaschine eingespritzt wird, wird üblicherweise als Ventilkörper oder Düsenkörper bezeichnet, der im wesentlichen rotationssymmetrisch ausgebildet ist. Da der Ventilkörper mit einem zugehörigen Haltekörper verbunden werden muss, der ebenfalls Teil des Gehäuses ist, ist eine Spannmutter vorgesehen, die den Ventilkörper auf einem Teil seiner Länge umgibt und die an einer Ventilschulter zur Anlage kommt. Die Ventilschulter wird durch wenigstens zwei unterschiedliche zylindrische Abschnitte des Ventilkörpers gebildet, wobei der erste zylindrische Abschnitt, der dem Haltekörper zugewandt ist, einen größeren Durchmesser aufweist als der zweite zylindrische Abschnitt. Die Spannmutter wird auf ein Außengewinde des Haltekörpers aufgeschraubt und greift dabei an dieser Ventilschulter an, sodass eine axiale Kraft auf den Ventilkörper in Richtung des Haltekörpers ausgeübt wird. Ein weiteres Kraftstoffeinspritzventil ist aus JPS6326770U bekannt. Da bei modernen Kraftstoffeinspritzventilen immer höhere Drücke eingesetzt werden, um eine gute Zerstäubung des Kraftstoffs zu erreichen, sind entsprechend hohe axiale Kräfte nötig, um den Ventilkörper sicher mit dem Haltekörper zu verbinden und die notwendige Dichtheit an der Übergangsfläche zu erreichen. Die hohen axialen Kräfte an der Ventilschulter führen im Bereich zwischen dem ersten zylindrischen Abschnitt und dem zweiten zylindrischen Abschnitt zu Zugspannungen, so dass hohe Kerbspannungen entstehen, da in der Regel ein rechtwinkliger Übergang zwischen dem ersten und dem zweiten zylindrischen Abschnitt gegeben ist. Übersteigen die Kerbspannungen einen kritischen Wert, kann an dieser Stelle ein Riss im Ventilkörper entstehen, durch den Kraftstoff aus dem Inneren des Ventilkörpers austreten kann. Schlimmstenfalls könnte es auch zu einem völligen mechanischen Versagen des Ventilkörpers kommen.The invention is based on a fuel injection valve, as for example from the published patent application DE 100 24 703 A1 is known. Such fuel injection valves have a housing which consists of several parts. The part which has the injection openings, through which the fuel is ultimately injected into the corresponding combustion chamber of the internal combustion engine, is usually referred to as a valve body or nozzle body, which is formed substantially rotationally symmetrical. Since the valve body must be connected to an associated holding body, which is also part of the housing, a clamping nut is provided which surrounds the valve body over part of its length and which comes into contact with a valve shoulder. The valve shoulder is formed by at least two different cylindrical portions of the valve body, wherein the first cylindrical portion, which faces the holding body, has a larger diameter than the second cylindrical portion. The clamping nut is screwed onto an external thread of the holding body and acts on this valve shoulder, so that an axial force is exerted on the valve body in the direction of the holding body. Another fuel injection valve is off JPS6326770U known. Since in modern fuel injection valves ever higher pressures are used to achieve a good atomization of the fuel, correspondingly high axial forces are necessary to securely connect the valve body with the holding body and to achieve the necessary tightness at the transition surface. The high axial forces on the valve shoulder lead in the area between the first cylindrical portion and the second cylindrical section to tensile stresses, so that high notch stresses arise because there is usually a right-angled transition between the first and the second cylindrical section. If the notch stresses exceed a critical value, a crack in the valve body can occur at this point, through which fuel can escape from the interior of the valve body. In the worst case, it could also lead to a complete mechanical failure of the valve body.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass auch bei hohen axialen Verspannungskräften und hohen inneren Drücken die mechanische Stabilität des Ventilkörpers gegeben ist. Hierzu werden die Kerbspannungen am Übergang vom ersten zylindrischen Abschnitt zum zweiten zylindrischen Abschnitt minimiert. Dies wird dadurch erreicht, dass am Übergang ein Hinterstich vorgesehen ist, der vorzugsweise einen fließenden, gerundeten Übergang zur Ventilschulter und zum zweiten zylindrischen Abschnitt aufweist. Weiter ist vorgesehen, dass an der Innenseite des zweiten zylindrischen Abschnitts eine umlaufende Ringnut vorgesehen ist, was den Ventilkörper in diesem Bereich gezielt flexibilisiert und damit stärker elastisch verformbar macht. Dadurch werden die Kerbspannungen am Übergang vom ersten zum zweiten zylindrischen Abschnitt ebenfalls reduziert und damit ein Riss in diesem Bereich verhindert. Bei dieser Ringnut ist auch ein fließender, gerundeter Übergang zur angrenzenden Innenseite des zweiten zylindrischen Abschnitts vorgesehen.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that even with high axial tension forces and high internal pressures, the mechanical stability of the valve body is given. For this purpose, the notch stresses are minimized at the transition from the first cylindrical portion to the second cylindrical portion. This is achieved in that an undercut is provided at the transition, which preferably has a flowing, rounded transition to the valve shoulder and the second cylindrical portion. It is further provided that a circumferential annular groove is provided on the inside of the second cylindrical portion, which makes the valve body specifically flexibilized in this area and thus makes it more elastically deformable. As a result, the notch stresses at the transition from the first to the second cylindrical section are also reduced, thus preventing a crack in this area. In this annular groove and a flowing, rounded transition to the adjacent inner side of the second cylindrical portion is provided.

Durch die abhängigen Ansprüche sind vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung möglich. In einer ersten vorteilhaften Ausgestaltung ist der Hinterstich mit einem kreissegmentförmigen Querschnitt ausgebildet, so dass ein weicher Übergang von der Ventilschulter zur Ringnut und von der Ringnut zum zweiten zylindrischen Abschnitt erreicht wird. Dadurch werden verbleibende Kerbspannungen minimiert und die Festigkeit weiter erhöht. Der Hinterstich kann hierbei ein axialer Hinterstich sein, bei dem eine Hintergreifung bezüglich der Längsachse des Ventilkörpers ausgebildet ist. Es ist auch möglich, den Hinterstich so auszubilden, dass auch in radialer Richtung, also in Richtung der Ventilschulter, eine Hintergreifung vorhanden ist. Welche der Varianten im Einzelfall die bessere ist, muss durch Versuche oder mit Simulationsrechnungen ermittelt werden.By the dependent claims advantageous embodiments of the subject invention are possible. In a first advantageous embodiment, the undercut is formed with a circular segment-shaped cross section, so that a smooth transition from the valve shoulder to the annular groove and from the annular groove to the second cylindrical portion is achieved. This minimizes remaining notch stresses and further increases strength. The undercut may in this case be an axial undercut, in which a rear engagement with respect to the longitudinal axis of the valve body is formed. It is also possible to design the undercut so that a rear engagement is also present in the radial direction, ie in the direction of the valve shoulder. Which of the variants in the individual case is the better, must be determined by experiments or with simulation calculations.

In einer vorteilhaften Ausgestaltung weist der Ventilkörper eine Bohrung auf, in der die Ventilnadel geführt ist. Zwischen der Ventilnadel und der Wand der Bohrung ist ein Druckraum ausgebildet, der im Bereich der Ventilschulter radial erweitert ist. Die Ventilnadel wird in einem Führungsabschnitt der Bohrung geführt, wobei sich der Führungsabschnitt im ersten zylindrischen Abschnitt des Ventilkörpers befindet. Die Ringnut im zweiten zylindrischen Abschnitt ist zu dieser Druckkammer beabstandet, so dass weiterhin Kraftstoff ungehindert in die Druckkammer eingeleitet werden kann. Die Ringnut im zweiten zylindrischen Abschnitt kann hierbei auch zusätzlich zum Hinterstich am Übergang vom ersten zum zweiten zylindrischen Abschnitt ausgebildet sein. Die Effekte überlagern sich in diesem Fall, so dass sich die Wirkungen im wesentlichen addieren.In an advantageous embodiment, the valve body has a bore in which the valve needle is guided. Between the valve needle and the wall of the bore, a pressure chamber is formed, which is radially expanded in the region of the valve shoulder. The valve needle is guided in a guide portion of the bore, wherein the guide portion is located in the first cylindrical portion of the valve body. The annular groove in the second cylindrical portion is spaced from this pressure chamber, so that further fuel can be introduced freely into the pressure chamber. The annular groove in the second cylindrical portion may in this case also be formed in addition to the undercut at the transition from the first to the second cylindrical portion. The effects overlap in this case, so that the effects essentially add up.

Weitere Vorteile und vorteilhafte Ausgestaltungen sind der Beschreibung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the description and the claims can be removed.

Zeichnungdrawing

In der Zeichnung sind verschiedene Ausführungsbeispiele des Gegenstandes der Erfindung gezeigt. Es zeigt

Figur 1
einen Längsschnitt durch ein nicht erfindungsgemäßes Kraftstoffeinspritzventil, wobei in der linken und rechten Hälfte der Figur 1 zwei verschiedene Kraftstoffeinspritzventile dargestellt sind,
Figur 2
zeigt eine vergrößerte Darstellung des mit II bezeichneten Ausschnittes der Figur 1,
Figur 3
eine vergrößerte Darstellung des mit III bezeichneten Ausschnitts der Figur 1,
Figur 4
ein erfindungsgemäßes Kraftstoffeinspritzventil, wobei hier nur der Ventilkörper gezeigt ist, dessen linke und rechte Hälfte unterschiedliche Ausgestaltungen zeigen und
Figur 5
ein weiteres, nicht erfindungsgemäßes Kraftstoffeinspritzventil, wobei hier die Ringnut an der Außenseite des Ventilkörpers ausgebildet ist.
In the drawing, various embodiments of the subject matter of the invention are shown. It shows
FIG. 1
a longitudinal section through a non-inventive fuel injection valve, wherein in the left and right half of FIG. 1 two different fuel injection valves are shown,
FIG. 2
shows an enlarged view of the designated II section of the FIG. 1 .
FIG. 3
3 is an enlarged view of the section of FIG. 1 designated by III,
FIG. 4
a fuel injection valve according to the invention, wherein here only the valve body is shown, the left and right half show different configurations and
FIG. 5
another, not inventive fuel injection valve, in which case the annular groove is formed on the outside of the valve body.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein nicht erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das unter anderem einen Ventilkörper 3 und einen Haltekörper 5 umfasst. Der Ventilkörper 3 weist eine Längsachse 6 auf und ist an seiner Außenfläche im wesentlichen rotationssymmetrisch ausgebildet. Die Außenmantelfläche des Ventilkörpers 3 wird dabei von einem ersten zylindrischen Abschnitt 103 und einem sich daran anschließenden zweiten zylindrischen Abschnitt 203 gebildet, wobei der zweite zylindrische Abschnitt 203 einen kleineren Durchmesser aufweist als der erste zylindrische Abschnitt 103. An den zweiten zylindrischen Abschnitt schließt sich ein dritter zylindrischer Abschnitt 303 an, der wiederum einen gegenüber dem zweiten zylindrischen Abschnitt 203 etwas verringerten Außendurchmesser aufweist.In FIG. 1 is a non-inventive fuel injection valve shown in longitudinal section. The fuel injection valve has a housing 1 which, inter alia, comprises a valve body 3 and a holding body 5. The valve body 3 has a longitudinal axis 6 and is formed on its outer surface substantially rotationally symmetrical. The outer circumferential surface of the valve body 3 is formed by a first cylindrical portion 103 and an adjoining second cylindrical portion 203, wherein the second cylindrical portion 203 has a smaller diameter than the first cylindrical portion 103. The third cylindrical portion is followed by a third cylindrical portion 303, which in turn has a relation to the second cylindrical portion 203 has slightly reduced outer diameter.

Durch den ersten zylindrischen Abschnitt 103 und den zweiten zylindrischen Abschnitt 203 ist an der Außenseite des Ventilkörpers 3 eine Ventilschulter 30 ausgebildet, die in einer Radialebene zur Längsachse 6 des Ventilkörpers 3 orientiert ist. Um den Ventilkörper 3 gegen den Haltekörper 5 zu verspannen, ist der Ventilkörper 3 im Bereich des ersten zylindrischen Abschnitts 103 und im Bereich des zweiten zylindrischen Abschnitts 203 von einer Spannmutter 7 umgeben, die eine Innenschulter 8 aufweist, mit der die Spannmutter 7 an der Ventilschulter 30 zur Anlage kommt. Die Spannmutter 7 greift in ein am Haltekörper 5 ausgebildetes und in der Zeichnung nicht dargestelltes Außengewinde ein, sodass durch Verschrauben der Spannmutter 7 eine axiale Spannkraft auf den Ventilkörper 3 entsteht, mit der dieser gegen den Haltekörper 5 gepresst wird. Die Höhe der axialen Spannkraft lässt sich dabei über das Anzugsmoment der Spannmutter 7 einstellen.By the first cylindrical portion 103 and the second cylindrical portion 203, a valve shoulder 30 is formed on the outside of the valve body 3, which is oriented in a radial plane to the longitudinal axis 6 of the valve body 3. In order to clamp the valve body 3 against the holding body 5, the valve body 3 is surrounded in the region of the first cylindrical portion 103 and in the region of the second cylindrical portion 203 of a clamping nut 7 having an inner shoulder 8, with the clamping nut 7 on the valve shoulder 30 comes to the plant. The clamping nut 7 engages in a formed on the holding body 5 and not shown in the drawing external thread, so that by screwing the clamping nut 7, an axial clamping force on the valve body 3 is formed, with which this is pressed against the holding body 5. The amount of axial clamping force can be adjusted via the tightening torque of the clamping nut 7.

Der Ventilkörper 3 weist eine Bohrung 9 auf, die an ihrem brennraumseitigen Ende von einem im wesentlichen konischen Ventilsitz 16 begrenzt wird, in dessen Bereich eine oder mehrere Einspritzöffnungen 18 ausgebildet sind, die in Einbaulage des Kraftstoffeinspritzventils in einen Brennraum der Brennkraftmaschine münden. Die Ventilnadel 12 wird mit einem Führungsabschnitt 112 in einem Führungsbereich 11 der Bohrung 3 dichtend geführt, verjüngt sich dem Ventilsitz 16 zu unter Bildung einer Druckschulter 21 und geht schließlich in einen Schaftbereich 212 über. Am ventilsitzseitigen Ende der Ventilnadel 12 ist eine Ventildichtfläche 14 ausgebildet, mit der die Ventilnadel 12 mit dem Ventilsitz 16 zusammenwirkt. Zwischen der Ventilnadel 12 und der Wand der Bohrung 9 ist ein Druckraum 20 ausgebildet, der sich auf Höhe der Druckschulter 21 radial erweitert und so eine Druckkammer 22 bildet. Die Druckkammer 22 kann über einen im Ventilkörper 3 und im Haltekörper 5 verlaufenden Zulaufkanal 25 mit Kraftstoff unter hohem Druck befüllt werden.The valve body 3 has a bore 9 which is delimited at its combustion chamber end by a substantially conical valve seat 16, in whose region one or more injection openings 18 are formed, which open in installation position of the fuel injection valve in a combustion chamber of the internal combustion engine. The valve needle 12 is sealingly guided with a guide portion 112 in a guide portion 11 of the bore 3, tapers the valve seat 16 to form a pressure shoulder 21 and finally goes into a shaft area 212. At the valve seat side end of the valve needle 12, a valve sealing surface 14 is formed, with which the valve needle 12 cooperates with the valve seat 16. Between the valve needle 12 and the wall of the bore 9, a pressure chamber 20 is formed which expands radially at the level of the pressure shoulder 21 and thus forms a pressure chamber 22. The pressure chamber 22 can be filled with fuel under high pressure via an inlet channel 25 extending in the valve body 3 and in the holding body 5.

Zur Steuerung der Längsbewegung der Ventilnadel 12 ist an ihrer ventilsitzabgewandten Seite im Ventilkörper 3 ein Steuerraum 17 ausgebildet, der einerseits von der Bohrung 3 und andererseits von der ventilsitzabgewandten Stirnseite der Ventilnadel 12 begrenzt wird. Der Ventilnadel 12 abgewandt wird der Steuerraum 17 vom Haltekörper 5 begrenzt, wobei im Haltekörper 5 wenigstens eine Zulaufdrossel 19 ausgebildet ist, über die der Steuerraum 17 mit Kraftstoff befüllt werden kann. Darüber hinaus befindet sich noch wenigstens eine Ablaufdrossel im Haltekörper 5, über die der Steuerraum 17 entlastet werden kann.To control the longitudinal movement of the valve needle 12, a control chamber 17 is formed on its valve seat side facing away in the valve body 3, which is bounded on the one hand by the bore 3 and on the other hand by the valve seat facing away from the end face of the valve needle 12. Facing away from the valve needle 12, the control chamber 17 is delimited by the holding body 5, wherein in the holding body 5 at least one inlet throttle 19 is formed, via which the control chamber 17 can be filled with fuel. In addition, there is still at least one outlet throttle in the holding body 5, via which the control chamber 17 can be relieved.

Zur Einspritzung von Kraftstoff wird im Druckraum 20 stets ein hoher Kraftstoffdruck aufrechterhalten, der dem Einspritzdruck entspricht. Solange im Steuerraum 17 ein genügend hoher Kraftstoffdruck vorhanden ist, wird die Ventilnadel 12 gegen den Ventilsitz 16 gepresst und verschließt die Einspritzöffnungen 18. Soll eine Einspritzung erfolgen, so wird der Druck im Steuerraum 17 gemindert, und die Ventilnadel 12 hebt vom Ventilsitz 16 ab und gibt so die Einspritzöffnungen 18 frei. Dadurch strömt Kraftstoff aus dem Druckraum 20 zwischen der Ventildichtfläche 14 und dem Ventilsitz 16 hindurch zu den Einspritzöffnungen 18 und wird durch diese in den Brennraum eingespritzt. Durch anschließendes Erhöhen des Kraftstoffdrucks im Steuerraum 17 fährt die Ventilnadel 12 zurück in ihre Schließstellung und die Einspritzung ist beendet.For the injection of fuel, a high fuel pressure is always maintained in the pressure chamber 20, which corresponds to the injection pressure. As long as in the control chamber 17, a sufficiently high fuel pressure is present, the valve needle 12 is pressed against the valve seat 16 and closes the injection ports 18. If injection take place, the pressure in the control chamber 17 is reduced, and the valve needle 12 lifts from the valve seat 16 and thus releases the injection openings 18. As a result, fuel flows from the pressure chamber 20 between the valve sealing surface 14 and the valve seat 16 to the injection openings 18 and is injected through them into the combustion chamber. By subsequently increasing the fuel pressure in the control chamber 17, the valve needle 12 moves back to its closed position and the injection is completed.

Die axialen Kräfte auf den Ventilkörper 3 wirken in axialer Richtung auf die Ventilschulter 30, sodass es im Übergangsbereich zwischen der Ventilschulter 30 und dem zweiten zylindrischen Abschnitt 203 zu Kerbspannungen kommt, die um so höher sind, je scharfkantiger der Übergang ausgebildet ist und je höher das Anzugsmoment der Spannmutter ist. Um die Kerbspannungen zu minimieren, ist am Übergang der Ventilschulter 30 zum zweiten zylindrischen Abschnitt 203 ein Hinterstich 35 ausgebildet, der den Ventilkörper 3 auf seinem gesamten Umfang umgibt. In der Figur 1 sind in der linken und rechten Hälfte jeweils zwei verschiedene Formen des Hinterstichs 35 angedeutet, die in Figur 2 und Figur 3 nochmals näher dargestellt sind.The axial forces acting on the valve body 3 in the axial direction on the valve shoulder 30, so that it comes in the transition region between the valve shoulder 30 and the second cylindrical portion 203 to notch stresses, which are the higher, the sharp-edged the transition is formed and the higher the Tightening torque of the clamping nut is. In order to minimize the notch stresses, an undercut 35 is formed at the transition of the valve shoulder 30 to the second cylindrical portion 203, which is the valve body Surrounds 3 on its entire circumference. In the FIG. 1 are each indicated in the left and right half respectively two different forms of the Hinterstichs 35, the in FIG. 2 and FIG. 3 again shown in more detail.

Figur 2 zeigt eine vergrößerte Darstellung des mit II bezeichneten Ausschnitts von Figur 1. Der Hinterstich 35 weist einen tangentialen Übergang zur Ventilschulter 30 auf, so dass sich der Hinterstich 35 im Längsschnitt, wie in Figur 2 dargestellt, in einen Konkavbereich 40 und einen sich daran anschließenden Konvexbereich 42 unterteilen lässt. Damit ergibt sich bezüglich der Längsachse 6 des Ventilkörpers 3 ein Hinterstich, der zu einer Minimierung der Spannungen im Bereich des Hinterstichs 35 führt, wenn über die Spannmutter 7 eine axiale Kraft auf den Ventilkörper 3 ausgeübt wird. FIG. 2 shows an enlarged view of the designated II section of FIG. 1 , The undercut 35 has a tangential transition to the valve shoulder 30, so that the undercut 35 in longitudinal section, as in FIG. 2 can be subdivided into a concave area 40 and an adjoining convex area 42. This results in respect to the longitudinal axis 6 of the valve body 3, an undercut, which leads to a minimization of the stresses in the region of the undercut 35 when an axial force is exerted on the valve body 3 via the clamping nut 7.

Figur 3 zeigt eine vergrößerte Darstellung des mit III bezeichneten Ausschnitts von Figur 1. Die hier gezeigt alternative Ausgestaltung des Hinterstichs 35 umgibt ebenso wie der in Figur 2 dargestellte Hinterstich 35 den Ventilkörper 3 auf seinem gesamten Umfang. Der in Figur 3 gezeigte Hinterstich 35 weist eine Hinterschneidung sowohl in Richtung der Längsachse 6 des Ventilkörpers 3 gesehen als auch in Richtung der Ventilschulter 30 auf. Ausgehend von der Ventilschulter 30 zeigt der Hinterstich 35 einen ersten Konvexbereich 45, einen sich daran anschließenden Konkavbereich 46 und einen sich daran wiederum anschließenden zweiten Konvexbereich 47 auf. Je nach den wirkenden Spannkräften durch die Spannmutter 7 und durch die Ausgestaltung der Druckkammer 22 kann eine solche Form des Hinterstichs 35 günstiger sein als der Hinterstich 35 nach Figur 2, um die Spannungen in diesem Bereich zu minimieren. FIG. 3 shows an enlarged view of the designated III section of FIG. 1 , The alternative embodiment shown here of the undercut 35 surrounds as well as in FIG. 2 illustrated undercut 35 the valve body 3 on its entire circumference. The in FIG. 3 shown undercut 35 has an undercut seen both in the direction of the longitudinal axis 6 of the valve body 3 and in the direction of the valve shoulder 30. Starting from the valve shoulder 30, the undercut 35 shows a first convex portion 45, a concave portion 46 adjoining thereto, and a second convex portion 47 adjoining thereon. Depending on the acting clamping forces by the clamping nut 7 and by the configuration of the pressure chamber 22, such a shape of the undercut 35 may be cheaper than the undercut 35 after FIG. 2 to minimize the stresses in this area.

Figur 4 zeigt ein erfindungsgemäßes Kraftstoffeinspritzventil, wobei hier nur der Ventilkörper 3 gezeigt ist. Der Aufbau des Ventilkörpers 3 ist im wesentlichen identisch mit dem, der in Figur 1 gezeigt ist, wobei die Ventilnadel
hier der Übersichtlichkeit halber weggelassen wurde. Neben der Druckkammer 22, die durch eine radiale Erweiterung der Bohrung 9 gebildet ist, ist hier im Bereich des zweiten zylindrischen Abschnitts 203 eine Ringnut 50 an der Innenseite der Bohrung 9 ausgebildet. Die Ringnut 50 ist von der Druckkammer 22 beabstandet und bewirkt in diesem Bereich eine größere elastische Verformbarkeit. Dadurch werden die Kerbspannungen am Übergang des ersten 103 zum zweiten zylindrischen Abschnitts 203 reduziert, da der zweite zylindrische Abschnitt durch elastische Verformung einen Teil der Spannung in diesem Bereich abbaut. FIG. 4 shows a fuel injection valve according to the invention, in which case only the valve body 3 is shown. The structure of the valve body 3 is substantially identical to that in FIG. 1 is shown, with the valve needle
here for the sake of clarity was omitted. In addition to the pressure chamber 22, which is formed by a radial extension of the bore 9, an annular groove 50 is formed on the inside of the bore 9 in the region of the second cylindrical portion 203 here. The annular groove 50 is spaced from the pressure chamber 22 and causes in this area a greater elastic deformability. Thereby, the notch stresses are reduced at the transition of the first 103 to the second cylindrical portion 203, since the second cylindrical portion degrades by elastic deformation of a portion of the voltage in this area.

In der rechten Hälfte der Figur 4 ist am Übergang vom ersten zylindrischen Abschnitt 103 zum zweiten zylindrischen Abschnitt 203 ein im Querschnitt rechtwinkliger Übergang vorgesehen. Es ist vorgesehen, wie in der linken Hälfte der Figur 4 dargestellt, zusätzlich zur Ringnut 50 einen Hinterstich 35 vorzusehen, wie er auch in den Figuren 1 bis 3 dargestellt ist. Im Zusammenspiel mit dem Hinterstich 35 ergibt sich durch die innere Ringnut 50 eine weitere, gezielte Schwächung der Wand des Ventilkörpers 3 und damit eine zusätzliche Flexibilisierung des Ventilkörpers 3 in diesem Bereich. Dies führt zu einer weiteren Minimierung der Spannungen im Bereich des Hinterstichs 35 und damit zu einer noch größeren Stabilität des Ventilkörpers 3, so dass die Entstehung von Rissen durch die Spannkräfte der Spannmutter 7 weitgehend ausgeschlossen ist. Für die Wirkung der Ringnut 50 ist die richtige Positionierung bezüglich des Hinterstichs 35 wichtig. Das heißt, es muss der geeignete axiale Abstand gefunden werden. Dies lässt sich leicht durch Versuche oder durch Berechnungen, beispielsweise mit der Methode der Finiten Elemente, erreichen. Ebenso wie beim Hinterstich 35 sollte auch hier der Übergang von der Innenseite der Bohrung 9 im Bereich des zweiten zylindrischen Abschnitts zur Ringnut 50 gerundet ausgebildet sein, um die Kerbspannungen in der Ringnut 50 nicht zu groß werden zu lassen.In the right half of the FIG. 4 At the transition from the first cylindrical portion 103 to the second cylindrical portion 203 is provided a cross-sectionally rectangular transition. It is provided as in the left half of the FIG. 4 shown, in addition to the annular groove 50 to provide an undercut 35, as shown in Figures 1 to 3. In conjunction with the undercut 35 results from the inner annular groove 50, a further, targeted weakening of the wall of the valve body 3 and thus an additional flexibilization of the valve body 3 in this area. This leads to a further minimization of the stresses in the region of the undercut 35 and thus to an even greater stability of the valve body 3, so that the formation of cracks by the clamping forces of the clamping nut 7 is largely excluded. For the effect of the annular groove 50, the correct positioning with respect to the undercut 35 is important. That is, the appropriate axial distance must be found. This can easily be achieved by experiments or calculations, for example with the finite element method. As in the case of the undercut 35, the transition from the inside of the bore 9 in the region of the second cylindrical section to the annular groove 50 should also be rounded here so that the notch stresses in the annular groove 50 are not too great.

Figur 5 zeigt ein weiteres Beispiel, wobei nur die rechte Hälfte des Ventilkörpers 3 dargestellt ist. Im zweiten zylindrischen Abschnitt 203 ist hier ebenfalls eine Ringnut 50' ausgebildet, jedoch an der Außenseite des Ventilkörpers 3. Die Wirkung bezüglich der Spannungserniedrigung ist vergleichbar mit denen bei einer an der Innenseite des Ventilkörpers 3 ausgebildeten Ringnut 50, jedoch ist die außenliegende Ringnut 50' leichter zu fertigen als eine Ringnut 50 an der schwer zugänglichen Innenseite des Ventilkörpers 3. Auch die außenliegende Ringnut 50' lässt sich mit einem Hinterstich 35 kombinieren, der in Figur 5 gestrichelt eingezeichnet ist. Hierbei überlagern und verstärken sich die Effekte des Hinterstichs 35 und der Ringnut 50'. FIG. 5 shows another example, wherein only the right half of the valve body 3 is shown. In the second cylindrical portion 203 is here also an annular groove 50 'is formed, but on the outside of the valve body 3. The effect with respect to the voltage reduction is comparable to those in a formed on the inside of the valve body 3 annular groove 50, but the outer annular groove 50' easier to manufacture than an annular groove 50 on the hard to reach inside of the valve body 3. The outer annular groove 50 'can be with an undercut 35th combine that in FIG. 5 indicated by dashed lines. In this case, the effects of the undercut 35 and the annular groove 50 'are superimposed and reinforced.

Die Tiefe des Hinterstichs 35 wird je nach Anforderung an die Spannungsreduzierung bestimmt und liegt im Bereich von vorzugsweise 0,1 bis 1 mm, wobei sich ein Bereich von 0,4 bis 0,6 mm als besonders vorteilhaft erwiesen hat.The depth of the undercut 35 is determined depending on the requirement for the voltage reduction and is in the range of preferably 0.1 to 1 mm, with a range of 0.4 to 0.6 mm has been found to be particularly advantageous.

Claims (8)

  1. Fuel injection valve having a housing (1) which comprises a valve body (3) with at least one injection opening (18), wherein the outer shell surface of the valve body (3) is of substantially rotationally symmetrical form and has a first cylindrical section (103) which is adjoined, towards the injection openings (18), by a second cylindrical section (203) of the outer shell surface, which second cylindrical section has a smaller diameter than the first cylindrical section (103), whereby a valve shoulder (30) is formed, wherein an undercut (35) is formed at the transition of the valve shoulder (30) to the second cylindrical section (203), which undercut minimizes the notch stresses at the transition from the first cylindrical section (103) to the second cylindrical section (203), wherein the transition from the valve shoulder (30) to the undercut (35) runs tangentially in cross section,
    characterized
    in that, on the inner side of the second cylindrical section (203), there is formed an encircling ring-shaped groove (50; 50') which minimizes the notch stresses at the transition from the first cylindrical section (103) to the second cylindrical section (203).
  2. Fuel injection valve according to Claim 1, characterized in that the valve body (3) is braced by means of a clamping nut (7) against a holding body (5), wherein the holding body (5) is part of the housing (1), wherein the clamping nut (7) bears against the valve shoulder (30) and surrounds the valve body (3) in the region of the first cylindrical section (103).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the valve shoulder (30) is formed in the manner of a ring-shaped disk.
  4. Fuel injection valve according to Claim 2 or 3, characterized in that the undercut (35) has a circular-segment-shaped cross section.
  5. Fuel injection valve according to Claim 4, characterized in that the transition of the valve shoulder (30) to the second cylindrical surface (205) is of rounded form.
  6. Fuel injection valve according to Claim 1, characterized in that a valve needle (12) is arranged in longitudinally displaceable fashion in the valve body (3), which valve needle is guided in the region of the first cylindrical section (103) of the valve body (3), wherein a pressure chamber (20) is formed between the valve needle (3) and the wall of the bore (9), which pressure chamber widens within the first cylindrical section (103) so as to form a pressure chamber (22).
  7. Fuel injection valve according to Claim 6, characterized in that the pressure chamber (22) is axially spaced apart from the ring-shaped groove (50; 50').
  8. Fuel injection valve according to Claim 7, characterized in that the ring-shaped groove (50; 51) is axially spaced apart from the undercut (35).
EP06708697.5A 2005-05-02 2006-03-09 Fuel injection valve for internal combustion engines Not-in-force EP1880100B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005020364 2005-05-02
DE102005038444A DE102005038444A1 (en) 2005-05-02 2005-08-16 Fuel injection valve for internal combustion engines
PCT/EP2006/060577 WO2006117259A1 (en) 2005-05-02 2006-03-09 Fuel injection valve for internal combustion engines

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EP1880100A1 EP1880100A1 (en) 2008-01-23
EP1880100B1 true EP1880100B1 (en) 2017-06-07

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WO (1) WO2006117259A1 (en)

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RU194380U1 (en) * 2019-08-19 2019-12-09 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" FUEL BURNER

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JPS6326770U (en) * 1986-08-04 1988-02-22
DE19546361A1 (en) * 1994-12-28 1996-07-11 Zexel Corp Solenoid fuel injector for IC engine
WO2004031570A1 (en) * 2002-09-27 2004-04-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
JP2004218542A (en) * 2003-01-15 2004-08-05 Toyota Motor Corp Fuel injection valve

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DE2120108A1 (en) * 1971-04-24 1972-11-09 LOrange KG, 7000 Stuttgart Fuel injector
DE10024703A1 (en) 2000-05-18 2001-11-22 Bosch Gmbh Robert Injection arrangement for fuel storage injection system has valve unit blocking auxiliary channel and outlet path in alternation
DE10149961A1 (en) * 2001-10-10 2003-04-30 Bosch Gmbh Robert Fuel injection device for internal combustion engine, especially common rail injector, has flow path control sections interacting to give defined flow characteristic against time
DE10260724A1 (en) * 2002-12-23 2004-07-01 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE20320869U1 (en) * 2003-08-11 2005-05-19 Siemens Ag Fuel injection valve has clamp nut opening internal diameter corresponding essentially to external diameter of second cylindrical section of valve body with peripheral groove in transition from second cylindrical section to contact surface

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Publication number Priority date Publication date Assignee Title
JPS6326770U (en) * 1986-08-04 1988-02-22
DE19546361A1 (en) * 1994-12-28 1996-07-11 Zexel Corp Solenoid fuel injector for IC engine
WO2004031570A1 (en) * 2002-09-27 2004-04-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
JP2004218542A (en) * 2003-01-15 2004-08-05 Toyota Motor Corp Fuel injection valve

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Publication number Priority date Publication date Assignee Title
RU194380U1 (en) * 2019-08-19 2019-12-09 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" FUEL BURNER

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WO2006117259A1 (en) 2006-11-09
EP1880100A1 (en) 2008-01-23

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