WO2006042488A1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
WO2006042488A1
WO2006042488A1 PCT/DE2004/002341 DE2004002341W WO2006042488A1 WO 2006042488 A1 WO2006042488 A1 WO 2006042488A1 DE 2004002341 W DE2004002341 W DE 2004002341W WO 2006042488 A1 WO2006042488 A1 WO 2006042488A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
ball
valve piece
fuel injector
seat
Prior art date
Application number
PCT/DE2004/002341
Other languages
German (de)
French (fr)
Inventor
Axel Schnaufer
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to PCT/DE2004/002341 priority Critical patent/WO2006042488A1/en
Publication of WO2006042488A1 publication Critical patent/WO2006042488A1/en

Links

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
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a fuel injector according to the preamble of claim 1.
  • Fuel injectors of the genus in modern art are preferably used in modern high-pressure injection systems (common rail systems).
  • Such fuel injectors comprise a valve piece arranged in an injector body with a nozzle opening which can be closed by means of a valve ball.
  • the valve ball is guided in a ball guide and is pressurized by a loaded by a compression spring armature.
  • armature stroke which has an adverse effect on the design of the injection quantity, can occur with these extremely heavily loaded fuel injectors.
  • the change in the armature stroke also undesirably changes the injection quantity of the injected fuel. Investigations have shown that this change in the armature stroke is due to wear or material removal between the armature and the ball guide or between the valve ball and the valve piece.
  • the valve piece of the fuel injector is subjected to high pressure from both inside and outside.
  • the invention is based on the recognition that while the valve seat of the valve ball is deformed in the vertical and radial directions and is forced as a result of this deformation in a rotary motion. This forced by the pressure load movement leads to the observed signs of wear, which prevent the supply of the most constant injection quantity.
  • the material wear can be significantly reduced by the fact that the rotary motion promoting the wear is largely reduced. This is achieved by means of the solution according to the invention essentially in that the radial component of the movement of the valve seat is significantly reduced.
  • valve seat is arranged substantially in a plane which is aligned with a plane containing the bearing surface of the valve seat.
  • the reduced wear can significantly increase the life of these highly loaded fuel injectors, which lowers the maintenance cost of vehicles equipped with them.
  • the proposed improvement is also possible without changing the outer geometry of the valve seat, so that complex and expensive adjustment work on the valve seat receiving injector omitted.
  • FIG. 2 shows the valve piece of a conventional fuel injector
  • FIG. 3 shows the valve piece of a fuel injector designed according to the invention
  • Figure 4 is a diagram showing the radial deformation of the valve seat in
  • FIG. 1 shows a part of a fuel injector 1 in a longitudinal section.
  • a fuel injector 1 is used in modern high-pressure injection systems (common rail systems) for the injection of fuel into the cylinder of an internal combustion engine.
  • the fuel injector 1 comprises an injector body 2 in which a valve piece 3 (FIG. 2, FIG. 3) is mounted.
  • the valve piece 3 has a concentric bore which is in operative connection with a valve ball 6.
  • the bore and the valve ball form a valve which, depending on the position of the valve ball 6, is open or closed.
  • the valve ball 6 rests in a ball seat and is guided in its movement by a ball guide 4, which is arranged in a concentric recess of the valve piece 3.
  • valve ball is acted upon by an armature 5 with pressure, which is applied by a compression spring 7, on the one hand on a plate 5 connected to the armature 5 and on the other hand on the Injector body 2 is supported.
  • the armature 5 is movable by appropriate control of an actuator (piezoelectric actuator or solenoid valve) against the force exerted by the compression spring 7 compressive force and thus enables the lifting of the valve ball 6 from its ball seat 10. After lifting the valve ball 6 from its ball seat 10 can fuel through the Pass hole in the valve piece 3.
  • FIG. 2 shows the valve piece 3 of a conventional fuel injector 1 partly in longitudinal section.
  • the valve member 3 is formed substantially sleeve-shaped and has a centrally disposed bore 13 with a stepped diameter.
  • the two end pieces of the valve piece 3 have a different outer diameter.
  • a step new is formed, which has a bearing surfaces eighth. With this bearing surface, the valve piece 3 rests on a shape-adapted step in the injector body (FIG. 1).
  • a recess is arranged, which is initially conical and then merges into a cylindrical region.
  • the conical area forms the ball seat 10 for the valve ball 6.
  • the cylindrical area 11 adjoins this ball seat 10.
  • FIG. 3 shows the valve piece 3 of a fuel injector designed according to the invention.
  • the outer geometry of this inventively designed valve piece 3 is consistent with that of the valve piece shown in Figure 2, known. In particular, as far as the outer contour and the position of the bearing surface 8 are concerned.
  • This offers the advantage that the inventively designed valve pieces are fully compatible with the already known valve pieces ( Figure 2) and can be installed without further adaptation work in a conventional fuel injector 1.
  • the resulting advantages in terms of storage and cost savings are obvious.
  • the valve piece 3 according to FIG. 3 again has a recess in its end piece with the larger diameter, which recess is composed of a region 12 with a conical surface and a region 11 with a cylindrical surface.
  • the area 12 also receives the ball seat 10 for the valve ball 6.
  • the ball seat 10 is substantially further away from the end face 14 of the valve piece and lies as close as possible to a plane which also comprises the bearing surface 8.
  • this is achieved in that the conical region 12 is displaced substantially deeper in the direction of the center of the valve piece 3.
  • a cylindrical region 11 which has a substantially greater height than in the known valve piece (FIG. 2), now adjoins the conical region 12.
  • valve piece has a plane which is parallel to the support surface 8 of the valve member 3, that is perpendicular to the plane, and marks the transition between the conical portion 12 and the cylindrical portion 11, a distance al from the support surface. 8
  • this distance is a2, where a> a2.
  • the distance a2 is less than 3 mm, in particular between 1.8 mm and 2.5 mm.
  • said plane E lies approximately at half the height of the step 9 bearing the support surface 8.
  • valve piece according to Figure 3 is characterized by a much better deformation behavior and thus by improved stability. This leads to less material wear and thus to a longer service life. With the inventively designed valve pieces equipped fuel in vectors 1 show a longer life under causes even lower maintenance costs in the operation of a motor vehicle equipped with it.
  • FIG. Figure 4 shows a diagram showing the radial deformation of the ball seat 10 as a function of the position of the ball seat 10 with respect to the support surface 8.
  • distance values are entered in mm for the ball seat 10 on the support surface 8.
  • Y-axis of the graph he is the radial deformation of the ball seat 10 in microns plotted.
  • two measuring points 20 and 30 are entered in the diagram.
  • the measuring point 20 was determined in a conventional valve piece according to FIG. In this valve piece, the ball seat 10 was about 1.5 mm above the support surface 8. When loaded, the valve piece 3 results in a radial deformation of the ball seat between 0.3 and 0.4. microns.
  • the measuring point 30 was determined by measurements on the inventively designed valve piece 3 according to FIG.
  • the ball seat 10 is arranged in a plane which is only slightly removed from the plane containing the support surface 8. The distance is only about 0.5 mm.
  • the inventive solution leads to a significantly improved stability of the valve piece 3.
  • deformation values can still be achieved in the radial direction, which are less than about 0.1 microns.

Abstract

The invention relates to a fuel injector (1) comprising an injector body (2) and a valve piece (3), which is mounted inside the injector body (2) and which, via a contact surface (8), rests against a seat of the injector body (2), and comprising a valve ball (6), which is displaceably mounted in a ball guide, is subjected to the action of pressure by a spring-loaded armature (2), and which is actively connected to a borehole (13) made in the valve piece (3) while forming a ball valve together with this borehole (13). The ball seat (10) of the valve ball (6) is situated inside the valve piece (3) in such a manner that the radial deformation of the valve piece (3), which arises during a closing movement of the valve ball (6), assumes a minimal value.

Description

KraftstofflnjektorKraftstofflnjektor
Technisches GebietTechnical area
Die Erfindung bezieht sich auf einen Kraftstoffinjektor nach dem Oberbegriff des Anspruchs 1. Kraftstoffinjektoren der gattungs gemäßen Art werden bevorzugt in modernen Hochdruckeinspritzsystemen (Common-Rail-Systemen) eingesetzt.The invention relates to a fuel injector according to the preamble of claim 1. Fuel injectors of the genus in modern art are preferably used in modern high-pressure injection systems (common rail systems).
Stand der TechnikState of the art
Derartige Kraftstoffinjektoren umfassen ein in einem Injektorkörper angeordnetes Ventilstück mit einer Düsenöffnung, die mittels einer Ventilkugel verschließbar ist. Die Ventilkugel ist in einer Kugelführung geführt und wird von einem durch eine Druckfeder belasteten Anker mit Druck beaufschlagt. Bei diesen extrem hoch belasteten Kraftstoffinjektoren kann, abhängig von der Betriebsdauer, eine Veränderung des Ankerhubs auftreten, die sich nachteilig auf die Bemessung der Einspritzmenge auswirkt. Durch die Änderung des Ankerhubs verändert sich in unerwünschter Weise auch die Einspritzmenge des eingespritzten Kraftstoffs. Untersuchungen haben ergeben, dass diese Änderung des Ankerhubs auf Verschleiß bzw. Materialabtrag zwischen dem Anker und der Kugelführung bzw. zwischen der Ventilkugel und dem Ventilstück zurückzuführen ist.Such fuel injectors comprise a valve piece arranged in an injector body with a nozzle opening which can be closed by means of a valve ball. The valve ball is guided in a ball guide and is pressurized by a loaded by a compression spring armature. Depending on the operating time, a change in the armature stroke, which has an adverse effect on the design of the injection quantity, can occur with these extremely heavily loaded fuel injectors. The change in the armature stroke also undesirably changes the injection quantity of the injected fuel. Investigations have shown that this change in the armature stroke is due to wear or material removal between the armature and the ball guide or between the valve ball and the valve piece.
Darstellung der ErfindungPresentation of the invention
Das Ventilstück des Kraftstoffinjektors wird im Betrieb der mit den Kraftstoffinjektoren ausgerüsteten Verbrennungskraftmaschine sowohl von innen als auch von außen mit hohem Druck beaufschlagt. Die Erfindung geht von der Erkenntnis aus, dass dabei der Ventilsitz der Ventilkugel in Vertikal- und Radialrichtung verförmt wird und infolge dieser Verformung in eine Drehbewegung gezwungen wird. Diese durch die Druckbelastung erzwungene Bewegung führt zu den beobachteten Verschleißerscheinungen, die die Zuführung einer möglichst konstanten Einspritzmenge verhindern. Nach den Erkenntnissen der Anmelderin lässt sich der Materialverschleiß wesentlich dadurch reduzieren, dass die den Verschleiß fördernde Drehbewegung weitgehend verringert wird. Dies gelingt mittels der erfindungsgemäßen Lösung im Wesentlichen dadurch, dass die Radialkomponente der Bewegung des Ventilsitzes erheblich vermindert wird. Gemäß der erfinderischen Lösung wird dies dadurch erreicht, dass der Ventilsitz im Wesentlichen in einer Ebene angeordnet ist, die mit einer die Auflagefläche des Ventilsitzes enthaltenden Ebene fluchtet. Durch den geringeren Verschleiß kann die Lebensdauer dieser hoch belasteten Kraftstoffinjektoren beträchtlich gesteigert werden, was die Wartungskosten für damit ausgestattete Kraftfahrzeuge senkt. Die vorgeschlagene Verbesserung ist zudem ohne Veränderung der äußeren Geometrie des Ventilsitzes möglich, so dass aufwendige und teure Anpassungsarbeiten an dem den Ventilsitz aufnehmenden Injektorkörper entfallen.During operation of the internal combustion engine equipped with the fuel injectors, the valve piece of the fuel injector is subjected to high pressure from both inside and outside. The invention is based on the recognition that while the valve seat of the valve ball is deformed in the vertical and radial directions and is forced as a result of this deformation in a rotary motion. This forced by the pressure load movement leads to the observed signs of wear, which prevent the supply of the most constant injection quantity. According to the findings of the applicant, the material wear can be significantly reduced by the fact that the rotary motion promoting the wear is largely reduced. This is achieved by means of the solution according to the invention essentially in that the radial component of the movement of the valve seat is significantly reduced. According to the inventive solution, this is achieved in that the valve seat is arranged substantially in a plane which is aligned with a plane containing the bearing surface of the valve seat. The reduced wear can significantly increase the life of these highly loaded fuel injectors, which lowers the maintenance cost of vehicles equipped with them. The proposed improvement is also possible without changing the outer geometry of the valve seat, so that complex and expensive adjustment work on the valve seat receiving injector omitted.
Zeichnungdrawing
Anhand der Zeichnung wird die Erfindung nachstehend näher erläutert.Reference to the drawings, the invention will be explained in more detail below.
Es zeigt:It shows:
Figur 1 einen Kraftstoffinjektor in einem Längsschnitt,1 shows a fuel injector in a longitudinal section,
Figur 2 das Ventilstück eines herkömmlichen Kraftstoffinjektors,FIG. 2 shows the valve piece of a conventional fuel injector,
Figur 3 das Ventilstück eines erfindungsgemäß ausgebildeten Kraftstoffiηjektors,FIG. 3 shows the valve piece of a fuel injector designed according to the invention,
Figur 4 ein Diagramm mit Darstellung der Radialverformung des Ventilsitzes inFigure 4 is a diagram showing the radial deformation of the valve seat in
Abhängigkeit von der Lage des Kugelsitzes.Dependence on the position of the ball seat.
Figur 1 zeigt einen Teil eines Kraftstoffinjektors 1 in einem Längsschnitt. Derartige Kraftstoffinjektoren werden in modernen Hochdruckeinspritzsystemen (Common-Rail- Systemen) für die Einspritzung von Kraftstoff in den Zylinder einer Verbrennungskraftmaschine eingesetzt. Der Kraftstoffinjektor 1 umfasst einen Injektorkörper 2, in dem ein Ventilstück 3 (Figur 2, Figur 3) gelagert ist. Das Ventilstück 3 weist eine konzentrische Bohrung auf, die mit einer Ventilkugel 6 in Wirkverbindung steht. Die Bohrung und die Ventilkugel bilden ein Ventil, das, je nach Lage der Ventilkugel 6, geöffnet oder geschlossen ist. Die Ventilkugel 6 ruht in einem Kugelsitz und wird bei ihrer Bewegung von einer Kugelführung 4 geführt, die in einer konzentrischen Ausnehmung des Ventilstücks 3 angeordnet ist. Die Ventilkugel ist von einem Anker 5 mit Druck beaufschlagt, der von einer Druckfeder 7 aufgebracht wird, die sich einerseits an einem mit dem Anker 5 verbundenen Teller 5a und andererseits an dem Injektorkörper 2 abstützt. Der Anker 5 ist durch entsprechende Steuerung eines Aktors (Piezoaktor oder Magnetventil) gegen die von der Druckfeder 7 ausgeübte Druckkraft bewegbar und ermöglicht so das Abheben der Ventilkugel 6 von ihrem Kugelsitz 10. Nach dem Abheben der Ventilkugel 6 von ihrem Kugelsitz 10 kann Kraftstoff durch die Bohrung in dem Ventilstück 3 hindurchtreten.FIG. 1 shows a part of a fuel injector 1 in a longitudinal section. Such fuel injectors are used in modern high-pressure injection systems (common rail systems) for the injection of fuel into the cylinder of an internal combustion engine. The fuel injector 1 comprises an injector body 2 in which a valve piece 3 (FIG. 2, FIG. 3) is mounted. The valve piece 3 has a concentric bore which is in operative connection with a valve ball 6. The bore and the valve ball form a valve which, depending on the position of the valve ball 6, is open or closed. The valve ball 6 rests in a ball seat and is guided in its movement by a ball guide 4, which is arranged in a concentric recess of the valve piece 3. The valve ball is acted upon by an armature 5 with pressure, which is applied by a compression spring 7, on the one hand on a plate 5 connected to the armature 5 and on the other hand on the Injector body 2 is supported. The armature 5 is movable by appropriate control of an actuator (piezoelectric actuator or solenoid valve) against the force exerted by the compression spring 7 compressive force and thus enables the lifting of the valve ball 6 from its ball seat 10. After lifting the valve ball 6 from its ball seat 10 can fuel through the Pass hole in the valve piece 3.
Figur 2 zeigt das Ventilstück 3 eines herkömmlichen Kraftstoffinjektors 1 zum Teil im Längsschnitt. Das Ventilstück 3 ist im Wesentlichen hülsenförmig ausgebildet und weist eine zentrisch angeordnete Bohrung 13 mit abgestuftem Durchmesser auf. Die beiden Endstücke des Ventilstücks 3 weisen einen unterschiedlichen Außendurchmesser auf. An dem Endstück des Ventilstücks 3, das den größeren Außendurchmesser weist, ist eine Stufe neuen ausgebildet, die eine Auflageflächen achte aufweist. Mit dieser Auflagefläche liegt das Ventilstück 3 auf einer formangepassten Stufe in dem Injektorkörper auf (Figur 1). In dem gleichen Endstück ist eine Ausnehmung angeordnet, die zunächst kegelförmig ausgebildet ist und dann in einen zylindrischen Bereich übergeht. Der kegel- förmige Bereich bildet den Kugelsitz 10 für die Ventilkugel 6 der zylindrische Bereich 11 schließt sich an diesen Kugelsitz 10 an. Bei einer Betätigung des Ankers 5 (Figur 1), die zur Folge hat, dass sich die Ventilkugel 6 hin und her bewegt, wird das Ventilstück 3 stark belastet. Insbesondere ergibt sich im Bereich des Kugelsitzes 10 eine starke Belastung in Radialrichtung, die wie schon erläutert, einen vergleichsweise starken Verschleiß zur Folge hat. Dieser Nachteil wird durch die erfindungsgemäße Lösung vermieden, die nun anhand von Figur 3 erläutert wird.Figure 2 shows the valve piece 3 of a conventional fuel injector 1 partly in longitudinal section. The valve member 3 is formed substantially sleeve-shaped and has a centrally disposed bore 13 with a stepped diameter. The two end pieces of the valve piece 3 have a different outer diameter. At the end of the valve piece 3, which has the larger outer diameter, a step new is formed, which has a bearing surfaces eighth. With this bearing surface, the valve piece 3 rests on a shape-adapted step in the injector body (FIG. 1). In the same end piece a recess is arranged, which is initially conical and then merges into a cylindrical region. The conical area forms the ball seat 10 for the valve ball 6. The cylindrical area 11 adjoins this ball seat 10. Upon actuation of the armature 5 (Figure 1), which has the consequence that the valve ball 6 moves back and forth, the valve member 3 is heavily loaded. In particular, results in the region of the ball seat 10, a strong load in the radial direction, which, as already explained, has a comparatively heavy wear result. This disadvantage is avoided by the solution according to the invention, which will now be explained with reference to FIG.
Figur 3 zeigt das Ventilstück 3 eines erfindungsgemäß ausgebildeten Kraftstoffinjektors. Die äußere Geometrie dieses erfindungsgemäß ausgebildeten Ventilstücks 3 stimmt mit jener des in Figur 2 dargestellten, bekannten Ventilstücks überein. Insbesondere, was die Außenkontur und die Lage der Auflagefläche 8 betrifft. Dies bietet den Vorteil, dass die erfindungsgemäß ausgestalteten Ventilstücke völlig kompatibel mit den bereits bekannten Ventilstücken (Figur 2) sind und ohne weitere Anpassarbeit in einen herkömmlichen Kraftstoffinjektor 1 einbaubar sind. Die sich daraus ergebenden Vorteile hinsichtlich Lagerhaltung und Kosteneinsparung sind offensichtlich. Auch das Ventilstück 3 gemäß Figur 3 weist wiederum in seinem Endstück mit dem größeren Durchmesser eine Ausnehmung aus, die sich aus einem Bereich 12 mit einer Kegelfläche und einem Bereich 11 mit einer zylindrischen Fläche zusammensetzt. Der Bereich 12 nimmt auch den Kugelsitz 10 für die Ventilkugel 6 auf. Im Unterschied zu dem in Figur 2 dargestellten Ventilstück 3 ist bei der erfindungsgemäßen Ausführungsform des Ventilstücks 3 gemäß Figur 3 der Kugelsitz 10 wesentlich weiter von der Stirnfläche 14 des Ventilstücks entfernt und liegt möglichst nahe an einer Ebene, die auch die Auflagefläche 8 umfasst. Konstruktiv wird dies dadurch erreicht, dass der kegelförmige Bereich 12 wesentlich tiefer in Richtung Mittelpunkt des Ventilstücks 3 verschoben ist. Um dennoch die äußere Geometrie des Ventilstücks 3 beibehalten zu können, schließt sich jetzt an den kegelförmigen Bereich 12 ein zylindrischer Bereich 11 an, der eine wesentlich größere Höhe als bei dem bekannten Ventilstück (Figur 2) aufweist. Bei dem bekannten Ventilstück hat eine Ebene, die parallel zu der Auflagefläche 8 des Ventilstücks 3 verläuft, die also senkrecht auf der Zeichenebene steht, und die den Übergang zwischen dem kegelförmigen Bereich 12 und dem zylindrischen Bereich 11 markiert, einen Abstand al von der Auflagefläche 8. Bei der erfindungsgemäßen Ausführung des Ventilstücks 3 dagegen beträgt dieser Abstand a2, wobei gilt al>a2. In einer bevorzugten Ausführungsform der Erfindung liegt der Abstand a2 unter 3 mm, insbesondere zwischen 1,8 mm und 2,5 mm. Vorzugsweise liegt dabei bei der erfindungsgemäßen Ausführungsform die genannte Ebene E etwa auf halber Höhe der die Auflagefläche 8 tragenden Stufe 9.FIG. 3 shows the valve piece 3 of a fuel injector designed according to the invention. The outer geometry of this inventively designed valve piece 3 is consistent with that of the valve piece shown in Figure 2, known. In particular, as far as the outer contour and the position of the bearing surface 8 are concerned. This offers the advantage that the inventively designed valve pieces are fully compatible with the already known valve pieces (Figure 2) and can be installed without further adaptation work in a conventional fuel injector 1. The resulting advantages in terms of storage and cost savings are obvious. The valve piece 3 according to FIG. 3 again has a recess in its end piece with the larger diameter, which recess is composed of a region 12 with a conical surface and a region 11 with a cylindrical surface. The area 12 also receives the ball seat 10 for the valve ball 6. In contrast to the valve piece 3 shown in FIG. 2, in the embodiment according to the invention of the valve piece 3 according to FIG. 3 the ball seat 10 is substantially further away from the end face 14 of the valve piece and lies as close as possible to a plane which also comprises the bearing surface 8. In terms of design, this is achieved in that the conical region 12 is displaced substantially deeper in the direction of the center of the valve piece 3. In order nevertheless to be able to retain the outer geometry of the valve piece 3, a cylindrical region 11, which has a substantially greater height than in the known valve piece (FIG. 2), now adjoins the conical region 12. In the known valve piece has a plane which is parallel to the support surface 8 of the valve member 3, that is perpendicular to the plane, and marks the transition between the conical portion 12 and the cylindrical portion 11, a distance al from the support surface. 8 In contrast, in the embodiment of the valve piece 3 according to the invention, this distance is a2, where a> a2. In a preferred embodiment of the invention, the distance a2 is less than 3 mm, in particular between 1.8 mm and 2.5 mm. Preferably, in the embodiment according to the invention, said plane E lies approximately at half the height of the step 9 bearing the support surface 8.
Die erfindungsgemäße Ausführungsform eines Ventilstücks nach Figur 3 zeichnet sich durch eine wesentlich besseres Verformungsverhalten und somit durch eine verbesserte Stabilität aus. Dies führt zu einem geringeren Materialverschleiß und damit zu einer höheren Lebensdauer. Mit dem erfindungsgemäß ausgestalteten Ventil Stücke ausgestattete Kraftstoff in Vektoren 1 zeigen eine längere Standzeit unter Ursachen gar durch niedrigere Wartungskosten bei den Betrieb eines damit ausgestattete Kraftfahrzeugs.The inventive embodiment of a valve piece according to Figure 3 is characterized by a much better deformation behavior and thus by improved stability. This leads to less material wear and thus to a longer service life. With the inventively designed valve pieces equipped fuel in vectors 1 show a longer life under causes even lower maintenance costs in the operation of a motor vehicle equipped with it.
Dieses Ergebnis wird durch die Darstellung in Figur 4 verdeutlicht. Figur 4 zeigt ein Diagramm mit Darstellung der Radialverformung des Kugelsitzes 10 in Abhängigkeit von der Lage des Kugelsitzes 10 in Bezug auf die Auflagefläche 8. Auf der X-Achse des Diagramms sind Abstandswerte in mm für den Kugelsitz 10 über der Auflagefläche 8 eingetragen. Auf der Y-Achse des Diagramms ist er die radiale Verformung des Kugelsitzes 10 in μm aufgetragen. Weiterhin sind in dem Diagramm zwei Messpunkte 20 und 30 eingetragen. Der Messepunkt 20 wurde bei einem herkömmlichen Ventilstück gemäß Figur 2 ermittelt. Bei diesem Ventilstück befand sich der Kugelsitz 10 etwa 1,5 mm über der Auflagefläche 8. Bei Belastung des Ventilstücks 3 ergibt sich dabei einer radiale Verformung des Kugelsitzes zwischen 0,3 und 0,4. μm. Der Messepunkt 30 wurde durch Messungen an dem erfindungsgemäß ausgestalteten Ventilstück 3 gemäß Figur 3 ermittelt. Hierbei ist der Kugelsitz 10 in einer Ebene angeordnet, die nur geringfügig von der die Auflagefläche 8 enthaltenden Ebene entfernt ist. Der Abstand beträgt etwa nur 0,5 mm. Wie aus dem Diagramm zu ersehen ist, findet praktisch keine radiale Verformung des Kugelsitzes 10 mehr statt. Dieses Messergebnis belegt überzeugend, dass die erfinderische Lösung zu einer wesentlich verbesserten Stabilität des Ventilstücks 3 führt. Für die Praxis brauchbare Ergebnisse sind auch noch erreichbar, wenn der Kugelsitz 10 zwischen etwa 0,3 mm und 0,8 mm über der Auflagefläche 8 angeordnet ist. Hierbei sind noch Verformungswerte in Radialrichtung erzielbar, die unter etwa 0,1 μm liegen. This result is illustrated by the illustration in FIG. Figure 4 shows a diagram showing the radial deformation of the ball seat 10 as a function of the position of the ball seat 10 with respect to the support surface 8. On the X-axis of the diagram distance values are entered in mm for the ball seat 10 on the support surface 8. On the Y-axis of the graph he is the radial deformation of the ball seat 10 in microns plotted. Furthermore, two measuring points 20 and 30 are entered in the diagram. The measuring point 20 was determined in a conventional valve piece according to FIG. In this valve piece, the ball seat 10 was about 1.5 mm above the support surface 8. When loaded, the valve piece 3 results in a radial deformation of the ball seat between 0.3 and 0.4. microns. The measuring point 30 was determined by measurements on the inventively designed valve piece 3 according to FIG. In this case, the ball seat 10 is arranged in a plane which is only slightly removed from the plane containing the support surface 8. The distance is only about 0.5 mm. As can be seen from the diagram, virtually no radial deformation of the ball seat 10 takes place. This measurement convincingly demonstrates that the inventive solution leads to a significantly improved stability of the valve piece 3. For the practice useful results are still achievable when the ball seat 10 is disposed between about 0.3 mm and 0.8 mm above the support surface 8. In this case, deformation values can still be achieved in the radial direction, which are less than about 0.1 microns.
BezuεszeichenlisteBezuεszeichenliste
1 Kraftstoffinjektor1 fuel injector
2 Injektorkörper2 injector bodies
3 Ventilstück3 valve piece
4 Kugelfuhrung4 ball guidance
5 Anker5 anchors
5a Teller5a plate
6 Ventilkugel6 valve ball
7 Druckfeder7 compression spring
8 Auflagefläche8 contact surface
9 Stufe9 step
10 Kugelsitz10 ball seat
11 Bereich11 area
12 Bereich12 area
13 Bohrung13 hole
14 Stirnfläche14 face
20 Position20 position
30 Position30 position
E Ebene al Abstand a2 Abstand E plane al distance a2 distance

Claims

Patentansprüche claims
1. Kraftstoffmjektor (1) mit einem Injektorkörper (2) und einem in dem Injektorkörper (2) gelagerten Ventilstück (3), das mit einer Auflagefläche (8) auf einem Sitz desAnspruch [en] A fuel injector (1) having an injector body (2) and a valve piece (3) mounted in the injector body (2) and having a bearing surface (8) mounted on a seat of the
Injektorkörpers (2) aufliegt, sowie mit einer in einer Kugelführung (4) beweglich gelagerten und von einem federbelasteten (Druckfeder 7) Anker (5) mit Druck beaufschlagten Ventilkugel (6), die in einem Kugelsitz (10) ruht, wobei die Ventilkugel (6) mit einer in dem Ventilstück (3) angeordneten Bohrung (13) in Wirkverbindung steht und mit dieser Bohrung (13) ein Kugelventil bildet, dadurch gekennzeichnet, dass der Kugelsitz (10) der Ventilkugel (6) derart in dem Ventilstück (3) angeordnet ist, dass die bei einer Schließbewegung der Ventilkugel (6) entstehende Radialverformung des Ventilstücks (3) einen minimalen Wert annimmt.Injector body (2) rests, and with a in a ball guide (4) movably mounted and by a spring-loaded (compression spring 7) armature (5) pressurized valve ball (6) which rests in a ball seat (10), wherein the valve ball ( 6) with a in the valve piece (3) arranged bore (13) is in operative connection and with this bore (13) forms a ball valve, characterized in that the ball seat (10) of the valve ball (6) in the valve piece (3) is arranged, that during a closing movement of the valve ball (6) resulting radial deformation of the valve piece (3) assumes a minimum value.
2. Kraftstoffmjektor nach Anspruch 1, dadurch gekennzeichnet, dass der Kugelsitz (10) der Ventilkugel (6) im Wesentlichen in einer mit der Auflagefläche (8) des Ventilstücks fluchtenden Ebene angeordnet oder nur geringfügig davon entfernt ist.2. Fuel injector according to claim 1, characterized in that the ball seat (10) of the valve ball (6) is arranged substantially in a plane aligned with the bearing surface (8) of the valve piece or only slightly removed therefrom.
3. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kugelsitz (10) in einer Ausnehmung in dem Ventilstück (3) angeordnet ist , wobei die Ausnehmung aus einem im Wesentlichen kegelförmigen Bereich (12) und einem zylinderförmigen Bereich (11) besteht und der zylinderförmige Bereich zu der Stirnfläche (14) des Ventilstücks (3) geöffnet ist.3. Fuel injector according to one of the preceding claims, characterized in that the ball seat (10) is arranged in a recess in the valve piece (3), wherein the recess consists of a substantially conical portion (12) and a cylindrical portion (11) and the cylindrical portion is opened to the end face (14) of the valve piece (3).
4. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der kegelförmige Bereich (12) und der zylinderförmige Bereich (11) der Ausnehmung durch eine Ebene (E) getrennt sind, die im Wesentlichen auf halber Höhe einer die Auflagefläche (8) tragenden Stufe (9) des4. Fuel injector according to one of the preceding claims, characterized in that the conical region (12) and the cylindrical portion (11) of the recess are separated by a plane (E) substantially at half the height of the support surface (8) bearing Stage (9) of the
Ventilstücks (3) liegt.Valve piece (3) is located.
5. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Abstand (a2) zwischen der Ebene (E) und der Auflagefläche (8) weniger als 3 mm beträgt. 5. Fuel injector according to one of the preceding claims, characterized in that the distance (a2) between the plane (E) and the support surface (8) is less than 3 mm.
6. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Abstand (a2) zwischen der Ebene (E) und der Auflagefläche (8) zwischen 1,8 mm und 2,5 mm liegt.6. Fuel injector according to one of the preceding claims, characterized in that the distance (a2) between the plane (E) and the support surface (8) is between 1.8 mm and 2.5 mm.
7. Kraft stoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kugelsitz (10) zwischen 0,3 mm und 0,8 mm von der Auflagefläche (8) entfernt angeordnet ist.7. fuel injector according to one of the preceding claims, characterized in that the ball seat (10) between 0.3 mm and 0.8 mm from the support surface (8) is arranged away.
8. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kugelsitz (10) zwischen o, 45 mm und 5,5 mm, insbesondere 0,5 mm von der Auflagefläche (8) entfernt angeordnet ist.8. Fuel injector according to one of the preceding claims, characterized in that the ball seat (10) between o, 45 mm and 5.5 mm, in particular 0.5 mm away from the support surface (8) is arranged.
9. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die radiale Verformung des Ventilstücks (3) im Bereich des Kugelsitzes (10) bei Belastung weniger als 0,1 μm beträgt. 9. Fuel injector according to one of the preceding claims, characterized in that the radial deformation of the valve piece (3) in the region of the ball seat (10) under load is less than 0.1 microns.
PCT/DE2004/002341 2004-10-21 2004-10-21 Fuel injector WO2006042488A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0753658A1 (en) * 1995-07-14 1997-01-15 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Improved electromagnetic metering valve for a fuel injector
EP0851115A1 (en) * 1996-12-23 1998-07-01 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Electromagnetic metering valve with a ball shutter for a fuel injector
EP1043497A2 (en) * 1999-04-07 2000-10-11 Delphi Technologies, Inc. Control valve
WO2002095217A1 (en) * 2001-05-21 2002-11-28 Robert Bosch Gmbh High pressure sealing element for injectors

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0753658A1 (en) * 1995-07-14 1997-01-15 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Improved electromagnetic metering valve for a fuel injector
EP0851115A1 (en) * 1996-12-23 1998-07-01 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Electromagnetic metering valve with a ball shutter for a fuel injector
EP1043497A2 (en) * 1999-04-07 2000-10-11 Delphi Technologies, Inc. Control valve
WO2002095217A1 (en) * 2001-05-21 2002-11-28 Robert Bosch Gmbh High pressure sealing element for injectors

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