EP1490594B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1490594B1
EP1490594B1 EP03714674A EP03714674A EP1490594B1 EP 1490594 B1 EP1490594 B1 EP 1490594B1 EP 03714674 A EP03714674 A EP 03714674A EP 03714674 A EP03714674 A EP 03714674A EP 1490594 B1 EP1490594 B1 EP 1490594B1
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EP
European Patent Office
Prior art keywords
spring element
apertures
fuel injection
injection valve
longitudinal axis
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
EP03714674A
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German (de)
French (fr)
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EP1490594A1 (en
Inventor
Dietmar Uhlmann
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1490594A1 publication Critical patent/EP1490594A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift

Definitions

  • the known helical compression spring has the disadvantage that, in order to produce the necessary rigidity, it has to be wound with a relatively strong wire and thus occupies a relatively large amount of installation space. This sets the further streamlining of the fuel injection valves a limit that can not be exceeded due to the prevailing high fuel pressure there.
  • a fuel injection valve which has a closing element in the form of a ball, which cooperates with a valve seat.
  • the ball is pressed by a spring sleeve against the valve seat, wherein the sleeve has openings at several points, which provides the desired longitudinal elasticity.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the spring element used in the form of a cylindrical sleeve with the same rigidity less space required than a corresponding helical compression spring, so that the outer diameter of the fuel injection valve can be reduced accordingly.
  • the cylindrical sleeve of the spring element has on its wall at several points openings, which make the cylindrical sleeve elastically deformable in the longitudinal direction, wherein the apertures are formed slit-shaped. In order to keep the notch stresses at the ends of the slot-shaped openings small, the ends are rounded, and the openings are formed with respect to their longitudinal axis in the center waisted.
  • the cylindrical sleeve thus obtains the desired longitudinal elasticity without the notch stresses becoming too high at the ends of the apertures and resulting in a plastic deformation of the material of the cylindrical sleeve.
  • FIG. 1 is a longitudinal section through an inventive fuel injection valve shown.
  • the fuel injection valve has a housing 1, which comprises a valve holding body 3 and a valve body 5, which are clamped by means of a clamping nut 7 in the axial direction against each other.
  • a bore 10 is formed, the a longitudinal axis 14 and in which a piston-shaped valve member 12 is arranged longitudinally displaceable.
  • the hole 10 expands at its end facing away from the combustion chamber to an interior space 9, into which an inlet channel 21 formed in the valve holding body 3 opens.
  • valve member 12 is guided in a bore bore portion 110 in the bore 10 and between the valve member 12 and the wall of the bore 10, a ring-channel-shaped pressure chamber 18 is formed, which is filled via the inlet channel 21 and the interior 9 with fuel under high pressure.
  • a ring-channel-shaped pressure chamber 18 is formed, which is filled via the inlet channel 21 and the interior 9 with fuel under high pressure.
  • four poles 16 are provided, which allow the fuel from the interior 9 between the valve member 12 and the wall of the bore 10 can flow into the pressure chamber 18.
  • valve seat 20 is formed, which is conically shaped and cooperates with a formed on the combustion chamber end of the valve member 12 valve sealing surface 24 in such a way that lifted from the valve seat 20 valve sealing surface 24 fuel from the Pressure chamber 18 between the valve sealing surface 24 and the valve seat 20 can flow through to formed in the valve body 5 injection openings 22, through which the fuel is injected into the combustion chamber 6 of the internal combustion engine. If the valve sealing surface 24 bears against the valve seat 20, this fuel flow is interrupted so that the injection openings 22 are closed.
  • a sleeve 34, a spring element 30 and a spring plate 32 is arranged, which surround the combustion chamber facing away from the end portion of the valve member 12.
  • a control chamber 37 is limited, can be passed into the trained via a valve holding body 3 control bore 40 fuel at high pressure.
  • the spring element 30 is arranged between the sleeve 34 and the spring plate 32 under compressive bias, whereby the sleeve 34 and the spring plate 32 are pressed apart. As the spring plate 32 is supported on the valve member, thereby the valve member 12 is pressed against the valve seat 20.
  • the longitudinal movement of the valve member 12 is controlled by the hydraulic pressure in the pressure chamber 18 and the pressure in the control chamber 37.
  • a continuously high fuel pressure prevails in the pressure chamber 18, resulting in a hydraulic force acting on a pressure shoulder 17, which is formed at the transition of the combustion chamber-facing section of the valve member 12 to the guided section in the region of the polished sections 16.
  • this opening force is the force of the prestressed spring element 30 and the hydraulic closing force, which results from the pressure in the pressure chamber 37 on the end face 13 of the valve member 12.
  • the spring element 30 is designed as a cylindrical sleeve, which has a plurality of apertures 45 on its wall, whereby the spring element 30 is elastically deformable in the longitudinal direction.
  • the exact structure of the formed as a cylindrical sleeve spring element 30 is in FIG. 4 shown, wherein the spring element 30 is shown here in the unloaded state and is made in this case as a separate component without the sleeve 34 and the ring member 42.
  • the apertures 45 of the spring element 30 are slot-shaped and have a longitudinal axis 52 which extends with respect to the longitudinal axis 14 of the spring element 30 in a radial plane.
  • the ends 47 of the slot-shaped openings 45 are rounded in order to reduce the notch stresses at this point during compression of the spring element 30.
  • plastic deformation of the material is to be prevented in any case at the ends 47 of the openings 45. Otherwise, the spring element 30 would irreversibly deform, which would change the rigidity.
  • two slot-shaped apertures 45 are arranged, which are separated by a connecting web 48 and a second connecting web 48 'opposite thereto.
  • the adjacent radial plane lying apertures 45 are configured the same, but they are rotated with respect to the longitudinal axis 14 by 90 °.
  • the thickness of the cantilever 49 and over the length thereof, resulting from the width of the connecting webs 48 the elasticity and thus the spring constant of the spring element 30 can be adjusted.
  • the spring element 30 shown here consists of two half-cylinders, which are connected to welds 50 together.
  • the production of the spring element 30 takes place, for example, in that two half cylinders are produced separately, which are then connected to each other at weld seams 50.
  • FIG. 5 shows an intermediate step of one of the half-cylinders, namely a spring element half 130, which represents a rectangular, planar sheet of a suitable steel.
  • breakthroughs 45 are introduced, for example by punching.
  • the spring element half 130 is then bent, so that the side surfaces 54 can each be connected to a corresponding side surface 54 of a second spring element half 130, preferably by welding.
  • the welds 50 are dispensed with.
  • the apertures 45 can not be introduced by punching in this case, but for example by means of a laser. Which manufacturing method makes sense in each case depends on the expected mechanical load of the spring element 30.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für eine Brennkraftmaschine aus, wie es der Gattung des Patentanspruchs 1 entspricht. Solche Kraftstoffeinspritzventile sind beispielsweise aus der Offenlegungsschrift DE 100 24 703 A1 bekannt. Derartige Kraftstoffeinspritzventile weisen ein Gehäuse auf, in dem ein bewegliches Ventilglied angeordnet ist, das durch seine Bewegung entgegen der elastischen Kraft eines Federelements die Kraftstoffzufuhr zum Brennraum der Brennkraftmaschine steuert. Das Ventilglied weist häufig die Form einer Ventilnadel auf, die eine Längsachse aufweist und deren Bewegung in Richtung der Längsachse erfolgt. Das Federelement ist als Schraubendruckfeder ausgebildet, die koaxial zum Ventilglied im Gehäuse angeordnet ist. Die bekannte Schraubendruckfeder weist hierbei jedoch den Nachteil auf, dass sie, um die notwendige Steifigkeit zu erzeugen, mit relativ starkem Draht gewickelt werden muss und damit relativ viel Bauraum einnimmt. Dies setzt der weiteren Verschlankung der Kraftstoffeinspritzventile eine Grenze, die aufgrund des dort herrschenden hohen Kraftstoffdrucks nicht unterschritten werden kann.The invention is based on a fuel injection valve for an internal combustion engine, as it corresponds to the preamble of claim 1. Such fuel injection valves are for example from the published patent application DE 100 24 703 A1 known. Such fuel injection valves have a housing in which a movable valve member is arranged, which controls the fuel supply to the combustion chamber of the internal combustion engine by its movement against the elastic force of a spring element. The valve member often has the shape of a valve needle, which has a longitudinal axis and whose movement takes place in the direction of the longitudinal axis. The spring element is designed as a helical compression spring, which is arranged coaxially to the valve member in the housing. However, the known helical compression spring has the disadvantage that, in order to produce the necessary rigidity, it has to be wound with a relatively strong wire and thus occupies a relatively large amount of installation space. This sets the further streamlining of the fuel injection valves a limit that can not be exceeded due to the prevailing high fuel pressure there.

Aus der US 4 984 744 A ist ein Kraftstoffeinspritzventil bekannt, das ein Schließelement in Form einer Kugel aufweist, die mit einem Ventilsitz zusammenwirkt. Die Kugel wird von einer Federhülse gegen den Ventilsitz gedrückt, wobei die Hülse an mehreren Stellen Durchbrüche aufweist, die für die gewünschte Längselastizität sorgt.From the US 4,984,744 A For example, a fuel injection valve is known which has a closing element in the form of a ball, which cooperates with a valve seat. The ball is pressed by a spring sleeve against the valve seat, wherein the sleeve has openings at several points, which provides the desired longitudinal elasticity.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass das hier verwendete Federelement in Form einer zylindrischen Hülse bei gleicher Steifigkeit weniger Bauraum benötigt als eine entsprechende Schraubendruckfeder, so dass der Außendurchmesser des Kraftstoffeinspritzventils entsprechend verkleinert werden kann. Die zylindrische Hülse des Federelements weist an ihrer Wand an mehreren Stellen Durchbrüche auf, die die zylindrische Hülse in Längsrichtung elastisch verformbar machen, wobei die Durchbrüche schlitzförmig ausgebildet sind. Um die Kerbspannungen an den Enden der schlitzförmigen Durchbrüche gering zu halten, sind die Enden gerundet ausgebildet, und die Durchbrüche sind bezüglich ihrer Längsachse in der Mitte tailliert ausgebildet. Die zylindrische Hülse erhält so die gewünschte Längselastizität, ohne dass an den Enden der Durchbrüche die Kerbspannungen zu hoch werden und es zu einer plastischen Verformung des Materials der zylindrischen Hülse kommen kann.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the spring element used in the form of a cylindrical sleeve with the same rigidity less space required than a corresponding helical compression spring, so that the outer diameter of the fuel injection valve can be reduced accordingly. The cylindrical sleeve of the spring element has on its wall at several points openings, which make the cylindrical sleeve elastically deformable in the longitudinal direction, wherein the apertures are formed slit-shaped. In order to keep the notch stresses at the ends of the slot-shaped openings small, the ends are rounded, and the openings are formed with respect to their longitudinal axis in the center waisted. The cylindrical sleeve thus obtains the desired longitudinal elasticity without the notch stresses becoming too high at the ends of the apertures and resulting in a plastic deformation of the material of the cylindrical sleeve.

Durch die Unteransprüche sind vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung möglich. Durch den Verlauf der Durchbrüche, die im wesentlichen in einer Radialebene der zylindrischen Hülse verlaufen, erreicht man in einfacher Art und Weise eine gute Längselastizität der zylindrischen Hülse. Besonders vorteilhaft ist es hierbei, wenn zwei gleichartige Durchbrüche in einer Radialebene liegen, die durch Verbindungsstege voneinander getrennt sind. Über die Dicke dieser Verbindungsstege kann sehr einfach die Elastizität der zylindrischen Hülse eingestellt werden. Bei Ausbildung von zwei Durchbrüchen in einer Radialebene ist es besonders vorteilhaft, wenn die Durchbrüche der unmittelbar benachbarten Radialebenen gegeneinander um 90° gedreht angeordnet sind.By the dependent claims advantageous embodiments of the subject invention are possible. Through the course of the openings, which extend substantially in a radial plane of the cylindrical sleeve, one reaches in a simple Way a good longitudinal elasticity of the cylindrical sleeve. It is particularly advantageous if two similar breakthroughs lie in a radial plane, which are separated by connecting webs. About the thickness of these connecting webs can be easily adjusted, the elasticity of the cylindrical sleeve. With the formation of two openings in a radial plane, it is particularly advantageous if the openings of the immediately adjacent radial planes are mutually rotated by 90 °.

Weitere vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung zu entnehmen.Further advantageous embodiments of the subject invention are the description and the drawings refer to.

Zeichnungdrawing

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

Figur 1
einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
Figur 2
eine perspektivisch geschnittene Ansicht des Ventilkörpers, wobei das Ventilglied der Übersichtlichkeit halber weggelassen ist,
Figur 3
eine vergrößerte Darstellung des Federelements mit angefügter Hülse,
Figur 4
eine Darstellung des Federelements im unbelasteten Zustand und
Figur 5
ein blechartiges Vorprodukt, aus dem das Federelement gefertigt werden kann.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a longitudinal section through a fuel injection valve according to the invention,
FIG. 2
a perspective cut view of the valve body, wherein the valve member is omitted for clarity,
FIG. 3
an enlarged view of the spring element with attached sleeve,
FIG. 4
an illustration of the spring element in the unloaded state and
FIG. 5
a sheet-like precursor from which the spring element can be made.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das einen Ventilhaltekörper 3 und einen Ventilkörper 5 umfasst, die mittels einer Spannmutter 7 in axialer Richtung gegeneinander verspannt sind. Im Ventilkörper 5 ist eine Bohrung 10 ausgebildet, die eine Längsachse 14 aufweist und in der ein kolbenförmiges Ventilglied 12 längsverschiebbar angeordnet ist. Die Bohrung 10 erweitert sich an ihrem brennraumabgewandten Ende zu einem Innenraum 9, in den ein im Ventilhaltekörper 3 ausgebildeter Zulaufkanal 21 mündet. Das Ventilglied 12 wird in einem mittleren Bohrungsabschnitt 110 in der Bohrung 10 geführt und zwischen dem Ventilglied 12 und der Wand der Bohrung 10 ist ein ringkanalförmiger Druckraum 18 ausgebildet, der über den Zulaufkanal 21 und den Innenraum 9 mit Kraftstoff unter hohem Druck befüllbar ist. Im geführten Abschnitt des Ventilgliedes 12 sind vier Anschliffe 16 vorgesehen, die es ermöglichen, dass der Kraftstoff aus dem Innenraum 9 zwischen dem Ventilglied 12 und der Wand der Bohrung 10 in den Druckraum 18 fließen kann. Am in den Brennraum 6 der Brennkraftmaschine ragenden Ende der Bohrung 10 ist ein Ventilsitz 20 ausgebildet, der konisch geformt ist und mit einer am brennraumseitigen Ende des Ventilglieds 12 ausgebildeten Ventildichtfläche 24 in der Art zusammenwirkt, dass bei vom Ventilsitz 20 abgehobener Ventildichtfläche 24 Kraftstoff aus dem Druckraum 18 zwischen der Ventildichtfläche 24 und dem Ventilsitz 20 hindurch zu im Ventilkörper 5 ausgebildeten Einspritzöffnungen 22 fließen kann, durch die der Kraftstoff in den Brennraum 6 der Brennkraftmaschine eingespritzt wird. Liegt die Ventildichtfläche 24 am Ventilsitz 20 an, so wird dieser Kraftstoffstrom unterbrochen, so dass die Einspritzöffnungen 22 verschlossen sind.In FIG. 1 is a longitudinal section through an inventive fuel injection valve shown. The fuel injection valve has a housing 1, which comprises a valve holding body 3 and a valve body 5, which are clamped by means of a clamping nut 7 in the axial direction against each other. In the valve body 5, a bore 10 is formed, the a longitudinal axis 14 and in which a piston-shaped valve member 12 is arranged longitudinally displaceable. The hole 10 expands at its end facing away from the combustion chamber to an interior space 9, into which an inlet channel 21 formed in the valve holding body 3 opens. The valve member 12 is guided in a bore bore portion 110 in the bore 10 and between the valve member 12 and the wall of the bore 10, a ring-channel-shaped pressure chamber 18 is formed, which is filled via the inlet channel 21 and the interior 9 with fuel under high pressure. In the guided portion of the valve member 12 four poles 16 are provided, which allow the fuel from the interior 9 between the valve member 12 and the wall of the bore 10 can flow into the pressure chamber 18. At the projecting into the combustion chamber 6 of the internal combustion engine end of the bore 10, a valve seat 20 is formed, which is conically shaped and cooperates with a formed on the combustion chamber end of the valve member 12 valve sealing surface 24 in such a way that lifted from the valve seat 20 valve sealing surface 24 fuel from the Pressure chamber 18 between the valve sealing surface 24 and the valve seat 20 can flow through to formed in the valve body 5 injection openings 22, through which the fuel is injected into the combustion chamber 6 of the internal combustion engine. If the valve sealing surface 24 bears against the valve seat 20, this fuel flow is interrupted so that the injection openings 22 are closed.

Im Innenraum 9 ist eine Hülse 34, ein Federelement 30 und ein Federteller 32 angeordnet, die den brennraumabgewandten Endabschnitt des Ventilglieds 12 umgeben. Durch die brennraumabgewandte Stirnseite 13 des Ventilglieds 12, den Ventilhaltekörper 3 und die das Ventilglied 12 umgebende Hülse 34 wird ein Steuerraum 37 begrenzt, in den über eine im Ventilhaltekörper 3 ausgebildete Steuerbohrung 40 Kraftstoff unter hohem Druck geleitet werden kann. Das Federelement 30 ist zwischen der Hülse 34 und dem Federteller 32 unter Druckvorspannung angeordnet, wodurch die Hülse 34 und der Federteller 32 auseinandergedrückt werden. Da sich der Federteller 32 am Ventilglied abstützt, wird dadurch das Ventilglied 12 gegen den Ventilsitz 20 gedrückt.In the interior 9, a sleeve 34, a spring element 30 and a spring plate 32 is arranged, which surround the combustion chamber facing away from the end portion of the valve member 12. By the combustion chamber facing away from end face 13 of the valve member 12, the valve holding body 3 and the valve member 12 surrounding sleeve 34, a control chamber 37 is limited, can be passed into the trained via a valve holding body 3 control bore 40 fuel at high pressure. The spring element 30 is arranged between the sleeve 34 and the spring plate 32 under compressive bias, whereby the sleeve 34 and the spring plate 32 are pressed apart. As the spring plate 32 is supported on the valve member, thereby the valve member 12 is pressed against the valve seat 20.

Die Längsbewegung des Ventilglieds 12 wird durch den hydraulischen Druck im Druckraum 18 und den Druck im Steuerraum 37 gesteuert. Im Druckraum 18 herrscht bei Betrieb der Brennkraftmaschine ein durchgehend hoher Kraftstoffdruck, durch den sich eine hydraulische Kraft auf eine Druckschulter 17 ergibt, die am Übergang des brennraumzugewandten Abschnitts des Ventilglieds 12 zum geführten Abschnitt im Bereich der Anschliffe 16 ausgebildet ist. Dadurch ergibt sich eine Öffnungskraft auf das Ventilglied 12, die vom Ventilsitz 20 weg gerichtet ist. Dieser Öffnungskraft entgegengesetzt ist die Kraft des vorgespannten Federelements 30 und die hydraulische Schließkraft, die sich durch den Druck im Druckraum 37 auf die Stirnseite 13 des Ventilglieds 12 ergibt. Herrscht im Druckraum 37 ein hoher Kraftstoffdruck, so wird das Ventilglied 12 in seiner Schließstellung gehalten, da die hydraulisch wirksame Fläche der Druckschulter 17 deutlich kleiner ist als die der Stirnfläche 13 des Ventilglieds 12. Wird der Steuerraum 37 über die Steuerbohrung 40 entlastet, so bewegt die hydraulische Kraft auf die Druckschulter 17 das Ventilglied 12 entgegen der Kraft des Federelements 30 vom Ventilsitz 20 weg, so dass Kraftstoff durch die Einspritzöffnungen 22 in der oben beschriebenen Art und Weise in den Brennraum 6 der Brennkraftmaschine eingespritzt wird. Da im Druckraum 18 und im Steuerraum 37 Drücke von mehr als 100 MPa herrschen können, spielt die Kraft des Federelements 30 bei der Öffnungshubbewegung des Ventilglieds 12 nur eine untergeordnete Rolle. Das Federelement 30 dient hauptsächlich dazu, das Ventilglied 12 bei abgeschalteter Brennkraftmaschine und damit bei fehlendem Kraftstoffdruck im Druckraum 18 und im Steuerraum 37 in Schließstellung zu halten.The longitudinal movement of the valve member 12 is controlled by the hydraulic pressure in the pressure chamber 18 and the pressure in the control chamber 37. During operation of the internal combustion engine, a continuously high fuel pressure prevails in the pressure chamber 18, resulting in a hydraulic force acting on a pressure shoulder 17, which is formed at the transition of the combustion chamber-facing section of the valve member 12 to the guided section in the region of the polished sections 16. This results in an opening force on the valve member 12, which is directed away from the valve seat 20. Opposite this opening force is the force of the prestressed spring element 30 and the hydraulic closing force, which results from the pressure in the pressure chamber 37 on the end face 13 of the valve member 12. If a high fuel pressure prevails in the pressure chamber 37, then the valve member 12 is held in its closed position, since the hydraulically effective surface of the pressure shoulder 17 is significantly smaller than that of the end face 13 of the valve member 12. If the control chamber 37 is relieved via the control bore 40, then moves the hydraulic force on the pressure shoulder 17, the valve member 12 against the force of the spring member 30 away from the valve seat 20, so that fuel is injected through the injection openings 22 in the manner described above in the combustion chamber 6 of the internal combustion engine. Since pressures of more than 100 MPa can prevail in the pressure chamber 18 and in the control chamber 37, the force of the spring element 30 plays only a minor role in the opening stroke movement of the valve member 12. The spring element 30 is mainly used to keep the valve member 12 in the closed combustion engine and thus in the absence of fuel pressure in the pressure chamber 18 and the control chamber 37 in the closed position.

In Figur 2 ist eine geschnittene perspektivische Darstellung des Ventilkörpers 5 im Bereich des Federelements 30 dargestellt. Das Ventilglied 12 ist hier der Übersichtlichkeit halber weggelassen worden. Die Hülse 34 ist einstückig mit dem Federelement 30 ausgebildet, so dass die Anlagefläche zwischen diesen beiden Teilen entfällt. Figur 3 zeigt eine vergrößerte Darstellung des Federelements 30 zusammen mit der Hülse 34 und einem Ringelement 42, das sich am gegenüberliegenden Ende zur Hülse 34 an das elastische Element 30 anschließt und über das sich das Federelement 30 direkt am Ventilglied 12 abstützt. Das Ringelement 42 kann hierbei ebenfalls einstückig mit dem Federelement 30 ausgebildet sein oder als separates Bauteil mit dem Federelement 30 verbunden werden, etwa durch Schweißen oder Löten. Das Federelement 30 ist als zylindrische Hülse ausgebildet, die an ihrer Wand mehrere Durchbrüche 45 aufweist, wodurch das Federelement 30 in Längsrichtung elastisch verformbar wird. Der genaue Aufbau des als zylindrische Hülse ausgebildeten Federelements 30 ist in Figur 4 dargestellt, wobei das Federelement 30 hier in unbelastetem Zustand gezeigt ist und in diesem Fall als separates Bauteil ohne die Hülse 34 und das Ringelement 42 gefertigt ist. Die Durchbrüche 45 des Federelements 30 sind schlitzförmig ausgebildet und weisen eine Längsachse 52 auf, die bezüglich der Längsachse 14 des Federelements 30 in einer Radialebene verläuft. Die Enden 47 der schlitzförmigen Durchbrüche 45 sind gerundet, um die Kerbspannungen an dieser Stelle beim Zusammenpressen des Federelements 30 zu vermindern. Um die Steifigkeit des Federelements 30 über die gesamte Lebensdauer zu erhalten, ist in jedem Fall zu verhindern, dass an den Enden 47 der Durchbrüche 45 eine plastische Verformung des Materials auftritt. Andernfalls würde sich das Federelement 30 irreversibel verformen, was die Steifigkeit ändern würde.In FIG. 2 is a sectional perspective view of the valve body 5 in the region of the spring element 30 shown. The valve member 12 has been omitted here for clarity. The sleeve 34 is formed integrally with the spring element 30, so that the contact surface between these two parts is eliminated. FIG. 3 shows an enlarged view of the spring element 30 together with the sleeve 34 and a ring member 42 which connects at the opposite end to the sleeve 34 to the elastic member 30 and over which the spring member 30 is supported directly on the valve member 12. The ring member 42 may also be formed integrally with the spring element 30 or be connected as a separate component with the spring element 30, such as by welding or soldering. The spring element 30 is designed as a cylindrical sleeve, which has a plurality of apertures 45 on its wall, whereby the spring element 30 is elastically deformable in the longitudinal direction. The exact structure of the formed as a cylindrical sleeve spring element 30 is in FIG. 4 shown, wherein the spring element 30 is shown here in the unloaded state and is made in this case as a separate component without the sleeve 34 and the ring member 42. The apertures 45 of the spring element 30 are slot-shaped and have a longitudinal axis 52 which extends with respect to the longitudinal axis 14 of the spring element 30 in a radial plane. The ends 47 of the slot-shaped openings 45 are rounded in order to reduce the notch stresses at this point during compression of the spring element 30. In order to maintain the rigidity of the spring element 30 over the entire service life, plastic deformation of the material is to be prevented in any case at the ends 47 of the openings 45. Otherwise, the spring element 30 would irreversibly deform, which would change the rigidity.

In einer Radialebene des Federelements 30 sind jeweils zwei schlitzförmige Durchbrüche 45 angeordnet, die durch einen Verbindungssteg 48 und einen diesem gegenüberliegenden zweiten Verbindungssteg 48' voneinander getrennt sind. Die in der benachbarten Radialebene liegenden Durchbrüche 45 sind gleich ausgestaltet, jedoch sind sie bezüglich der Längsachse 14 um 90° gedreht. Hierdurch ergeben sich zwischen den Verbindungsstegen 48 zweier aneinandergrenzender Radialebenen Kantilever 49, deren Durchbiegung bei Belastung des Federelements 30 dessen elastische Verformbarkeit bewirkt. Über die Dicke der Kantilever 49 und über deren Länge, die sich aus der Breite der Verbindungsstege 48 ergibt, lässt sich die Elastizität und damit die Federkonstante des Federelements 30 einstellen. Bevorzugte Abmessungen des Federelements 30 sind ein Außendurchmesser D von 4,0 mm bis 4,5 mm und eine Wandstärke S von 0,4 mm bis 0,5 mm. Die Breite der Verbindungsstege 48 ist etwa 0,8 mm und der Rundungsradius an den Enden 47 der Durchbrüche 45 etwa 0,4 mm bis 0,5 mm. Die Gesamthöhe H des Federelements 30 beträgt etwa 10 mm. Mit diesen Abmessungen erreicht man eine Federkonstante des Federelements 30 von etwa 30 N/mm. Der dafür benötigte Außendurchmesser des Federelements 30 ist deutlich geringer als der einer Schraubendruckfeder mit vergleichbarer Federkonstante.In a radial plane of the spring element 30, two slot-shaped apertures 45 are arranged, which are separated by a connecting web 48 and a second connecting web 48 'opposite thereto. In the the adjacent radial plane lying apertures 45 are configured the same, but they are rotated with respect to the longitudinal axis 14 by 90 °. This results in between the connecting webs 48 of two adjoining radial planes cantilever 49, the deflection causes 30 under load of the spring element whose elastic deformability. About the thickness of the cantilever 49 and over the length thereof, resulting from the width of the connecting webs 48, the elasticity and thus the spring constant of the spring element 30 can be adjusted. Preferred dimensions of the spring element 30 are an outer diameter D of 4.0 mm to 4.5 mm and a wall thickness S of 0.4 mm to 0.5 mm. The width of the connecting webs 48 is about 0.8 mm and the radius of curvature at the ends 47 of the apertures 45 about 0.4 mm to 0.5 mm. The total height H of the spring element 30 is about 10 mm. With these dimensions, a spring constant of the spring element 30 of about 30 N / mm is achieved. The required outer diameter of the spring element 30 is significantly lower than that of a helical compression spring with a comparable spring constant.

Das hier gezeigte Federelement 30 besteht aus zwei Halbzylindern, die an Schweißnähten 50 miteinander verbunden sind. Die Herstellung des Federelements 30 erfolgt beispielsweise dadurch, dass zwei Halbzylinder separat hergestellt werden, die dann an Schweißnähten 50 miteinander verbunden werden. Figur 5 zeigt einen Zwischenschritt eines der Halbzylinder, nämlich eine Federelementhälfte 130, die ein rechteckiges, ebenes Blech aus einem geeigneten Stahl darstellt. In die Federelementhälfte 130 werden Durchbrüche 45 beispielsweise durch Stanzen eingebracht. Die Federelementhälfte 130 wird anschließend gebogen, so dass die Seitenflächen 54 mit jeweils einer korrespondierenden Seitenfläche 54 einer zweiten Federelementhälfte 130 verbunden werden können, vorzugsweise durch Schweißen.The spring element 30 shown here consists of two half-cylinders, which are connected to welds 50 together. The production of the spring element 30 takes place, for example, in that two half cylinders are produced separately, which are then connected to each other at weld seams 50. FIG. 5 shows an intermediate step of one of the half-cylinders, namely a spring element half 130, which represents a rectangular, planar sheet of a suitable steel. In the spring element half 130 breakthroughs 45 are introduced, for example by punching. The spring element half 130 is then bent, so that the side surfaces 54 can each be connected to a corresponding side surface 54 of a second spring element half 130, preferably by welding.

Soll das Federelement 30 aus einem Stück, beispielsweise durch Tiefziehen, hergestellt werden, so entfallen die Schweißnähte 50. Die Durchbrüche 45 können in diesem Fall nicht durch Stanzen eingebracht werden, sondern beispielsweise mit Hilfe eines Lasers. Welches Herstellungsverfahren im einzelnen sinnvoll ist, hängt von der zu erwartenden mechanischen Belastung des Federelements 30 ab.If the spring element 30 is to be produced in one piece, for example by deep-drawing, then the welds 50 are dispensed with. The apertures 45 can not be introduced by punching in this case, but for example by means of a laser. Which manufacturing method makes sense in each case depends on the expected mechanical load of the spring element 30.

Neben der Beaufschlagung eines Ventilglieds 12 durch das Federelement 30 kann das erfindungsgemäße Federelement 30 auch an anderer Stelle in einem Kraftstoffeinspritzventil eingesetzt werden, wo der entsprechende Bauraum knapp ist und das Federelement eine möglichst geringe Ausdehnung aufweisen soll. Mögliche weitere Anwendungsbeispiele sind Magnetventile in Kraftstoffeinspritzventilen.In addition to the loading of a valve member 12 by the spring element 30, the spring element 30 according to the invention can also be used elsewhere in a fuel injection valve, where the corresponding space is scarce and the spring element should have the smallest possible extent. Possible further application examples are solenoid valves in fuel injection valves.

Claims (5)

  1. Fuel injection valve for internal combustion engines, with a housing (1) in which a valve element (12) is arranged movably and, by means of its movement counter to the elastic force of a spring element (30), controls the supply of fuel to the combustion chamber (6) of the internal combustion engine, wherein the spring element (30) is a cylindrical sleeve with a longitudinal axis (14), and the wall of the sleeve has apertures (45) which are separate from one another at a plurality of locations such that the spring element (30) can be deformed elastically in the direction of the longitudinal axis (14), characterized in that the ends (47) of the apertures (45) are rounded, and the apertures (45) have a longitudinal axis (52), with respect to which said apertures are symmetrical, and in that the apertures (45) are in the shape of a longitudinal slot, which longitudinal slot is constricted in the centre with respect to its longitudinal axis (52).
  2. Fuel injection valve according to Claim 1, characterized in that the apertures (45) in the wall of the spring element (30) run substantially in a radial plane of the longitudinal axis (14) of the spring element (30).
  3. Fuel injection valve according to Claim 2, characterized in that two identical apertures (45) lie in a radial plane of the spring element (30), the apertures (45) being separated from each other by connecting webs (48).
  4. Fuel injection valve according to Claim 3, characterized in that apertures (45) are arranged in at least two radial planes, the apertures of the one radial plane being rotated through 90° in relation to those of the adjacent radial plane.
  5. Fuel injection valve according to Claim 1, characterized in that the spring element (30) is arranged in an elastically prestressed manner in the housing (1).
EP03714674A 2002-03-26 2003-03-03 Fuel injection valve Expired - Lifetime EP1490594B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10213382A DE10213382A1 (en) 2002-03-26 2002-03-26 Fuel injection valve
DE10213382 2002-03-26
PCT/DE2003/000694 WO2003081023A1 (en) 2002-03-26 2003-03-03 Fuel injection valve

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EP1490594A1 EP1490594A1 (en) 2004-12-29
EP1490594B1 true EP1490594B1 (en) 2009-07-22

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EP03714674A Expired - Lifetime EP1490594B1 (en) 2002-03-26 2003-03-03 Fuel injection valve

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US (1) US7175112B2 (en)
EP (1) EP1490594B1 (en)
JP (1) JP2005520981A (en)
DE (2) DE10213382A1 (en)
WO (1) WO2003081023A1 (en)

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Also Published As

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US20050224604A1 (en) 2005-10-13
DE10213382A1 (en) 2003-10-16
US7175112B2 (en) 2007-02-13
EP1490594A1 (en) 2004-12-29
DE50311728D1 (en) 2009-09-03
WO2003081023A1 (en) 2003-10-02
JP2005520981A (en) 2005-07-14

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