WO2002016759A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
WO2002016759A1
WO2002016759A1 PCT/DE2001/002759 DE0102759W WO0216759A1 WO 2002016759 A1 WO2002016759 A1 WO 2002016759A1 DE 0102759 W DE0102759 W DE 0102759W WO 0216759 A1 WO0216759 A1 WO 0216759A1
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WO
WIPO (PCT)
Prior art keywords
spring
compression spring
chamber
fuel injection
valve
Prior art date
Application number
PCT/DE2001/002759
Other languages
German (de)
French (fr)
Inventor
Joachim Winter
Juergen Gottschling
Dietmar Bantle
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 BR0107139-4A priority Critical patent/BR0107139A/en
Priority to EP01956358A priority patent/EP1313943A1/en
Publication of WO2002016759A1 publication Critical patent/WO2002016759A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve for example from the document DE 44 08 245 AI and comprises a valve holding body in which a spring chamber is formed.
  • a compression spring is arranged under prestress, which is supported at one end on a stationary stop and comes to rest on a spring plate at the other end.
  • the spring plate is connected to a valve member which is piston-shaped and is arranged to be longitudinally displaceable in a bore.
  • the longitudinal movement of the valve member controls at least one injection opening, via which fuel can be injected into the combustion chamber of an internal combustion engine.
  • the valve member has at least one pressure surface, which is arranged in a pressure chamber that can be filled with fuel under high pressure.
  • the known fuel injection valve has the disadvantage that the opening pressure decreases over the service life of the fuel injection valve and does not remain constant as desired. Due to the vibrations of the internal combustion engine during operation and thus also of the fuel injection valve, the position of the compression spring in the spring chamber changes, and this results in a slightly different spring force and thus also a different opening pressure, depending on the position of the compression spring. In addition, the end faces of the compression spring twist slightly against each other when pressed together, so that there is wear on the contact surface of the compression spring on the spring plate or on the stationary stop, as a result of which the pretension of the compression spring is reduced and the opening pressure of the fuel injector thus decreases.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the compression spring jams itself in the spring chamber and so the opening pressure of the fuel injection valve remains largely constant.
  • the compression spring is ground on at least one end so that the normal of this surface encloses an angle with the longitudinal axis of the compression spring. When the compression spring is preloaded in the spring chamber, this results in a force acting on the compression spring in the radial direction, which at the end presses it against the wall of the spring chamber, thereby preventing rotation of the compression spring in the spring chamber or any other change in position.
  • both contact surfaces of the compression spring are ground parallel to one another. This results in a radial force on the compression spring at both ends, which caulks it in the spring chamber. Since there is no preferred direction in the longitudinal direction, installation is also unproblematic.
  • the spring chamber is designed as a bore and has a diameter which allows the compression spring to be arranged at an angle in the spring chamber.
  • Figure 1 shows a longitudinal section through a fuel injection valve according to the invention
  • Figure 2 shows an enlarged view of Figure 1 in the area of the spring chamber
  • Figure 3 shows a longitudinal section through a compression spring according to the invention before installation.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention.
  • a valve body 1 is interposed by an washer 3 by means of a Clamping nut 7 clamped against a valve holding body 5 in the axial direction.
  • the fuel injection valve is arranged in an internal combustion engine such that the free end of the valve body 1 extends into the combustion chamber of the internal combustion engine.
  • a bore 10 is formed in the valve body 1, in which a piston-shaped valve member 12 is arranged to be longitudinally displaceable.
  • the valve member 12 is guided in a section in the bore 10 facing away from the combustion chamber, tapers towards the combustion chamber to form a pressure shoulder 19 and merges at the end on the combustion chamber side into a valve sealing surface 22 which at least has a valve seat 20 for control purposes which is formed on the end of the bore 10 on the combustion chamber side an injection opening 24 cooperates.
  • a pressure chamber 15 is formed in the valve body 1 by a radial expansion of the bore 10, which surrounds the pressure shoulder 19 and which continues as an annular channel surrounding the valve member 12 up to the valve seat 20.
  • the pressure chamber 15 can be filled with fuel under high pressure via an inlet channel 17 running in the valve body 1, the intermediate disk 3 and the valve holding body 5.
  • the valve member 12 merges into a spring plate 27 which is arranged in the intermediate disk 3 and extends into a spring chamber 30 formed in the valve holding body 5.
  • the spring chamber 30 is designed as a bore which is aligned coaxially with the bore 10 in the valve body 1 and has a longitudinal axis 31.
  • the spring chamber 30 is connected at its end remote from the combustion chamber to an outlet channel 18 which is connected to a leakage oil system, not shown in the drawing.
  • a compression spring 32 is arranged under prestress, which is designed here as a helical compression spring and whose end face 42 facing the combustion chamber comes to rest on the spring plate 27, while its end face 41 facing away from the combustion chamber comes to rest on the end face facing away from the combustion chamber of the spring chamber 30 comes to rest.
  • a compensating disk 36 is arranged between the end face 41 of the compression spring 32 facing away from the combustion chamber and the end face of the spring chamber 30 facing away from the combustion chamber, and the thickness of the prestress of the compression spring 32 can be adjusted.
  • the mode of operation of the fuel injection valve is such that fuel is introduced under high pressure from a fuel high-pressure source (not shown in the drawing) into the pressure chamber 15 via the inlet channel 17. There, the pressure rises until the hydraulic force acting on the pressure shoulder 19 in the axial direction on the valve member 12 is greater than the force of the compression spring 32.
  • the valve member 12 then lifts with the valve sealing surface 22 from the valve seat 20, so that the pressure chamber 15 is connected to the injection openings 24 and fuel is injected into the combustion chamber of the internal combustion engine.
  • the spring plate 27 is also moved, so that a direction of movement 39 is thereby defined, which in the present exemplary embodiment coincides with the longitudinal axis 31 of the spring chamber.
  • FIG. 2 shows an enlargement of Figure 1 in the area of the spring chamber 30 and the compression spring 32 in the installed position.
  • FIG. 3 shows the compression spring 32 before installation in the spring chamber 30.
  • the compression spring 32 has a longitudinal axis 34.
  • the end face 41 of the compression spring 32 facing the combustion chamber like the end face 42 facing the combustion chamber, has a surface normal 35 which forms an angle ⁇ with the longitudinal axis 34 of the compression spring 32.
  • the angle ⁇ is less than 5 degrees, preferably 0.5 to 3.0 degrees. This results in an inclined position of the compression spring 32 in the spring chamber 30 in the installed position, so that the longitudinal axis 34 of the compression spring 32 encloses the angle with the longitudinal axis 31 of the spring chamber 30.
  • the angle ⁇ causes an overhang e of the compression spring 32, so that the diameter of the spring chamber 30 corresponds at least approximately to the diameter of the compression spring 32 plus the overhang e.
  • the arrangement of the compression spring 32 under prestress in the spring chamber 30 results in a force acting in the radial direction on the ends of the compression spring 32 which presses the compression spring 32 against the wall of the spring chamber 30. This jamming of the compression spring 32 in the spring chamber 30 prevents rotation of the compression spring 32 about its axis during operation of the fuel injection valve.
  • the compression spring 32 is compressed by the opening stroke movement of the valve member 12, the end faces 41 and 42 are also slightly rotated relative to one another, but the compression also increases the radial force with which the compression spring 32 is clamped in the spring chamber 30. With a suitable design of the compression spring 32, it is thus ensured that mechanical vibrations, such as occur during operation of the internal combustion engine, machine occur, rotation of the compression spring 32 or another change in position within the spring chamber 30 is prevented.
  • the compression spring 32 shown in the drawing provision can also be made to provide the compression spring 32 with a bevel angle 1 only on one end face (41; 42).
  • the technical effort is less in this case, since two end faces (41; 42) do not have to be ground parallel to one another.
  • the resulting radial force on the compression spring 32 only acts on one side in this case, which - depending on the embodiment of the fuel injection valve - can be sufficient to fix the compression spring 32.
  • the spring wire of the compression spring 32 can also have a meandering arrangement.
  • the compression spring 32 according to the invention in another device in which a constant force is to be exerted on a movable element and it is disadvantageous if the compression spring is movable in the corresponding spring chamber.

Abstract

The invention relates to a fuel injection valve with a valve body (1), in which a valve member (12) may be longitudinally displaced in a drilling (10). The valve member (12) co-operates with a valve seat (20) at the combustion chamber end of the drilling (10) with the combustion chamber facing end thereof, such as to control at least one injection opening (24). A valve retaining body (5) is connected to the valve body (1) in which a spring chamber (30) is formed. The valve member (12) is connected at the combustion chamber end thereof to a spring collar (27), which extends into the spring chamber (30). A pressure spring (32) is arranged under tension between the spring collar (27) and the front face of the spring chamber (30) facing away from the combustion chamber, which presses the valve member (12) against the valve seat (20). The pressure spring (32) comprises end faces (41; 42) which are flat and the normals to the surfaces thereof are at an angle (α) to the longitudinal axis (34) of the pressure spring (32), such that the pressure spring (32) is subjected to a radial force on both ends due to the tension, which forces the pressure spring (32) against the wall of the spring chamber (30) and is thus fixed there.

Description

Kra tstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Ein solches Kraftstoffeinspritzventil ist beispielsweise aus der Schrift DE 44 08 245 AI bekannt und umfasst einen Ventilhaltekörper, in dem ein Federraum ausgebildet ist. In dem Federraum ist eine Druckfeder unter Vorspannung angeordnet, die sich mit einem Ende an einem ortsfesten Anschlag abstützt und mit dem anderen Ende an einem Federteller zur Anlage kommt. Der Federteller ist mit einem Ventilglied verbunden, das kolbenförmig ausgebildet ist und in einer Bohrung längsverschiebbar angeordnet ist. Das Ventilglied steuert durch seine Längsbewegung wenigstens eine Einspritzöffnung, über die Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt werden kann. Das Ventilglied weist dabei wenigstens eine Druckfläche auf, die in einem Druckraum angeordnet ist, der mit Kraftstoff unter hohem Druck befüll- bar ist. Dadurch ergibt sich eine hydraulische Kraft auf die Druckfläche, deren in axialer Richtung wirkende Komponente entgegen der Kraft der Druckfeder gerichtet ist. Bei einem ausreichend hohen Druck im Druckraum übersteigt die hydraulische Kraft die Kraft der Druckfeder und das Ventilglied durchfährt eine Öffnungshubbewegung, wobei die Druckfeder zusammengepresst wird. Der Kraftstoffdruck, bei dem das Ventilglied seine Öffnungshubbewegung beginnt, wird dabei als Öffnungsdruck bezeichnet.The invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is known for example from the document DE 44 08 245 AI and comprises a valve holding body in which a spring chamber is formed. In the spring chamber, a compression spring is arranged under prestress, which is supported at one end on a stationary stop and comes to rest on a spring plate at the other end. The spring plate is connected to a valve member which is piston-shaped and is arranged to be longitudinally displaceable in a bore. The longitudinal movement of the valve member controls at least one injection opening, via which fuel can be injected into the combustion chamber of an internal combustion engine. The valve member has at least one pressure surface, which is arranged in a pressure chamber that can be filled with fuel under high pressure. This results in a hydraulic force on the pressure surface, whose component acting in the axial direction is directed against the force of the compression spring. At a sufficiently high pressure in the pressure chamber, the hydraulic force exceeds the force of the compression spring and the valve member performs an opening stroke movement, the compression spring is pressed together. The fuel pressure at which the valve member begins its opening stroke movement is referred to as the opening pressure.
Das bekannte Kraftstoffeinspritzventil weist dabei den Nachteil auf, dass der Öffnungsdruck über die Lebensdauer des Kraftstoffeinspritzventils abnimmt und nicht, wie gewünscht, konstant bleibt . Durch die Erschütterungen der Brennkraftmaschine beim Betrieb und damit auch des Kra tstoffeinspritzventils ändert sich die Lage der Druckfeder im Federraum, und dadurch ergibt sich, je nach Lage der Druckfeder, eine etwas unterschiedliche Federkraft und damit auch ein unterschiedlicher Öffnungsdruck. Darüber hinaus verdrehen sich die Stirnseiten der Druckfeder beim Zusammenpressen leicht gegeneinander, so dass es dadurch zu einem Verschleiß an der Auflagefläche der Druckfeder am Federteller beziehungsweise am ortsfesten Anschlag kommt, wodurch sich die Vorspannung der Druckfeder erniedrigt und damit der Öffnungsdruck des Kraftstoffeinspritzventils abnimmt .The known fuel injection valve has the disadvantage that the opening pressure decreases over the service life of the fuel injection valve and does not remain constant as desired. Due to the vibrations of the internal combustion engine during operation and thus also of the fuel injection valve, the position of the compression spring in the spring chamber changes, and this results in a slightly different spring force and thus also a different opening pressure, depending on the position of the compression spring. In addition, the end faces of the compression spring twist slightly against each other when pressed together, so that there is wear on the contact surface of the compression spring on the spring plate or on the stationary stop, as a result of which the pretension of the compression spring is reduced and the opening pressure of the fuel injector thus decreases.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, dass sich die Druckfeder selbständig im Federraum verklemmt und so der Öffnungsdruck des Kraftstoffeinspritzventils weitgehend konstant bleibt. Die Druckfeder ist an wenigstens einem Ende so flächenhaft angeschliffen, dass die Normale dieser Fläche mit der Längsachse der Druckfeder einen Winkel einschließt. Beim Vorspannen der Druckfeder im Federraum ergibt sich dadurch eine in radialer Richtung wirkende Kraft auf die Druckfeder, die diese am ihrem Ende gegen die Wand des Federraums presst, wodurch eine Rotation der Druckfeder im Federraum oder eine sonstige Lageänderung verhindert wird. In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung sind beide Anlageflächen der Druckfeder parallel zueinander angeschliffen. Dadurch ergibt sich an beiden Enden eine radiale Kraft auf die Druckfeder, die diese im Federraum verstemmt . Da keine Vorzugsrichtung in Längsrichtung existiert ist darüber hinaus der Einbau unproblematisch.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the compression spring jams itself in the spring chamber and so the opening pressure of the fuel injection valve remains largely constant. The compression spring is ground on at least one end so that the normal of this surface encloses an angle with the longitudinal axis of the compression spring. When the compression spring is preloaded in the spring chamber, this results in a force acting on the compression spring in the radial direction, which at the end presses it against the wall of the spring chamber, thereby preventing rotation of the compression spring in the spring chamber or any other change in position. In an advantageous embodiment of the object of the invention, both contact surfaces of the compression spring are ground parallel to one another. This results in a radial force on the compression spring at both ends, which caulks it in the spring chamber. Since there is no preferred direction in the longitudinal direction, installation is also unproblematic.
In einer weiteren vorteilhaften Ausgestaltung ist der Federraum als Bohrung ausgebildet und weist einen Durchmesser auf, der es erlaubt, die Druckfeder im Federraum schräggestellt anzuordnen. Dadurch sind die Anlageflächen der Druckfeder auch im vorgespannten Zustand zueinander parallel, so dass sich eine gleichmäßige Anlagekraft der Druckfeder an der Anlagefläche ergibt .In a further advantageous embodiment, the spring chamber is designed as a bore and has a diameter which allows the compression spring to be arranged at an angle in the spring chamber. As a result, the contact surfaces of the compression spring are parallel to one another even in the prestressed state, so that there is a uniform contact force of the compression spring on the contact surface.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the subject matter of the invention can be gathered from the drawing, the description and the patent claims.
Zeichnungdrawing
In der Zeichnung ist ein Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Figur 1 zeigt einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil, Figur 2 eine vergrößerte Darstellung der Figur 1 im Bereich des Federraums und Figur 3 zeigt einen Längsschnitt durch eine erfindungsgemäße Druckfeder vor dem Einbau.In the drawing, an embodiment of a fuel injection valve according to the invention is shown. Figure 1 shows a longitudinal section through a fuel injection valve according to the invention, Figure 2 shows an enlarged view of Figure 1 in the area of the spring chamber and Figure 3 shows a longitudinal section through a compression spring according to the invention before installation.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Ein Ventilkörper 1 ist unter Zwischenlage einer Zwischenscheibe 3 mittels einer Spannmutter 7 gegen einen Ventilhaltekörper 5 in axialer Richtung verspannt. Das Kraftstoffeinspritzventil ist dabei so in einer Brennkraftmaschine angeordnet, dass das freie Ende des Ventilkörpers 1 bis in den Brennraum der Brennkraftmaschine ragt. Im Ventilkörper 1 ist eine Bohrung 10 ausgebildet, in der ein kolbenförmiges Ventilglied 12 längsverschiebbar angeordnet ist . Das Ventilglied 12 ist in einem brennraumabgewandten Abschnitt in der Bohrung 10 geführt, verjüngt sich dem Brennraum zu unter Bildung einer Druckschulter 19 und geht am brennraumseitigen Ende in eine Ventildichtfläche 22 über, die mit einem am brennraumseitigen Ende der Bohrung 10 ausgebildeten Ventilsitz 20 zur Steuerung wenigstens einer Einspritzöffnung 24 zusammenwirkt . Im Ventilkörper 1 ist durch eine radiale Erweiterung der Bohrung 10 ein Druckraum 15 ausgebildet, der die Druckschulter 19 umgibt und der sich als ein das Ventilglied 12 umgebender Ringkanal bis zum Ventilsitz 20 fortsetzt. Der Druckraum 15 ist über einen im Ventilkörper 1, der Zwischenscheibe 3 und dem Ventilhaltekörper 5 verlaufenden Zulaufkanal 17 mit Kraftstoff unter hohem Druck befüllbar.FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention. A valve body 1 is interposed by an washer 3 by means of a Clamping nut 7 clamped against a valve holding body 5 in the axial direction. The fuel injection valve is arranged in an internal combustion engine such that the free end of the valve body 1 extends into the combustion chamber of the internal combustion engine. A bore 10 is formed in the valve body 1, in which a piston-shaped valve member 12 is arranged to be longitudinally displaceable. The valve member 12 is guided in a section in the bore 10 facing away from the combustion chamber, tapers towards the combustion chamber to form a pressure shoulder 19 and merges at the end on the combustion chamber side into a valve sealing surface 22 which at least has a valve seat 20 for control purposes which is formed on the end of the bore 10 on the combustion chamber side an injection opening 24 cooperates. A pressure chamber 15 is formed in the valve body 1 by a radial expansion of the bore 10, which surrounds the pressure shoulder 19 and which continues as an annular channel surrounding the valve member 12 up to the valve seat 20. The pressure chamber 15 can be filled with fuel under high pressure via an inlet channel 17 running in the valve body 1, the intermediate disk 3 and the valve holding body 5.
Das Ventilglied 12 geht an seinem brennraumabgewandten Ende in einen Federteller 27 über, der in der Zwischenscheibe 3 angeordnet ist und bis in einen im Ventilhaltekörper 5 ausgebildeten Federraum 30 ragt. Der Federraum 30 ist hierbei als Bohrung ausgebildet, die koaxial zur Bohrung 10 im Ventilkörper 1 ausgerichtet ist und eine Längsachse 31 aufweist. Der Federraum 30 ist an seinem brennraumabgewandten Ende mit einem Ablaufkanal 18 verbunden, der mit einem in der Zeichnung nicht dargestellten Leckölsystem verbunden ist. Im Federraum 30 ist eine Druckfeder 32 unter Vorspannung angeordnet, die hier als Schraubendruckfeder ausgebildet ist und deren brennraumzugewandte Stirnfläche 42 am Federteller 27 zur Anlage kommt, während deren brennraumabge- wandte Stirnfläche 41 an der brennraumabgewandten Stirnseite des Federraums 30 zur Anlage kommt. Zwischen der brennraumabgewandten Stirnfläche 41 der Druckfeder 32 und dem brennraumabgewandten Stirnseite des Federraums 30 ist erforderlichenfalls eine Ausgleichsscheibe 36 angeordnet, über deren Dicke die Vorspannung der Druckfeder 32 eingestellt werden kann.At its end facing away from the combustion chamber, the valve member 12 merges into a spring plate 27 which is arranged in the intermediate disk 3 and extends into a spring chamber 30 formed in the valve holding body 5. The spring chamber 30 is designed as a bore which is aligned coaxially with the bore 10 in the valve body 1 and has a longitudinal axis 31. The spring chamber 30 is connected at its end remote from the combustion chamber to an outlet channel 18 which is connected to a leakage oil system, not shown in the drawing. In the spring chamber 30, a compression spring 32 is arranged under prestress, which is designed here as a helical compression spring and whose end face 42 facing the combustion chamber comes to rest on the spring plate 27, while its end face 41 facing away from the combustion chamber comes to rest on the end face facing away from the combustion chamber of the spring chamber 30 comes to rest. If necessary, a compensating disk 36 is arranged between the end face 41 of the compression spring 32 facing away from the combustion chamber and the end face of the spring chamber 30 facing away from the combustion chamber, and the thickness of the prestress of the compression spring 32 can be adjusted.
Die Funktionsweise des Kraftstoffeinspritzventils ist dergestalt, dass aus einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle Kraftstoff unter hohem Druck über den Zulaufkanal 17 in den Druckraum 15 eingeführt wird. Dort steigt der Druck an, bis die auf die Druckschulter 19 in axialer Richtung wirkende hydraulische Kraft auf das Ventilglied 12 größer ist als die Kraft der Druckfeder 32. Das Ventilglied 12 hebt dann mit der Ventildichtfläche 22 vom Ventilsitz 20 ab, so dass der Druckraum 15 mit den Einspritzöffnungen 24 verbunden ist und Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. Bei der Bewegung des Ventilglieds 12 wird auch der Federteller 27 mitbewegt, so dass dadurch eine Bewegungsrichtung 39 definiert wird, die im vorliegenden Ausführungsbeispiel mit der Längsachse 31 des Federraums zusammenfällt. Durch den hohen Druck im Druckraum 15 während der Einspritzung wird auch ein Teil des Kraftstoffs am geführten Abschnitt des Ventilglieds 12 vorbei in den Federraum 30 gepresst. Dabei wird der Druck entsprechend gemindert, so dass im Federraum 30 ein wesentlich geringerer Druck herrscht als im Druckraum 15. Das so in den Federraum 30 eindringende Lecköl wird über den Ablaufkanal 18 einem in der Zeichnung nicht dargestellten Leckölsystem zugeführt, um einen konstant niedrigen Druck im Federraum 30 aufrecht zu erhalten. Zur Beendigung der Einspritzung wird die Kraf stoffzufuhr in den Druckraum 15 unterbrochen, wodurch der Druck und damit auch die hydraulische Kraft auf das Ventilglied 12 entsprechend abnimmt. Unterschreitet der Druck im Druckraum 15 den Öffnungsdruck, so wird das Ventilglied 12 von der Kraft der Druckfeder 32 wieder in Richtung des Ventilsitzes 20 gedrückt, bis das Ventilglied 12 dort zur Anlage kommt und die Einspritzöffnungen 22 verschließt.The mode of operation of the fuel injection valve is such that fuel is introduced under high pressure from a fuel high-pressure source (not shown in the drawing) into the pressure chamber 15 via the inlet channel 17. There, the pressure rises until the hydraulic force acting on the pressure shoulder 19 in the axial direction on the valve member 12 is greater than the force of the compression spring 32. The valve member 12 then lifts with the valve sealing surface 22 from the valve seat 20, so that the pressure chamber 15 is connected to the injection openings 24 and fuel is injected into the combustion chamber of the internal combustion engine. When the valve member 12 is moved, the spring plate 27 is also moved, so that a direction of movement 39 is thereby defined, which in the present exemplary embodiment coincides with the longitudinal axis 31 of the spring chamber. Due to the high pressure in the pressure chamber 15 during the injection, some of the fuel is also pressed past the guided section of the valve member 12 into the spring chamber 30. The pressure is reduced accordingly, so that there is a substantially lower pressure in the spring chamber 30 than in the pressure chamber 15. The leakage oil thus penetrating into the spring chamber 30 is fed via the outlet channel 18 to a leakage oil system, not shown in the drawing, in order to maintain a constant low pressure in the To maintain spring chamber 30. To end the injection, the fuel supply to the pressure chamber 15 is interrupted, as a result of which the pressure and thus also the hydraulic force on the valve member 12 decreases accordingly. If the pressure in the pressure chamber 15 falls below the opening pressure, then the valve member 12 is pressed again by the force of the compression spring 32 in the direction of the valve seat 20 until the valve member 12 comes to rest there and closes the injection openings 22.
Figur 2 zeigt eine Vergrößerung der Figur 1 im Bereich des Federraums 30 und die Druckfeder 32 in Einbaulage. Figur 3 zeigt die Druckfeder 32 vor dem Einbau in den Federraum 30. Die Druckfeder 32 weist eine Längsachse 34 auf. Die brenn- raumzugewandte Stirnfläche 41 der Druckfeder 32 weist ebenso wie die brennraumzugewandte Stirnfläche 42 eine Flächennormale 35 auf, die mit der Längsachse 34 der Druckfeder 32 einen Winkel α einschließt. Der Winkel α beträgt dabei weniger als 5 Grad, vorzugsweise 0,5 bis 3,0 Grad. Hierdurch ergibt sich in Einbaulage eine Schrägstellung der Druckfeder 32 im Federraum 30, so dass die Längsachse 34 der Druckfeder 32 mit der Längsachse 31 des Federraums 30 den Winkel einschließt . Der Winkel α bewirkt dabei einen Überhang e der Druckfeder 32, so dass der Durchmesser des Federraums 30 zumindest annähernd dem Durchmesser der Druckfeder 32 zuzüglich des Überhangs e entspricht. Durch die Anordnung der Druckfeder 32 unter Vorspannung im Federraum 30 ergibt sich auf die Enden der Druckfeder 32 eine in radialer Richtung wirkende Kraft, die die Druckfeder 32 gegen die Wand des Federraums 30 presst. Durch dieses Verklemmen der Druckfeder 32 im Federraum 30 wird eine Rotation der Druckfeder 32 um ihre Achse im Betrieb des Kraftstoffeinspritzventils verhindert . Zwar kommt es durch das Zusammenpressen der Druckfeder 32 durch die Öffnungshubbewegung des Ventilgliedes 12 ebenfalls zu einer leichten Verdrehung der Stirnflächen 41 und 42 gegeneinander, jedoch verstärkt sich durch das Zusammenpressen auch die radiale Kraft, mit der die Druckfeder 32 im Federraum 30 verklemmt wird. Bei geeigneter Auslegung der Druckfeder 32 ist somit sichergestellt, dass auch durch mechanische Schwingungen, wie sie beim Betrieb der Brennkraft- maschine auftreten, eine Rotation der Druckfeder 32 oder eine sonstige Lageänderung innerhalb des Federraums 30 verhindert wird.Figure 2 shows an enlargement of Figure 1 in the area of the spring chamber 30 and the compression spring 32 in the installed position. FIG. 3 shows the compression spring 32 before installation in the spring chamber 30. The compression spring 32 has a longitudinal axis 34. The end face 41 of the compression spring 32 facing the combustion chamber, like the end face 42 facing the combustion chamber, has a surface normal 35 which forms an angle α with the longitudinal axis 34 of the compression spring 32. The angle α is less than 5 degrees, preferably 0.5 to 3.0 degrees. This results in an inclined position of the compression spring 32 in the spring chamber 30 in the installed position, so that the longitudinal axis 34 of the compression spring 32 encloses the angle with the longitudinal axis 31 of the spring chamber 30. The angle α causes an overhang e of the compression spring 32, so that the diameter of the spring chamber 30 corresponds at least approximately to the diameter of the compression spring 32 plus the overhang e. The arrangement of the compression spring 32 under prestress in the spring chamber 30 results in a force acting in the radial direction on the ends of the compression spring 32 which presses the compression spring 32 against the wall of the spring chamber 30. This jamming of the compression spring 32 in the spring chamber 30 prevents rotation of the compression spring 32 about its axis during operation of the fuel injection valve. Although the compression spring 32 is compressed by the opening stroke movement of the valve member 12, the end faces 41 and 42 are also slightly rotated relative to one another, but the compression also increases the radial force with which the compression spring 32 is clamped in the spring chamber 30. With a suitable design of the compression spring 32, it is thus ensured that mechanical vibrations, such as occur during operation of the internal combustion engine, machine occur, rotation of the compression spring 32 or another change in position within the spring chamber 30 is prevented.
Alternativ zu der in der Zeichnung dargestellten Druckfeder 32 kann es auch vorgesehen sein, die Druckfeder 32 nur an einer Stirnfläche (41; 42) mit einem Anschliffwinke1 zu versehen. Der technische Aufwand ist in diesem Fall geringer, da nicht zwei Stirnflächen (41; 42) parallel zueinander angeschliffen werden müssen. Die sich dadurch ergebende radiale Kraft auf die Druckfeder 32 wirkt in diesem Fall nur auf einer Seite, was - je nach Ausführungsform des Kraftstoff- einspritzventils - ausreichend sein kann, die Druckfeder 32 zu fixieren.As an alternative to the compression spring 32 shown in the drawing, provision can also be made to provide the compression spring 32 with a bevel angle 1 only on one end face (41; 42). The technical effort is less in this case, since two end faces (41; 42) do not have to be ground parallel to one another. The resulting radial force on the compression spring 32 only acts on one side in this case, which - depending on the embodiment of the fuel injection valve - can be sufficient to fix the compression spring 32.
Es kann auch vorgesehen sein, statt einer als Schraubendruckfeder ausgebildeten Druckfeder 32 eine andere Druckfeder im Federraum 30 anzuordnen. Beispielsweise kann der Federdraht der Druckfeder 32 auch eine mäanderförmige Anordnung aufweisen.It can also be provided to arrange another compression spring in the spring chamber 30 instead of a compression spring 32 designed as a helical compression spring. For example, the spring wire of the compression spring 32 can also have a meandering arrangement.
Neben der Verwendung in einem Kraftstoffeinspritzventil kann es auch vorgesehen sein, die erfindungsgemäße Druckfeder 32 in einer anderen Vorrichtung einzusetzen, bei der eine konstante Kraft auf ein bewegliches Element ausgeübt werden soll und wobei es unvorteilhaft ist, wenn die Druckfeder im entsprechenden Federraum beweglich ist . In addition to use in a fuel injection valve, it can also be provided to use the compression spring 32 according to the invention in another device in which a constant force is to be exerted on a movable element and it is disadvantageous if the compression spring is movable in the corresponding spring chamber.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil mit einem Ventilhaltekörper (5) und einem darin ausgebildeten Federraum (30) , in dem wenigstens eine eine Längsachse (34) aufweisende Druckfeder1. Fuel injection valve with a valve holding body (5) and a spring chamber (30) formed therein, in which at least one compression spring has a longitudinal axis (34)
(32) unter Vorspannung zwischen einem ortsfesten Anschlag und einem Federteller (27) angeordnet ist, wobei die Druckfeder (32) zwei ebene Stirnflächen (41; 42) aufweist und wobei der Federteller (27) zumindest mittelbar mit einem Ventilglied (12) verbunden und zusammen mit diesem im Federraum (30) bewegbar ist, so dass die Druckfeder(32) is arranged under prestress between a stationary stop and a spring plate (27), the compression spring (32) having two flat end faces (41; 42) and wherein the spring plate (27) is at least indirectly connected to a valve member (12) and is movable together with this in the spring chamber (30), so that the compression spring
(32) eine Schließkraft auf das Ventilglied (12) ausübt, wobei das Ventilglied (12) durch eine hydraulische Kraft entgegen der Kraft der Druckfeder (32) bewegt werden kann und dabei wenigstens eine Einspritzöffnung (24) steuert, über die Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt werden kann, dadurch gekennzeichnet, dass die Druckfeder (32) im Federraum (30) derart angeordnet ist, dass deren Längsachse (34) geneigt zur Bewegungsrichtung (39) des Federtellers (27) verläuft.(32) exerts a closing force on the valve member (12), the valve member (12) being able to be moved by a hydraulic force against the force of the compression spring (32) and thereby controlling at least one injection opening (24) via which fuel into the combustion chamber can be injected into an internal combustion engine, characterized in that the compression spring (32) is arranged in the spring chamber (30) such that its longitudinal axis (34) is inclined to the direction of movement (39) of the spring plate (27).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass wenigstens eine Stirnfläche (41; 42) der Druckfeder (32) eine Flächennormale (35) aufweist, die mit Längsachse (34) der Druckfeder (32) einen Winkel (α) einschließt. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass die beiden Stirnflächen (41; 42) der Druckfeder (32) parallel zueinander sind.2. Fuel injection valve according to claim 1, characterized in that at least one end face (41; 42) of the compression spring (32) has a surface normal (35) which includes an angle (α) with the longitudinal axis (34) of the compression spring (32). Fuel injection valve according to Claim 2, characterized in that the two end faces (41; 42) of the compression spring (32) are parallel to one another.
Kraftstoffeinspritzventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Winkel (α) der Flächennormale (35) mit der Längsachse (34) der Druckfeder (32) 0,5 bis 2 , 5 Grad beträgt .Fuel injection valve according to claim 2 or 3, characterized in that the angle (α) of the surface normal (35) with the longitudinal axis (34) of the compression spring (32) is 0.5 to 2.5 degrees.
Kraftstoffeinspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Federraum (30) als Bohrung ausgebildet ist, deren Durchmesser zumindest annähernd dem Durchmesser der Druckfeder (32) zuzüglich des Überhangs (e) der Druckfeder (32) entspricht. Kraftstoffeinspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Druckfeder (32) als Schraubendruckfeder ausgebildet ist. Fuel injection valve according to one of the preceding claims, characterized in that the spring chamber (30) is designed as a bore, the diameter of which corresponds at least approximately to the diameter of the compression spring (32) plus the overhang (e) of the compression spring (32). Fuel injection valve according to one of the preceding claims, characterized in that the compression spring (32) is designed as a helical compression spring.
PCT/DE2001/002759 2000-08-24 2001-07-20 Fuel injection valve for internal combustion engines WO2002016759A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
BR0107139-4A BR0107139A (en) 2000-08-24 2001-07-20 Fuel injection valve for combustion engine
EP01956358A EP1313943A1 (en) 2000-08-24 2001-07-20 Fuel injection valve for internal combustion engines

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000141675 DE10041675A1 (en) 2000-08-24 2000-08-24 Fuel injection valve for internal combustion engines
DE10041675.6 2000-08-24

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WO2002016759A1 true WO2002016759A1 (en) 2002-02-28

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BR (1) BR0107139A (en)
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WO (1) WO2002016759A1 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4655396A (en) * 1985-09-25 1987-04-07 United Technologies Diesel Systems, Inc. Electromagnetic fuel injector
US4660770A (en) * 1985-09-25 1987-04-28 United Technologies Diesel Systems, Inc. Electromagnetic fuel injector
GB2226078A (en) * 1988-11-09 1990-06-20 Lucas Ind Plc C.i. engine fuel injection nozzle
EP0583139A1 (en) * 1992-08-14 1994-02-16 LUCAS INDUSTRIES public limited company Fuel injector
DE4408245A1 (en) 1994-03-11 1995-09-14 Bosch Gmbh Robert Injection nozzle for internal combustion engines
EP0867611A1 (en) * 1997-03-26 1998-09-30 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Fuel injection nozzle for an internal combustion engine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4655396A (en) * 1985-09-25 1987-04-07 United Technologies Diesel Systems, Inc. Electromagnetic fuel injector
US4660770A (en) * 1985-09-25 1987-04-28 United Technologies Diesel Systems, Inc. Electromagnetic fuel injector
GB2226078A (en) * 1988-11-09 1990-06-20 Lucas Ind Plc C.i. engine fuel injection nozzle
EP0583139A1 (en) * 1992-08-14 1994-02-16 LUCAS INDUSTRIES public limited company Fuel injector
DE4408245A1 (en) 1994-03-11 1995-09-14 Bosch Gmbh Robert Injection nozzle for internal combustion engines
EP0867611A1 (en) * 1997-03-26 1998-09-30 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Fuel injection nozzle for an internal combustion engine

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DE10041675A1 (en) 2002-03-07
BR0107139A (en) 2002-07-02
CN1388865A (en) 2003-01-01

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