EP1407133B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1407133B1
EP1407133B1 EP02754314A EP02754314A EP1407133B1 EP 1407133 B1 EP1407133 B1 EP 1407133B1 EP 02754314 A EP02754314 A EP 02754314A EP 02754314 A EP02754314 A EP 02754314A EP 1407133 B1 EP1407133 B1 EP 1407133B1
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EP
European Patent Office
Prior art keywords
fuel injection
recess
injection valve
chamber
flank
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
EP02754314A
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German (de)
French (fr)
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EP1407133A1 (en
Inventor
Michael Lindner
Juergen Bauer
Martin Zimmer
Claus Westphal
Alexander Redlich
Ruediger Bohnsack
Peter Rehbein
Juergen Hackenberg
Georg Ketteler
Marcus Rinke
Jochen Straehle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1407133A1 publication Critical patent/EP1407133A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve is for example from the Scriptures DE 198 20 264 A1 known.
  • the fuel injection valve has a housing in which a valve needle is arranged to be longitudinally displaceable in a bore.
  • the valve needle is guided in a guide portion of the bore sealingly in this.
  • a first fuel-filled space adjoins this and at the other end of the guide portion a second fuel-filled space. Due to the sealing guide, only highly throttled fuel can flow from one fuel-filled space into the other through the annular gap formed between the piston-shaped component and the wall of the bore, the fuel forming a lubricating film in the annular gap.
  • the valve needle in the bore moves in the longitudinal direction. This can lead to wear between the valve needle and the wall of the bore.
  • various measures such as structures and coatings of the valve needle, are known.
  • A1 groove-like grooves are shown on the guide portion of the valve needle, which are formed there in various depths and widths and in various arrangements.
  • the first and the second fuel-filled space the fuel injection valve in its function and the pressures occurring therein are unequal and that the valve needle moves, for example, in the two longitudinal directions each with different speeds.
  • the lubricating film between the guide portion of the valve needle and der.Wand the bore is not always optimally formed.
  • a fuel injection pump in which a pump piston is driven by a camshaft and thereby compressing fuel in a pressure chamber.
  • the camshaft is mounted in lubricating oil, which also lubricates the pump piston.
  • grooves are provided on the pump piston to prevent the oil from rising on the pump piston into the pressure chamber.
  • the fuel injection valve for internal combustion engines has the advantage that between the guide portion of the valve needle and the wall of the bore always an optimum fuel lubricating film is formed, which minimizes the friction of the valve needle in the bore.
  • at least approximately in the tangential direction runs at the guide portion of the valve needle at least one recess which extends at least over part of the component circumference.
  • the recess has an asymmetrical cross-section, so that the different conditions, as they prevail in the one or the other longitudinal direction in the movement of the valve needle, is taken into account.
  • the recess has a V-shaped cross-section viewed in the longitudinal direction of the valve needle, wherein one flank of the cross-section is shorter than the other flank.
  • the valve needle can be achieved an optimization of the lubricating properties in the annular gap between the valve needle and the wall of the bore.
  • a plurality of recesses are formed on the valve needle, each having a V-shaped cross section, wherein the shorter edge of a recess to the other alternately facing the first and the second space.
  • the transition from the surface of the guide portion of the valve needle to the shorter edge of the recess is sharp-edged, while the transition of the surface of the valve needle to the longer edge of the V-shaped recess is rounded. This refinement of the transitions makes it possible to achieve further optimization of the lubricating properties.
  • flanks of the V-shaped recess have a length of 0.03 mm to 1 mm. This microstructuring allows the lubrication properties to be adapted to high-precision valve needle guides such as those used in fuel injectors used in auto-ignition internal combustion engines.
  • FIG. 1 an inventive fuel injection valve is shown having a housing 1.
  • the housing 1 comprises a valve body 2 and a valve holding body 4, which abut each other and are pressed against each other by a device not shown in the drawing.
  • a bore 3 is formed, which is closed at its combustion chamber end by a substantially conical valve seat 9.
  • at least one injection opening 11 is formed, which connects the bore 3 with the combustion chamber of the internal combustion engine.
  • a valve needle 5 is arranged, which valve needle 5 has a longitudinal axis 6 and in a guide portion 103 of the bore 3 with a guide portion 105 is guided sealing.
  • the valve needle 5 tapers the valve seat 9 to form a pressure shoulder 13 and merges at its combustion chamber end into a substantially conical valve sealing surface 7, which interacts with the valve seat 9.
  • the interaction takes place here in such a way that upon contact of the valve sealing surface 7 on the valve seat 9, the injection port 11 is closed against the bore 3, while lifted from the valve seat 9 valve sealing surface 7, the injection port 11 is released.
  • a first fuel-filled space 19 is arranged at the level of the pressure shoulder 13, which is designed as a pressure chamber in the valve body 2 and continues as a valve needle 5 surrounding the annular channel to the valve seat 9.
  • the pressure chamber 19 can be filled with fuel at high pressure via a feed channel 25 extending in the valve body 2 and in the valve holding body 4.
  • the bore 3 is adjacent to a second fuel-filled space 15 formed in the valve holding body 4, which space is designed as a leakage oil space in this exemplary embodiment.
  • the leakage oil chamber 15 is in this case permanently connected to a leakage oil system, which is not shown in the drawing and which ensures that the leakage oil chamber 15 is always depressurized. At least temporarily, therefore, there is a large pressure difference between the first chamber formed as a pressure chamber 19 and formed as a leakage oil chamber second space 15. Between the valve needle 5 and the wall of the bore 3 remains an annular gap 17 through which a certain, strongly throttled fuel flow from the pressure chamber 19th takes place in the leakage oil chamber 15.
  • FIG. 2 shows an enlargement of the section designated II, wherein in FIG. 2 Both the valve body 2 and the valve needle 5 and its guide portion 105 are shown in section.
  • the recess 30 has a V-shaped cross section, which is formed by a first flank 38 and a second flank 40.
  • the first flank 38 is in this case shorter than the second flank 40, so that the first flank 38 with the longitudinal axis 6 of the valve needle 5 includes a larger angle than the second flank 40.
  • the first flank 38 and the second flank 40 meet in a crest line 34, at which the recess 30 has the greatest depth t.
  • the apex line 34 may hereby be sharp-edged or rounded.
  • the first flank 38 has an extension a and the second flank 40 an extension b, wherein the recesses 30 have a distance d from each other.
  • the ratio of a to b can be varied in large ranges to adapt the lubricating properties of the recesses 30 to the surfaces of the bore wall 3 and the valve needle 5 or the size of the annular gap 17.
  • a first Transition edge 32 is formed, as well as at the transition of the guide portion 105 to the second flank 40, a second transition edge 36.
  • the pressure chamber 19 facing first transition edge 32 is formed as a sharp-edged transition, which is not rounded.
  • the second transition edge 36 is rounded. This makes it possible, as can be demonstrated both in the simulation and in the experiment, to optimize the lubricating properties of the recess 30.
  • FIG. 3 a further embodiment of the recesses 30 according to the invention is shown.
  • the recesses 30 correspond in their dimensions and in the formation of the first flank 38 and the second flank 40 to the recesses in FIG. 2
  • the adjacent recesses 30 have a different orientation. That is, in the one recess 30, the first short edge 38 faces the pressure chamber 19 and faces away from the pressure chamber 19 in the adjacent recess 30.
  • Such an alternating arrangement of the recesses 30 is particularly advantageous when the pressure difference from the first space 19 to the second space 15 is not very large.
  • the first transition edge 32 is formed here sharp-edged, while the second transition edge 36 is rounded.
  • the dimensions a and b of the first flank 38 and the second flank 40 can be varied within wide limits. It can also be provided to set the axial extent a of the first flank 38 equal to 0, so that the first flank 38 is arranged in a radial plane of the longitudinal axis 6 of the valve needle 5. It can also be provided that the flanks 38 and 40 are not straight, but assume a convex or concave curvature, which may be advantageous in certain circumstances.
  • the dimensions of the recesses 30 are as follows: The axial extent of the flanks 38 and 40 in the direction of the longitudinal axis 6 of the valve needle 5 is 0.03 to 1 mm, preferably 0.02 to 0.1 mm. The depth t of the recesses 30 is less than 0.1 mm, preferably 0.001 to 0.04 mm. The distance d of the recesses 40 from each other is 0.05 to 1 mm.
  • the recesses 30 are not formed as annular grooves that cover the entire circumference of the piston-shaped component, which is designed here as a valve needle 5, surrounded, but only a portion of the circumference. Furthermore, it can be provided that the depth t of the recesses 30 varies with the circumference.
  • FIG. 4 represented where a cross section through the valve needle 5 along the line IV-IV of FIG. 1 is shown.
  • the recess 30 has here at one point a depth of 0, wherein the depth of the recess 30 increases over the circumference until it assumes a maximum value on the opposite side of the valve needle 5. Another example is in FIG.
  • FIG. 5 represented where the recess 30 in cross section has a crescent-shaped contour, so that the depth t in this case also ranges from 0 to a maximum value.
  • FIG. 6 shows a further embodiment of the recess 30, wherein the recess 30 extends here only over about 1/4 of the circumference. However, it has a constant depth t. If a plurality of recesses 30 are provided on the valve needle 5 and cover them in each case only part of the circumference of the guide section 105 of the valve needle 5, then these recesses 30 can be distributed over the circumference of the guide section 105.
  • FIG. 7 shows the cross section of the guide portion 105 of the valve needle 5 at a designed as an annular groove recess 30 which has the same depth t over the entire circumference.
  • the described forms of the recesses 30 may be formed both on the piston-shaped component 5 or its guide portion 105 or on the inner wall of the bore 3. It can also be provided to form such structuring of the recesses on both surfaces, that is to say both on the inside of the bore 3 and on the guide surface 105 of the piston-shaped component 5. It may likewise be provided that the recesses 30 designed as grooves do not exactly fit in tangential direction of the piston-shaped component 5, but in a more or less large angle to the longitudinal axis of the piston-shaped component 5, for example 5 ° to 10 °.
  • recesses 30 In addition to the formation of recesses 30 according to the invention on valve needles of fuel injection valves, it can also be provided to form such recesses on other piston-shaped components which are guided in a bore and in which the friction in the bore is to be reduced. In particular, it is advantageous to form such recesses when the first and the second spaces filled with fuel or another liquid have a significantly different pressure from each other.

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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)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Eine solche Kraftstoffeinspritzventil ist beispielsweise aus der Schrift DE 198 20 264 A1 bekannt. Das Kraftstoffeinspritzventil weist ein Gehäuse auf, in dem in einer Bohrung eine Ventilnadel längsverschiebbar angeordnet ist. Die Ventilnadel wird in einem Führungsabschnitt der Bohrung dichtend in dieser geführt. An einem Ende des Führungsabschnitts schließt sich an diesen ein erster kraftstoffgefüllter Raum an und an das andere Ende des Führungsabschnitts ein zweiter kraftstoffgefüllter Raum. Aufgrund der dichtenden Führung kann nur stark gedrosselt Kraftstoff durch den zwischen dem kolbenförmigen Bauteil und der Wand der Bohrung ausgebildeten Ringspalt von einem kraftstoffgefüllten Raum in den anderen fließen, wobei der Kraftstoff im Ringspalt einen Schmierfilm bildet.The invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is for example from the Scriptures DE 198 20 264 A1 known. The fuel injection valve has a housing in which a valve needle is arranged to be longitudinally displaceable in a bore. The valve needle is guided in a guide portion of the bore sealingly in this. At one end of the guide portion, a first fuel-filled space adjoins this and at the other end of the guide portion a second fuel-filled space. Due to the sealing guide, only highly throttled fuel can flow from one fuel-filled space into the other through the annular gap formed between the piston-shaped component and the wall of the bore, the fuel forming a lubricating film in the annular gap.

In dem Kraftstoffeinspritzventil für Brennkraftmaschinen bewegt sich die Ventilnadel in der Bohrung in Längsrichtung. Hierdurch kann es zu einem Verschleiß zwischen der Ventilnadel und der Wand der Bohrung kommen. Um den Verschleiß zu minimieren, insbesondere dann, wenn zwischen dem ersten und dem zweiten kraftstoffgefüllten Raum eine Druckdifferenz herrscht, sind verschiedene Maßnahmen, wie beispielsweise Strukturierungen und Beschichtungen der Ventilnadel, bekannt. In der DE 198 20 264 A1 sind rillenartige Nuten am Führungsabschnitt der Ventilnadel gezeigt, die dort in verschiedenen Tiefen und Breiten und in verschiedenen Anordnungen ausgebildet sind. Hierbei wird jedoch nicht berücksichtigt, dass der erste und der zweite kraftstoffgefüllte Raum des Kraftstoffeinspritzventils in seiner Funktion und den darin auftretenden Drücken ungleich sind und dass sich die Ventilnadel beispielsweise in die beiden Längsrichtungen jeweils mit unterschiedlicher Geschwindigkeit bewegt. Hierdurch ist der Schmierfilm zwischen dem Führungsabschnitt der Ventilnadel und der.Wand der Bohrung nicht immer optimal ausgebildet.In the fuel injection valve for internal combustion engines, the valve needle in the bore moves in the longitudinal direction. This can lead to wear between the valve needle and the wall of the bore. In order to minimize the wear, in particular when there is a pressure difference between the first and the second fuel-filled space, various measures, such as structures and coatings of the valve needle, are known. In the DE 198 20 264 A1 groove-like grooves are shown on the guide portion of the valve needle, which are formed there in various depths and widths and in various arrangements. However, this does not take into account that the first and the second fuel-filled space the fuel injection valve in its function and the pressures occurring therein are unequal and that the valve needle moves, for example, in the two longitudinal directions each with different speeds. As a result, the lubricating film between the guide portion of the valve needle and der.Wand the bore is not always optimally formed.

Aus der EP 0 534 771 A1 ist eine Kraftstoffeinspritzpumpe bekannt, bei der ein Pumpkolben von einer Nockenwelle angetrieben wird und dabei Kraftstoff in einem Druckraum komprimiert. Die Nockenwelle ist in Schmieröl gelagert, welches auch den Pumpkolben schmiert. Um zu verhindern, dass sich das Schmieröl mit dem Kraftstoff mischt, sind am Pumpkolben Nuten vorgesehen, die das Aufsteigen des Schmieröls am Pumpkolben in den Druckraum verhindern sollen.From the EP 0 534 771 A1 a fuel injection pump is known in which a pump piston is driven by a camshaft and thereby compressing fuel in a pressure chamber. The camshaft is mounted in lubricating oil, which also lubricates the pump piston. In order to prevent the lubricating oil from mixing with the fuel, grooves are provided on the pump piston to prevent the oil from rising on the pump piston into the pressure chamber.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen weist demgegenüber den Vorteil auf, dass zwischen dem Führungsabschnitt der Ventilnadel und der Wand der Bohrung stets ein optimaler Kraftstoffschmierfilm gebildet wird, der die Reibung der Ventilnadel in der Bohrung minimiert. Zu diesem Zweck verläuft am Führungsabschnitt der Ventilnadel zumindest näherungsweise in tangentialer Richtung zumindest eine Ausnehmung, die sich zumindest über einen Teil des Bauteilumfangs erstreckt. In Längsrichtung der Ventilnadel weist die Ausnehmung einen asymmetrischen Querschnitt auf, so dass den unterschiedlichen Bedingungen, wie sie bei der Bewegung der Ventilnadel in die eine beziehungsweise die andere Längsrichtung herrschen, Rechnung getragen wird.The fuel injection valve for internal combustion engines according to the invention has the advantage that between the guide portion of the valve needle and the wall of the bore always an optimum fuel lubricating film is formed, which minimizes the friction of the valve needle in the bore. For this purpose, at least approximately in the tangential direction runs at the guide portion of the valve needle at least one recess which extends at least over part of the component circumference. In the longitudinal direction of the valve needle, the recess has an asymmetrical cross-section, so that the different conditions, as they prevail in the one or the other longitudinal direction in the movement of the valve needle, is taken into account.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung weist die Ausnehmung einen in Längsrichtung der Ventilnadel gesehen V-förmigen Querschnitt auf, wobei eine Flanke des Querschnittes kürzer ist als die andere Flanke. Je nach Orientierung der Flanken bezüglich der Längsrichtung der Ventilnadel kann eine Optimierung der Schmiereigenschaften im Ringspalt zwischen der Ventilnadel und der Wand der Bohrung erreicht werden.In an advantageous embodiment of the subject matter of the invention, the recess has a V-shaped cross-section viewed in the longitudinal direction of the valve needle, wherein one flank of the cross-section is shorter than the other flank. Depending on the orientation of the flanks with respect to the longitudinal direction the valve needle can be achieved an optimization of the lubricating properties in the annular gap between the valve needle and the wall of the bore.

In einer weiteren vorteilhaften Ausgestaltung sind an der Ventilnadel mehrere Ausnehmungen ausgebildet, die jeweils einen V-förmigen Querschnitt aufweisen, wobei die kürzere Flanke von einer Ausnehmung zur anderen abwechselnd dem ersten und dem zweiten Raum zugewandt sind. Diese Anordnung hat sich bei bestimmten Konfigurationen bezüglich des Drucks und des Betriebs in der Brennkraftmaschine als vorteilhaft erwiesen.In a further advantageous embodiment, a plurality of recesses are formed on the valve needle, each having a V-shaped cross section, wherein the shorter edge of a recess to the other alternately facing the first and the second space. This arrangement has proven advantageous in certain configurations with respect to pressure and operation in the internal combustion engine.

In einer weiteren vorteilhaften Ausgestaltung ist der Übergang von der Oberfläche des Führungsabschnitts der Ventilnadel zur kürzeren Flanke der Ausnehmung scharfkantig ausgebildet, während der Übergang der Oberfläche der Ventilnadel zur längeren Flanke der V-förmigen Ausnehmung gerundet ist. Durch diese Ausgestaltung der Übergänge lässt sich eine weitere Optimierung der Schmiereigenschaften erreichen.In a further advantageous embodiment, the transition from the surface of the guide portion of the valve needle to the shorter edge of the recess is sharp-edged, while the transition of the surface of the valve needle to the longer edge of the V-shaped recess is rounded. This refinement of the transitions makes it possible to achieve further optimization of the lubricating properties.

In einer vorteilhaften Ausgestaltung weisen die Flanken der V-förmigen Ausnehmung einen Länge von 0,03 mm bis 1 mm auf. Diese Mikrostrukturierung erlaubt eine Anpassung der Schmiereigenschaften an hochpräzise Führungen der Ventilnadel, wie sie beispielsweise in Kraftstoffeinspritzventilen verwendet werden, die für selbstzündende Brennkraftmaschinen Verwendung finden.In an advantageous embodiment, the flanks of the V-shaped recess have a length of 0.03 mm to 1 mm. This microstructuring allows the lubrication properties to be adapted to high-precision valve needle guides such as those used in fuel injectors used in auto-ignition internal combustion engines.

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

Zeichnungdrawing

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

  • Figur 1 ein Kraftstoffeinspritzventil für Brennkraftmaschinen im Längsschnitt,
  • Figur 2 eine Vergrößerung von Figur 1 im mit II bezeichneten Ausschnitt,
  • Figur 3 denselben Ausschnitt wie Figur 2 eines weiteren Ausführungsbeispiels und
  • Figur 4, 5, 6, und 7 einen Querschnitt der in Figur 1 gezeigten Ventilnadel entlang der Linie IV-IV verschiedener Ausführungsbeispiele.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
  • FIG. 1 a fuel injection valve for internal combustion engines in longitudinal section,
  • FIG. 2 an enlargement of FIG. 1 in the section marked II,
  • FIG. 3 same section as FIG. 2 a further embodiment and
  • FIGS. 4, 5, 6, and 7 a cross section of in FIG. 1 shown valve needle along the line IV-IV of various embodiments.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt, das ein Gehäuse 1 aufweist. Das Gehäuse 1 umfasst einen Ventilkörper 2 und einen Ventilhaltekörper 4, die aneinander anliegen und durch eine in der Zeichnung nicht dargestellte Vorrichtung gegeneinander gepresst werden. Im Ventilkörper 2 ist eine Bohrung 3 ausgebildet, die an ihrem brennraumseitigen Ende durch einen im wesentlichen konischen Ventilsitz 9 verschlossen ist. Im Ventilsitz 9 ist wenigstens eine Einspritzöffnung 11 ausgebildet, die die Bohrung 3 mit dem Brennraum der Brennkraftmaschine verbindet. In der Bohrung 3 ist eine Ventilnadel 5 angeordnet, welche Ventilnadel 5 eine Längsachse 6 aufweist und in einem Führungsbereich 103 der Bohrung 3 mit einem Führungsabschnitt 105 dichtend geführt ist. Die Ventilnadel 5 verjüngt sich dem Ventilsitz 9 zu unter Bildung einer Druckschulter 13 und geht an ihrem brennraumseitigen Ende in eine im wesentlichen konische Ventildichtfläche 7 über, die mit dem Ventilsitz 9 zusammenwirkt. Das Zusammenwirken geschieht hierbei in der Weise, dass bei Anlage der Ventildichtfläche 7 am Ventilsitz 9 die Einspritzöffnung 11 gegen die Bohrung 3 verschlossen wird, während bei vom Ventilsitz 9 abgehobene Ventildichtfläche 7 die Einspritzöffnung 11 freigegeben wird. Durch eine radiale Erweiterung der Bohrung 3 ist auf Höhe der Druckschulter 13 ein erster kraftstoffgefüllter Raum 19 angeordnet, der als Druckraum im Ventilkörper 2 ausgebildet ist und der sich als ein die Ventilnadel 5 umgebender Ringkanal bis zum Ventilsitz 9 fortsetzt. Der Druckraum 19 ist hierbei über einen im Ventilkörper 2 und im Ventilhaltekörper 4 verlaufenden Zulaufkanal 25 mit Kraftstoff unter hohem Druck befüllbar.In FIG. 1 an inventive fuel injection valve is shown having a housing 1. The housing 1 comprises a valve body 2 and a valve holding body 4, which abut each other and are pressed against each other by a device not shown in the drawing. In the valve body 2, a bore 3 is formed, which is closed at its combustion chamber end by a substantially conical valve seat 9. In the valve seat 9, at least one injection opening 11 is formed, which connects the bore 3 with the combustion chamber of the internal combustion engine. In the bore 3, a valve needle 5 is arranged, which valve needle 5 has a longitudinal axis 6 and in a guide portion 103 of the bore 3 with a guide portion 105 is guided sealing. The valve needle 5 tapers the valve seat 9 to form a pressure shoulder 13 and merges at its combustion chamber end into a substantially conical valve sealing surface 7, which interacts with the valve seat 9. The interaction takes place here in such a way that upon contact of the valve sealing surface 7 on the valve seat 9, the injection port 11 is closed against the bore 3, while lifted from the valve seat 9 valve sealing surface 7, the injection port 11 is released. By a radial extension of the bore 3, a first fuel-filled space 19 is arranged at the level of the pressure shoulder 13, which is designed as a pressure chamber in the valve body 2 and continues as a valve needle 5 surrounding the annular channel to the valve seat 9. In this case, the pressure chamber 19 can be filled with fuel at high pressure via a feed channel 25 extending in the valve body 2 and in the valve holding body 4.

Am brennraumabgewandten Ende grenzt die Bohrung 3 an einen im Ventilhaltekörper 4 ausgebildeten zweiten kraftstoffgefüllten Raum 15, der in diesem Ausführungsbeispiel als Leckölraum ausgebildet ist. Der Leckölraum 15 ist hierbei ständig mit einem Leckölsystem verbunden, das in der Zeichnung nicht dargestellt ist und das gewährleistet, dass der Leckölraum 15 stets druckentlastet ist. Zumindest zeitweilig besteht also ein großer Druckunterschied zwischen dem als Druckraum ausgebildeten ersten Raum 19 und dem als Leckölraum ausgebildeten zweiten Raum 15. Zwischen der Ventilnadel 5 und der Wand der Bohrung 3 verbleibt ein Ringspalt 17, durch den ein gewisser, stark gedrosselter Kraftstoffstrom vom Druckraum 19 in den Leckölraum 15 stattfindet. Dadurch bildet sich im Ringspalt 17 ein Kraftstoff-Schmierfilm, auf dem die Ventilnadel 5 gleitet. Im Druckraum 19 kann hierbei ein Kraftstoffdruck von 150 MPa und mehr erreicht werden, während im Leckölraum 15 stets ein Druck herrscht, der im wesentlichen dem Atmosphärendruck entspricht.At the end facing away from the combustion chamber, the bore 3 is adjacent to a second fuel-filled space 15 formed in the valve holding body 4, which space is designed as a leakage oil space in this exemplary embodiment. The leakage oil chamber 15 is in this case permanently connected to a leakage oil system, which is not shown in the drawing and which ensures that the leakage oil chamber 15 is always depressurized. At least temporarily, therefore, there is a large pressure difference between the first chamber formed as a pressure chamber 19 and formed as a leakage oil chamber second space 15. Between the valve needle 5 and the wall of the bore 3 remains an annular gap 17 through which a certain, strongly throttled fuel flow from the pressure chamber 19th takes place in the leakage oil chamber 15. This forms in the annular gap 17, a fuel lubricating film on which the valve needle 5 slides. In the pressure chamber 19, in this case, a fuel pressure of 150 MPa and more can be achieved, while in the leakage oil chamber 15, there is always a pressure which substantially corresponds to the atmospheric pressure.

Im Führungsabschnitt 105 der Ventilnadel 5 sind Ausnehmungen 30 angeordnet, die als Ringnuten den gesamten Umfang der Ventilnadel 5 umfassen. Figur 2 zeigt eine Vergrößerung des mit II bezeichneten Ausschnitts, wobei in Figur 2 sowohl der Ventilkörper 2 als auch die Ventilnadel 5 bzw. deren Führungsabschnitt 105 geschnitten dargestellt sind. Wie in Figur 2 zu sehen weist die Ausnehmung 30 einen V-förmigen Querschnitt auf, der durch eine erste Flanke 38 und eine zweite Flanke 40 gebildet wird. Die erste Flanke 38 ist hierbei kürzer als die zweite Flanke 40, so dass die erste Flanke 38 mit der Längsachse 6 der Ventilnadel 5 einen größeren Winkel einschließt als die zweite Flanke 40. Die erste Flanke 38 und die zweite Flanke 40 treffen sich in einer Scheitellinie 34, an der die Ausnehmung 30 die größte Tiefe t aufweist. Die Scheitellinie 34 kann hierbei scharfkantig ausgeführt sein oder auch abgerundet.In the guide portion 105 of the valve needle 5 recesses 30 are arranged, which comprise the entire circumference of the valve needle 5 as annular grooves. FIG. 2 shows an enlargement of the section designated II, wherein in FIG. 2 Both the valve body 2 and the valve needle 5 and its guide portion 105 are shown in section. As can be seen in FIG. 2, the recess 30 has a V-shaped cross section, which is formed by a first flank 38 and a second flank 40. The first flank 38 is in this case shorter than the second flank 40, so that the first flank 38 with the longitudinal axis 6 of the valve needle 5 includes a larger angle than the second flank 40. The first flank 38 and the second flank 40 meet in a crest line 34, at which the recess 30 has the greatest depth t. The apex line 34 may hereby be sharp-edged or rounded.

In Richtung der Längsachse 6 weist die erste Flanke 38 eine Ausdehnung a und die zweite Flanke 40 eine Ausdehnung b auf, wobei die Ausnehmungen 30 einen Abstand d voneinander aufweisen. Das Verhältnis von a zu b kann in großen Bereichen variiert werden, um die Schmiereigenschaften der Ausnehmungen 30 an die Oberflächen der Bohrungswand 3 und der Ventilnadel 5 anzupassen oder an die Größe des Ringspalts 17. Am Übergang des Führungsabschnitts 105 zur ersten Flanke 38 ist eine erste Übergangskante 32 ausgebildet, ebenso am Übergang des Führungsabschnitts 105 zur zweiten Flanke 40 eine zweite Übergangskante 36. Um die Schmiereigenschaften der Ausnehmungen 30 zu optimieren, ist die dem Druckraum 19 zugewandte erste Übergangskante 32 als scharfkantiger Übergang ausgebildet, der nicht gerundet wird. Im Gegensatz dazu ist die zweite Übergangskante 36 gerundet ausgebildet. Hierdurch lassen sich, was sowohl in der Simulation als auch im Versuch nachweisbar ist, die Schmiereigenschaften der Ausnehmung 30 optimieren.In the direction of the longitudinal axis 6, the first flank 38 has an extension a and the second flank 40 an extension b, wherein the recesses 30 have a distance d from each other. The ratio of a to b can be varied in large ranges to adapt the lubricating properties of the recesses 30 to the surfaces of the bore wall 3 and the valve needle 5 or the size of the annular gap 17. At the transition of the guide portion 105 to the first edge 38 is a first Transition edge 32 is formed, as well as at the transition of the guide portion 105 to the second flank 40, a second transition edge 36. In order to optimize the lubricating properties of the recesses 30, the pressure chamber 19 facing first transition edge 32 is formed as a sharp-edged transition, which is not rounded. In contrast, the second transition edge 36 is rounded. This makes it possible, as can be demonstrated both in the simulation and in the experiment, to optimize the lubricating properties of the recess 30.

In Figur 3 ist ein weiteres Ausführungsbeispiel der erfindungsgemäßen Ausnehmungen 30 dargestellt. Die Ausnehmungen 30 entsprechen in ihren Abmessungen und in der Ausbildung der ersten Flanke 38 und der zweiten Flanke 40 den Ausnehmungen in Figur 2, jedoch weisen die benachbarten Ausnehmungen 30 eine unterschiedliche Orientierung auf. Das heißt, in der einen Ausnehmung 30 ist die erste kurze Flanke 38 dem Druckraum 19 zugewandt und in der benachbarten Ausnehmung 30 dem Druckraum 19 abgewandt. Eine solche alternierende Anordnung der Ausnehmungen 30 ist insbesondere dann von Vorteil, wenn der Druckunterschied vom ersten Raum 19 zum zweiten Raum 15 nicht sehr groß ist. Die erste Übergangskante 32 ist auch hier scharfkantig ausgebildet, während die zweite Übergangskante 36 gerundet ausgeführt ist.In FIG. 3 a further embodiment of the recesses 30 according to the invention is shown. The recesses 30 correspond in their dimensions and in the formation of the first flank 38 and the second flank 40 to the recesses in FIG FIG. 2 However, the adjacent recesses 30 have a different orientation. That is, in the one recess 30, the first short edge 38 faces the pressure chamber 19 and faces away from the pressure chamber 19 in the adjacent recess 30. Such an alternating arrangement of the recesses 30 is particularly advantageous when the pressure difference from the first space 19 to the second space 15 is not very large. The first transition edge 32 is formed here sharp-edged, while the second transition edge 36 is rounded.

Wie bereits erwähnt können die Abmessungen a und b der ersten Flanke 38 bzw. der zweiten Flanke 40 in weiten Grenzen variiert werden. Es kann auch vorgesehen sein, die axiale Erstreckung a der ersten Flanke 38 gleich 0 zu setzen, so dass die erste Flanke 38 in einer Radialebene der Längsachse 6 der Ventilnadel 5 angeordnet ist. Es kann auch vorgesehen sein, dass die Flanken 38 bzw. 40 nicht gerade ausgeführt sind, sondern eine konvexe oder konkave Krümmung annehmen, was unter bestimmten Umständen vorteilhaft sein kann.As already mentioned, the dimensions a and b of the first flank 38 and the second flank 40 can be varied within wide limits. It can also be provided to set the axial extent a of the first flank 38 equal to 0, so that the first flank 38 is arranged in a radial plane of the longitudinal axis 6 of the valve needle 5. It can also be provided that the flanks 38 and 40 are not straight, but assume a convex or concave curvature, which may be advantageous in certain circumstances.

Die Abmessungen der Ausnehmungen 30 sind folgendermaßen: Die axialen Erstreckungen der Flanken 38 bzw. 40 in Richtung der Längsachse 6 der Ventilnadel 5 beträgt 0,03 bis 1 mm, vorzugsweise 0,02 bis 0,1 mm. Die Tiefe t der Ausnehmungen 30 ist hierbei kleiner als 0,1 mm, vorzugsweise 0,001 bis 0,04 mm. Der Abstand d der Ausnehmungen 40 voneinander beträgt 0,05 bis 1 mm.The dimensions of the recesses 30 are as follows: The axial extent of the flanks 38 and 40 in the direction of the longitudinal axis 6 of the valve needle 5 is 0.03 to 1 mm, preferably 0.02 to 0.1 mm. The depth t of the recesses 30 is less than 0.1 mm, preferably 0.001 to 0.04 mm. The distance d of the recesses 40 from each other is 0.05 to 1 mm.

Es kann auch vorgesehen sein, dass die Ausnehmungen 30 nicht als Ringnuten ausgebildet sind, die den gesamten Umfang des kolbenförmigen Bauteils, das hier als Ventilnadel 5 ausgebildet ist, umgeben, sondern nur einen Teil des Umfangs. Weiter kann es vorgesehen sein, dass die Tiefe t der Ausnehmungen 30 mit dem Umfang variiert. Ein entsprechendes Ausführungsbeispiel ist in Figur 4 dargestellt, wo ein Querschnitt durch die Ventilnadel 5 entlang der Linie IV-IV der Figur 1 gezeigt ist. Die Ausnehmung 30 weist hier an einem Punkt eine Tiefe von 0 auf, wobei sich die Tiefe der Ausnehmung 30 über den Umfang erhöht, bis sie an der gegenüberliegenden Seite der Ventilnadel 5 einen Maximalwert annimmt. Ein weiteres Beispiel ist in Figur 5 dargestellt, wo die Ausnehmung 30 im Querschnitt eine sichelförmige Kontur aufweist, so dass die Tiefe t in diesem Fall ebenfalls von 0 bis zu einem Maximalwert reicht. Figur 6 zeigt ein weiteres Ausführungsbeispiel der Ausnehmung 30, wobei sich die Ausnehmung 30 hier nur über etwa 1/4 des Umfangs erstreckt. Sie weist jedoch eine konstante Tiefe t auf. Sind mehrere Ausnehmungen 30 an der Ventilnadel 5 vorgesehen und bedecken diese jeweils nur einen Teil des Umfangs des Führungsabschnitts 105 der Ventilnadel 5, so können diese Ausnehmungen 30 über den Umfang des Führungsabschnitts 105 verteilt angeordnet sein. Figur 7 zeigt den Querschnitt des Führungsabschnitts 105 der Ventilnadel 5 bei einer als Ringnut ausgeführten Ausnehmung 30, die über den gesamten Umfang dieselbe Tiefe t aufweist.It can also be provided that the recesses 30 are not formed as annular grooves that cover the entire circumference of the piston-shaped component, which is designed here as a valve needle 5, surrounded, but only a portion of the circumference. Furthermore, it can be provided that the depth t of the recesses 30 varies with the circumference. A corresponding embodiment is in FIG. 4 represented where a cross section through the valve needle 5 along the line IV-IV of FIG. 1 is shown. The recess 30 has here at one point a depth of 0, wherein the depth of the recess 30 increases over the circumference until it assumes a maximum value on the opposite side of the valve needle 5. Another example is in FIG. 5 represented where the recess 30 in cross section has a crescent-shaped contour, so that the depth t in this case also ranges from 0 to a maximum value. FIG. 6 shows a further embodiment of the recess 30, wherein the recess 30 extends here only over about 1/4 of the circumference. However, it has a constant depth t. If a plurality of recesses 30 are provided on the valve needle 5 and cover them in each case only part of the circumference of the guide section 105 of the valve needle 5, then these recesses 30 can be distributed over the circumference of the guide section 105. FIG. 7 shows the cross section of the guide portion 105 of the valve needle 5 at a designed as an annular groove recess 30 which has the same depth t over the entire circumference.

Die beschriebenen Formen der Ausnehmungen 30 können sowohl auf dem kolbenförmigen Bauteil 5 beziehungsweise dessen Führungsabschnitt 105 oder auch an der Innenwand der Bohrung 3 ausgebildet sein. Es kann auch vorgesehen sein, derartige Strukturierungen der Ausnehmungen an beiden Flächen auszubilden, also sowohl an der Innenseite der Bohrung 3 als auch an der Führungsfläche 105 des kolbenförmigen Bauteils 5. Ebenso kann es vorgesehen sein, dass die als Nuten ausgebildeten Ausnehmungen 30 nicht exakt in tangentialer Richtung des kolbenförmigen Bauteils 5 verlaufen, sondern in einem mehr oder weniger großen Winkel zur Längsachse des kolbenförmigen Bauteils 5, beispielsweise 5° bis 10°.The described forms of the recesses 30 may be formed both on the piston-shaped component 5 or its guide portion 105 or on the inner wall of the bore 3. It can also be provided to form such structuring of the recesses on both surfaces, that is to say both on the inside of the bore 3 and on the guide surface 105 of the piston-shaped component 5. It may likewise be provided that the recesses 30 designed as grooves do not exactly fit in tangential direction of the piston-shaped component 5, but in a more or less large angle to the longitudinal axis of the piston-shaped component 5, for example 5 ° to 10 °.

Neben der Ausbildung von erfindungsgemäßen Ausnehmungen 30 an Ventilnadeln von Kraftstoffeinspritzventilen kann es auch vorgesehen sein, derartige Ausnehmungen an sonstigen kolbenförmigen Bauteilen auszubilden, die in einer Bohrung geführt sind und bei denen die Reibung in der Bohrung reduziert werden soll. Insbesondere ist es vorteilhaft, derartige Ausnehmungen dann auszubilden, wenn der erste und der zweite mit Kraftstoff oder einer sonstigen Flüssigkeit gefüllte Raum einen voneinander deutlich verschiedenen Druck aufweisen.In addition to the formation of recesses 30 according to the invention on valve needles of fuel injection valves, it can also be provided to form such recesses on other piston-shaped components which are guided in a bore and in which the friction in the bore is to be reduced. In particular, it is advantageous to form such recesses when the first and the second spaces filled with fuel or another liquid have a significantly different pressure from each other.

Claims (11)

  1. Fuel injection valve for an internal combustion engine having a housing (1), in which a valve needle (5) is arranged in a longitudinally displaceable manner in a hole (3), said valve needle being sealingly guided in the hole (3) by means of a guide section (105), the guide section (105) being adjacent at one end to a first fuel-filled chamber (19) and at its other end to a second fuel-filled chamber (15), and at least one recess (30) running at least approximately in the circumferential direction being formed in the guide section (105) of the valve needle (5), said recess extending at least over part of the circumference of the valve needle (5), characterized in that the recess (30) has an asymmetric cross section, as seen in the longitudinal direction of the valve needle.
  2. Fuel injection valve according to Claim 1, characterized in that the at least one recess (30) has a V-shaped cross section resulting in the formation of a first flank (38) and a second flank (40), with the first flank (38) being shorter than the second flank (40).
  3. Fuel injection valve according to Claim 2, characterized in that a plurality of recesses (30) are formed on the piston-shaped component (5), where with two recesses in succession, the longer flanks (40) and the shorter flanks (38) of the recess (30) are adjacent to one another.
  4. Fuel injection valve according to Claim 2, characterized in that the transition from the surface of the piston-shaped component (5) to the shorter flank (38) of the recess (30) is of sharp-edged design while the transition of the surface of the piston-shaped component (5) to the longer flank (40) is rounded.
  5. Fuel supply device according to one of claims 2, 3 or 4, characterized in that the flanks (38; 40) have an extent of 0.03 mm to 1 mm in the longitudinal direction of the piston-shaped component (5).
  6. Fuel injection valve according to Claim 1, characterized in that the depth of the recess (30) varies over the circumference of the piston-shaped component (5).
  7. Fuel injection valve according to Claim 1, characterized in that the depth (t) of the at least one recess is less than 0.1 mm.
  8. Fuel injection valve according to Claim 7, characterized in that the depth (t) of the recess is 0.001 to 0.04 mm.
  9. Fuel injection valve according to Claim 1, characterized in that in the first chamber (19) a higher pressure than in the second chamber (15) prevails at least temporarily.
  10. Fuel injection valve according to Claim 9, characterized in that the pressure difference from the first chamber (19) to the second chamber (15) is at least temporarily more than 50 MPa.
  11. Fuel injection valve according to Claim 1, characterized in that the first chamber is a pressure chamber (19) which can be filled with fuel under high pressure and the second chamber is an overflow oil chamber (15) which is connected to an overflow oil device.
EP02754314A 2001-07-07 2002-07-04 Fuel injection valve for internal combustion engines Expired - Lifetime EP1407133B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10133166A DE10133166A1 (en) 2001-07-07 2001-07-07 Fuel injection valve for internal combustion engines
DE10133166 2001-07-07
PCT/DE2002/002443 WO2003004865A1 (en) 2001-07-07 2002-07-04 Fuel injection valve for internal combustion engines

Publications (2)

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EP1407133A1 EP1407133A1 (en) 2004-04-14
EP1407133B1 true EP1407133B1 (en) 2010-10-13

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US (1) US7143965B2 (en)
EP (1) EP1407133B1 (en)
JP (1) JP4204462B2 (en)
KR (1) KR20030036754A (en)
CN (1) CN1308592C (en)
BR (1) BR0205718A (en)
DE (2) DE10133166A1 (en)
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DE50214714D1 (en) 2010-11-25
KR20030036754A (en) 2003-05-09
WO2003004865A1 (en) 2003-01-16
PL370638A1 (en) 2005-05-30
EP1407133A1 (en) 2004-04-14
DE10133166A1 (en) 2003-01-16
JP2004521264A (en) 2004-07-15
CN1308592C (en) 2007-04-04
JP4204462B2 (en) 2009-01-07
BR0205718A (en) 2003-07-22
CN1464941A (en) 2003-12-31
PL201527B1 (en) 2009-04-30
US7143965B2 (en) 2006-12-05
US20040079818A1 (en) 2004-04-29

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