EP3018335B1 - Fuel injector and method for producing a fuel injector - Google Patents

Fuel injector and method for producing a fuel injector Download PDF

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Publication number
EP3018335B1
EP3018335B1 EP15190117.0A EP15190117A EP3018335B1 EP 3018335 B1 EP3018335 B1 EP 3018335B1 EP 15190117 A EP15190117 A EP 15190117A EP 3018335 B1 EP3018335 B1 EP 3018335B1
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EP
European Patent Office
Prior art keywords
valve piece
clamping element
fuel injector
valve
clamping
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.)
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Application number
EP15190117.0A
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German (de)
French (fr)
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EP3018335A1 (en
Inventor
Lars Olems
Philipp Schott
Thomas Nierychlo
Axel Schnaufer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3018335A1 publication Critical patent/EP3018335A1/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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members

Definitions

  • the invention relates to a fuel injector, in particular a common rail injector for self-igniting internal combustion engines, according to the preamble of claim 1. Furthermore, the invention relates to a method for producing a fuel injector according to the invention.
  • a fuel injector according to the preamble of claim 1 is known from DE 10 2012 224 226 A1 the applicant known.
  • a valve piece is clamped by means of a valve clamping screw axially against a shoulder of a holding body.
  • the valve piece include a control room and, starting from the bottom of the control room, a drain hole with outlet throttle and drain diffuser arranged.
  • a drain hole with outlet throttle and drain diffuser arranged in addition, opens into the control chamber formed in the wall of the valve piece, an inlet throttle having inlet bore.
  • the control chamber in which the end portion of a nozzle needle dips serves in a known manner to control the movement of the nozzle needle by closing or releasing the drain hole in the direction of a low pressure region by means of an actuator.
  • valve piece Due to the steadily increasing system pressures in auto-ignition internal combustion engines, it is necessary to tighten the valve piece with a relatively large axial clamping force against the retaining shoulder of the holder body to ensure the tightness of the fuel injector. Due to the geometry of the valve piece and the arrangement of the valve clamping screw to the valve piece both areas with compressive stresses and those with tensile stresses are generated during clamping in the valve piece. In the case of the fuel injector known from the cited document, in which the outlet throttle or the outlet diffuser lies approximately at the level of an end face in which the valve clamping screw bears against the valve piece, relatively high tensile stresses occur in the region of the outlet throttle and the outlet diffuser. the have a significant negative impact on the fatigue strength of the valve piece.
  • a radially outer element comprises a radially inner element to form a press fit, so that in the radially inner element radially acting compressive stresses are generated, which counteract the caused due to the system pressure in the Injektorgepuruse compressive stresses in the radially inner element.
  • the invention has the object, a fuel injector according to the preamble of claim 1 such that the fatigue strength of the valve piece is improved.
  • valve member is at least partially radially surrounded by a clamping element which is adapted to generate a radially acting pressure force on the valve piece.
  • clamping element compressive stresses are generated in the valve member, which can be used in response to the position of the clamping element to counteract the tensile stresses occurring during assembly of the valve member in the holding body during axial clamping of the valve member or to reduce these.
  • the outer diameter of the valve piece is larger than the inner diameter of the clamping element, such that in the assembled state between the valve piece and the clamping element a press fit is formed.
  • the clamping element in which this can be manufactured in manufacturing technology particularly simple manner and at the same time over the circumference of the valve piece considered equal pressure forces generated, it is provided that the clamping element is sleeve-shaped with preferably constant wall thickness.
  • the clamping element in the installed state is arranged axially spaced from the valve clamping screw and the holding body. As a result, the clamping element does not come into contact with the holding body or the valve clamping screw during the axial clamping of the valve piece, so that no forces possibly influencing the compressive stresses are transmitted to the clamping element via these elements.
  • the clamping element is received with radial play within the holding body.
  • the coefficient of thermal expansion of the valve piece is equal to or greater than the thermal expansion coefficient of the clamping element. In other words, this means that with a warming of the valve piece and the clamping element, the valve piece always expands more than the clamping element, so that the radial compressive forces of the clamping element on the valve piece even increased and reduced in any case.
  • the invention also includes a method for producing a fuel injector according to the invention.
  • This method is inventively characterized in that cooled before joining the valve piece and / or the clamping element is heated / is.
  • the two joining partners can be axially without the risk of mechanical damage to the joining partners into each other or add with relatively little axial force.
  • the valve piece is clamped axially in the holding body by means of the valve clamping screw.
  • This preferred method has the advantage that the axial clamping of the valve piece in the holding body takes place only in a state in which the desired radial compressive stresses have been generated via the clamping element in the valve piece.
  • the Indian Fig. 1 shown fuel injector 10 is part of a common rail injection system, in particular for self-igniting internal combustion engines, and has an injector 11 with a holding body 12.
  • a high-pressure inlet 14 which is connected via a fuel line, not shown, with a fuel reservoir (rail).
  • a valve member 16 is inserted, in which partially an injection valve member 18 in the form of a nozzle needle or a push rod, which actuates a lower lying injection valve member, is added.
  • a control chamber 20 is formed, which is acted upon via an inlet throttle 22 of the entering from the high-pressure inlet 14 and under system pressure fuel.
  • the injection valve member 18 serves to close or release in the Fig. 1 injection openings, not shown.
  • the control chamber 20 in the valve piece 16 is depressurized via a drain hole 24 in a low pressure region or in a fuel return.
  • a drain hole 24 In the drain hole 24 is below an opening formed as a diffuser 25, i. below a valve seat 28, an outlet throttle 26.
  • the valve seat 28 of the drain hole 24 is closed in the region of the diffuser 25 by a spherical closing element 30.
  • the fuel injector 10 is exemplified, and not by way of limitation, actuated by a solenoid valve.
  • a magnet assembly of the solenoid valve includes an armature 32 which is radially guided in an armature guide 36 with play.
  • the armature guide 36 is in turn partially surrounded by a valve clamping screw 50, with which the valve member 16 is clamped in the holder body 12 axially against a formed in the holding body 12 retaining shoulder 13.
  • the armature 32 has a flat end face 34, which is arranged opposite a likewise flat end face 40 of a magnetic core 38.
  • the magnetic core 38 comprises a magnetic coil 42 radially.
  • the magnet assembly which comprises the magnet core 38, the magnet coil 42 and the armature 32, is radially encompassed by a magnet sleeve 44, which is screwed by means of a clamping nut 48 on the holding body 12. Furthermore, in the Fig. 1 recognizable that the armature 32 is acted upon by an armature spring 46 which presses the armature 32 in the valve seat 28.
  • valve seat 28 Upon energization of the magnetic coil 42 accommodated in the magnetic core 38, the valve seat 28 is opened by tightening the armature 32 and thus an outflow of fuel from the control chamber 20 via the drainage bore 24 into the mentioned low-pressure region of the fuel injector 10 or into the fuel return.
  • the valve piece 16 has on the side facing the retaining shoulder 13 on its periphery an inclined chamfer 15. Furthermore, the valve piece 16 forms on the valve clamping screw 50 facing end side at least in the region of the valve clamping screw 50 flat end face 51.
  • the diffuser 25 and the outlet throttle 26 are, viewed in the axial direction, arranged approximately at the level or slightly below the end face 51 of the valve piece 16. During axial clamping of the valve member 16 against the retaining shoulder 13 of the holding body 12 by means of the valve clamping screw 26 tensile stresses are generated in the region of the diffuser 25 and the outlet throttle 26, which can be at least partially reduced or equalized by the now described, inventive design of the fuel injector 10.
  • valve member 16 at least partially, in the illustrated embodiment, approximately between the region of the end face 51 of the valve member 16 and the chamfer 15 is surrounded by a clamping element 55 which generates a radially acting pressure force on the valve member 16, which In the area of the outlet throttle 26 and the diffuser 25 prevailing tensile stresses reduced.
  • a press fit is formed between the outer diameter of the valve piece 16 and the inner diameter of the clamping element 55.
  • the clamping element 55 is sleeve-shaped with preferably constant wall thickness. Furthermore, it is provided in the installed state of the clamping element 55, that between the clamping element 55 and the holding body 12, a radially encircling space 57 is formed.
  • the valve member 16 is cooled down and / or the clamping member 55 is heated / is.
  • the heating or cooling down of the addressed components serves to reduce the differences in diameter between the outer diameter of the valve piece 16 and the inner diameter of the clamping element 55 in the joining region, to a subsequent axial joining of the components avoid mechanical damage to the components.
  • a second step 62 it is preferably provided after joining the components, in a second step 62 by a waiting time to achieve an approximation of the temperatures of the valve member 16 and the clamping member 55, whereby the clamping member 55 shrinks or expands the valve member 16 in the joint area.
  • the desired compressive stresses in the joining region between the valve piece 16 and the clamping element 55 are generated.
  • a third step 63 it is provided to insert the assembly formed from the valve piece 16 and the clamping element 55, possibly together with other components, into the holding body 12 and to clamp it axially against the holding shoulder 13 of the holding body 12 by means of the valve clamping screw 50, to ensure the desired tightness of the injector 11.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoffinjektor, insbesondere einen Common-Rail-Injektor für selbstzündende Brennkraftmaschinen, nach dem Oberbegriff des Anspruchs 1. Ferner betrifft die Erfindung ein Verfahren zum Herstellen eines erfindungsgemäßen Kraftstoffinjektors.The invention relates to a fuel injector, in particular a common rail injector for self-igniting internal combustion engines, according to the preamble of claim 1. Furthermore, the invention relates to a method for producing a fuel injector according to the invention.

Ein Kraftstoffinjektor nach dem Oberbegriff des Anspruchs 1 ist aus der DE 10 2012 224 226 A1 der Anmelderin bekannt. Bei dem bekannten Kraftstoffinjektor ist ein Ventilstück mittels einer Ventilspannschraube axial gegen eine Schulter eines Haltekörpers verspannt. In dem Ventilstück sind unter anderem ein Steuerraum sowie, vom Grund des Steuerraums ausgehend, eine Ablaufbohrung mit Ablaufdrossel und Ablaufdiffusor angeordnet. Darüber hinaus mündet in den Steuerraum eine in der Wand des Ventilstücks ausgebildete, eine Zulaufdrossel aufweisende Zulaufbohrung. Der Steuerraum, in dem der Endbereich einer Düsennadel eintaucht, dient in bekannter Art und Weise der Steuerung der Bewegung der Düsennadel durch Verschließen bzw. Freigeben der Ablaufbohrung in Richtung eines Niederdruckbereichs mittels eines Aktuators.A fuel injector according to the preamble of claim 1 is known from DE 10 2012 224 226 A1 the applicant known. In the known fuel injector a valve piece is clamped by means of a valve clamping screw axially against a shoulder of a holding body. In the valve piece include a control room and, starting from the bottom of the control room, a drain hole with outlet throttle and drain diffuser arranged. In addition, opens into the control chamber formed in the wall of the valve piece, an inlet throttle having inlet bore. The control chamber in which the end portion of a nozzle needle dips, serves in a known manner to control the movement of the nozzle needle by closing or releasing the drain hole in the direction of a low pressure region by means of an actuator.

Aufgrund der stetig zunehmenden Systemdrücke bei selbstzündenden Brennkraftmaschinen ist es erforderlich, zur Sicherstellung der Dichtheit des Kraftstoffinjektors das Ventilstück mit einer relativ großen axialen Spannkraft gegen die Halteschulter des Halterkörpers zu verspannen. Aufgrund der Geometrie des Ventilstücks und der Anordnung der Ventilspannschraube zum Ventilstück werden beim Verspannen in dem Ventilstück sowohl Bereiche mit Druckspannungen als auch solche mit Zugspannungen erzeugt. Bei dem aus der genannten Schrift bekannten Kraftstoffinjektor, bei dem die Ablaufdrossel bzw. der Ablaufdiffusor in etwa in Höhe einer Stirnfläche liegt, in der auch die die Ventilspannschraube gegen das Ventilstück anliegt, kommt es im Bereich der Ablaufdrossel und des Ablaufdiffusors zu relativ hohen Zugspannungen, die einen erheblichen negativen Einfluss auf die Schwingfestigkeit des Ventilstücks haben.Due to the steadily increasing system pressures in auto-ignition internal combustion engines, it is necessary to tighten the valve piece with a relatively large axial clamping force against the retaining shoulder of the holder body to ensure the tightness of the fuel injector. Due to the geometry of the valve piece and the arrangement of the valve clamping screw to the valve piece both areas with compressive stresses and those with tensile stresses are generated during clamping in the valve piece. In the case of the fuel injector known from the cited document, in which the outlet throttle or the outlet diffuser lies approximately at the level of an end face in which the valve clamping screw bears against the valve piece, relatively high tensile stresses occur in the region of the outlet throttle and the outlet diffuser. the have a significant negative impact on the fatigue strength of the valve piece.

Darüber hinaus ist es aus der nachveröffentlichten DE 10 2013 226 569 A1 der Anmelderin bekannt, zur Erhöhung der Festigkeit eines Ventilgehäuses dieses aus zwei Elementen auszubilden. Dabei umfasst ein radial äußeres Element ein radial inneres Element unter Ausbildung einer Presspassung, so dass in dem radial inneren Element radial wirkende Druckspannungen erzeugt werden, die den infolge des Systemdrucks in dem Injektorgehäuse hervorgerufenen Druckspannungen im radial inneren Element entgegenwirken.In addition, it is from the post-published DE 10 2013 226 569 A1 Applicant known to increase the strength of a valve housing to form this of two elements. In this case, a radially outer element comprises a radially inner element to form a press fit, so that in the radially inner element radially acting compressive stresses are generated, which counteract the caused due to the system pressure in the Injektorgehäuse compressive stresses in the radially inner element.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, einen Kraftstoffinjektor nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass die Schwingfestigkeit des Ventilstücks verbessert wird.Based on the illustrated prior art, the invention has the object, a fuel injector according to the preamble of claim 1 such that the fatigue strength of the valve piece is improved.

Diese Aufgabe wird erfindungsgemäß bei einem Kraftstoffinjektor mit den kennzeichnenden Merkmalen des Anspruchs 1 dadurch gelöst, dass das Ventilstück zumindest bereichsweise von einem Spannelement radial umfasst ist, das dazu ausgebildet ist, eine radial wirkende Druckkraft auf das Ventilstück zu erzeugen.This object is achieved in a fuel injector with the characterizing features of claim 1, characterized in that the valve member is at least partially radially surrounded by a clamping element which is adapted to generate a radially acting pressure force on the valve piece.

Durch das erfindungsgemäß vorgesehene Spannelement werden in dem Ventilstück Druckspannungen erzeugt, die in Abhängigkeit von der Position des Spannelements dazu genutzt werden können, den bei der Montage des Ventilstücks in dem Haltekörper beim axialen Verspannen des Ventilstücks auftretenden Zugspannungen entgegenzuwirken bzw. diese zu reduzieren.By the inventively provided clamping element compressive stresses are generated in the valve member, which can be used in response to the position of the clamping element to counteract the tensile stresses occurring during assembly of the valve member in the holding body during axial clamping of the valve member or to reduce these.

Vorteilhafte Weiterbildungen des erfindungsgemäßen Kraftstoffinjektors sind in den Unteransprüchen aufgeführt.Advantageous developments of the fuel injector according to the invention are listed in the subclaims.

Zur Ausbildung der radialen Druckkraft auf das Ventilstück ist es vorgesehen, dass zwischen dem Ventilstück und dem Spannelement im unbelasteten Zustand der Außendurchmesser des Ventilstücks größer ist als der Innendurchmesser des Spannelements, derart, dass im gefügten Zustand zwischen dem Ventilstück und dem Spannelement eine Presspassung ausgebildet ist.To form the radial pressure force on the valve piece, it is provided that between the valve piece and the clamping element in the unloaded state the outer diameter of the valve piece is larger than the inner diameter of the clamping element, such that in the assembled state between the valve piece and the clamping element a press fit is formed.

In bevorzugter konstruktiver Ausgestaltung des Spannelements, bei der sich dieses in herstellungstechnisch besonders einfacher Art und Weise fertigen lässt und gleichzeitig über den Umfang des Ventilstücks betrachtet gleich große Druckkräfte erzeugt, ist es vorgesehen, dass das Spannelement hülsenförmig mit vorzugsweise konstanter Wanddicke ausgebildet ist.In a preferred constructive embodiment of the clamping element, in which this can be manufactured in manufacturing technology particularly simple manner and at the same time over the circumference of the valve piece considered equal pressure forces generated, it is provided that the clamping element is sleeve-shaped with preferably constant wall thickness.

Um bei der Montage des Ventilstücks in dem Haltekörper äußere Einflüsse durch in Wirkverbindung mit dem Spannelement angeordnete Elemente zu vermeiden, ist es bevorzugt vorgesehen, dass das Spannelement im Einbauzustand axial beabstandet von der Ventilspannschraube und dem Haltekörper angeordnet ist. Dadurch gelangt das Spannelement beim axialen Verspannen des Ventilstücks stirnseitig nicht in Kontakt mit dem Haltekörper bzw. der Ventilspannschraube, so dass über diese Elemente keine ggf. die Druckspannungen beeinflussenden Kräfte auf das Spannelement übertragen werden.In order to avoid external influences due to elements arranged in operative connection with the clamping element during assembly of the valve piece in the holding body, it is preferably provided that the clamping element in the installed state is arranged axially spaced from the valve clamping screw and the holding body. As a result, the clamping element does not come into contact with the holding body or the valve clamping screw during the axial clamping of the valve piece, so that no forces possibly influencing the compressive stresses are transmitted to the clamping element via these elements.

Ebenso ist es zur einfachen Montage sowie zur Vermeidung äußerer Einflüsse bevorzugt vorgesehen, dass das Spannelement mit radialem Spiel innerhalb des Haltekörpers aufgenommen ist.Likewise, it is preferably provided for easy installation and to avoid external influences, that the clamping element is received with radial play within the holding body.

Während des Betriebs des Kraftstoffinjektors ist dieser unterschiedlichen Betriebstemperaturen ausgesetzt, die beispielsweise von -30°C beim Kaltstart bis 150°C beim hoher Last und Außentemperaturen beträgt. Um zu vermeiden, dass aufgrund der Erwärmung des Kraftstoffinjektors die zwischen dem Ventilstück und dem Spannelement ausgebildete Presspassung reduziert wird, und dadurch die Druckspannungen bzw. Druckkräfte das Ventilstück herabgesetzt werden, kann es vorgesehen sein, dass der Wärmeausdehnungskoeffizient des Ventilstücks gleich groß oder größer ist als der Wärmeausdehnungskoeffizient des Spannelements. Mit anderen Worten gesagt bedeutet dies, dass sich bei einer Erwärmung des Ventilstücks und des Spannelements das Ventilstücks stets stärker ausdehnt als das Spannelement, so dass die radialen Druckkräfte von dem Spannelement auf das Ventilstück sogar noch erhöht und in keinem Fall reduziert werden.During operation of the fuel injector this is exposed to different operating temperatures, for example, from -30 ° C at cold start to 150 ° C at high load and outside temperatures. In order to avoid that due to the heating of the fuel injector formed between the valve piece and the clamping element press fit is reduced, and thereby the compressive stresses or compressive forces are reduced the valve piece, it may be provided that the coefficient of thermal expansion of the valve piece is equal to or greater than the thermal expansion coefficient of the clamping element. In other words, this means that with a warming of the valve piece and the clamping element, the valve piece always expands more than the clamping element, so that the radial compressive forces of the clamping element on the valve piece even increased and reduced in any case.

Die Erfindung umfasst auch ein Verfahren zum Herstellen eines erfindungsgemäßen Kraftstoffinjektors. Dieses Verfahren zeichnet sich erfindungsgemäß dadurch aus, dass vor dem Fügen das Ventilstück herabgekühlt und/oder das Spannelement erwärmt werden/wird. Bei einem derartigen Verfahren lassen sich die beiden Fügepartner ohne die Gefahr einer mechanischen Beschädigung der Fügepartner axial ineinander schieben bzw. mit relativ geringer axialer Kraft fügen.The invention also includes a method for producing a fuel injector according to the invention. This method is inventively characterized in that cooled before joining the valve piece and / or the clamping element is heated / is. In such a method, the two joining partners can be axially without the risk of mechanical damage to the joining partners into each other or add with relatively little axial force.

In bevorzugter Weiterbildung des erfindungsgemäßen Verfahrens ist es vorgesehen, dass nach dem Fügen des Ventilstücks und des Spannelements und vorzugsweise nach einer Wartezeit zur Angleichung der Temperaturen des Ventilstücks und des Spannelements das Ventilstück axial in dem Haltekörper mittels der Ventilspannschraube verspannt wird. Dieses bevorzugte Verfahren hat den Vorteil, dass die axiale Verspannung des Ventilstücks im Haltekörper erst in einem Zustand erfolgt, bei dem über das Spannelement in dem Ventilstück die gewünschten radialen Druckspannungen erzeugt worden sind.In a preferred embodiment of the method according to the invention, it is provided that after the joining of the valve piece and the clamping element and preferably after a waiting time for equalization of the temperatures of the valve piece and the clamping element, the valve piece is clamped axially in the holding body by means of the valve clamping screw. This preferred method has the advantage that the axial clamping of the valve piece in the holding body takes place only in a state in which the desired radial compressive stresses have been generated via the clamping element in the valve piece.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing.

Diese zeigt in:

Fig. 1
einen Ausschnitt aus einem erfindungsgemäßen Kraftstoffinjektors im Längsschnitt und
Fig. 2
ein Diagramm zur Erläuterung erfindungswesentlicher Schritte zum Herstellen des Kraftstoffinjektors.
This shows in:
Fig. 1
a section of a fuel injector according to the invention in longitudinal section and
Fig. 2
a diagram for explaining essential to the invention steps for producing the fuel injector.

Der in der Fig. 1 dargestellte erfindungsgemäße Kraftstoffinjektor 10 ist Bestandteil eines Common-Rail-Einspritzsystems, insbesondere für selbstzündende Brennkraftmaschinen, und weist ein Injektorgehäuse 11 mit einem Haltekörper 12 auf. In den Haltekörper 12 mündet seitlich ein Hochdruckzulauf 14, der über eine nicht dargestellte Kraftstoffleitung mit einem Kraftstoffspeicher (Rail) verbunden ist. Über den Hochdruckzulauf 14 wird unter Systemdruck stehender Kraftstoff dem Kraftstoffinjektor 10 zugeführt. Im Haltekörper 12 des Kraftstoffinjektors 10 ist ein Ventilstück 16 eingesetzt, in welchem bereichsweise ein Einspritzventilglied 18 in Form einer Düsennadel oder eine Druckstange, die ein weiter unten liegendes Einspritzventilglied betätigt, aufgenommen ist. Im Ventilstück 16 ist ein Steuerraum 20 ausgebildet, der über eine Zulaufdrossel 22 von dem aus dem Hochdruckzulauf 14 eintretenden und unter Systemdruck stehenden Kraftstoff beaufschlagt wird. Das Einspritzventilglied 18 dient zum Verschließen bzw. Freigeben von in der Fig. 1 nicht dargestellten Einspritzöffnungen.The Indian Fig. 1 shown fuel injector 10 is part of a common rail injection system, in particular for self-igniting internal combustion engines, and has an injector 11 with a holding body 12. In the holding body 12 opens laterally a high-pressure inlet 14 which is connected via a fuel line, not shown, with a fuel reservoir (rail). About the high-pressure inlet 14 is under System pressure fuel supplied to the fuel injector 10. In the holding body 12 of the fuel injector 10, a valve member 16 is inserted, in which partially an injection valve member 18 in the form of a nozzle needle or a push rod, which actuates a lower lying injection valve member, is added. In the valve piece 16, a control chamber 20 is formed, which is acted upon via an inlet throttle 22 of the entering from the high-pressure inlet 14 and under system pressure fuel. The injection valve member 18 serves to close or release in the Fig. 1 injection openings, not shown.

Der Steuerraum 20 im Ventilstück 16 ist über eine Ablaufbohrung 24 in einen Niederdruckbereich bzw. in einen Kraftstoffrücklauf druckentlastbar. In der Ablaufbohrung 24 befindet sich unterhalb einer als Diffusor 25 ausgebildeten Mündungsstelle, d.h. unterhalb eines Ventilsitzes 28, eine Ablaufdrossel 26. Der Ventilsitz 28 der Ablaufbohrung 24 ist im Bereich des Diffusors 25 durch ein kugelförmiges Schließelement 30 verschließbar.The control chamber 20 in the valve piece 16 is depressurized via a drain hole 24 in a low pressure region or in a fuel return. In the drain hole 24 is below an opening formed as a diffuser 25, i. below a valve seat 28, an outlet throttle 26. The valve seat 28 of the drain hole 24 is closed in the region of the diffuser 25 by a spherical closing element 30.

Der Kraftstoffinjektor 10 wird beispielhaft, und nicht einschränkend, mittels eines Magnetventils betätigt. Eine Magnetbaugruppe des Magnetventils umfasst einen Anker 32, der in einer Ankerführung 36 radial mit Spiel geführt ist. Die Ankerführung 36 ist ihrerseits von einer Ventilspannschraube 50 bereichsweise umgeben, mit der das Ventilstück 16 im Haltekörper 12 axial gegen eine im Haltekörper 12 ausgebildete Halteschulter 13 verspannt ist.The fuel injector 10 is exemplified, and not by way of limitation, actuated by a solenoid valve. A magnet assembly of the solenoid valve includes an armature 32 which is radially guided in an armature guide 36 with play. The armature guide 36 is in turn partially surrounded by a valve clamping screw 50, with which the valve member 16 is clamped in the holder body 12 axially against a formed in the holding body 12 retaining shoulder 13.

Der Anker 32 weist eine ebene Stirnfläche 34 auf, die gegenüber einer ebenfalls ebenen Stirnseite 40 eines Magnetkerns 38 angeordnet ist. Der Magnetkern 38 umfasst eine Magnetspule 42 radial. Die Magnetbaugruppe, die den Magnetkern 38, die Magnetspule 42 sowie den Anker 32 umfasst, ist von einer Magnethülse 44 radial umfasst, die mittels einer Spannmutter 48 am Haltekörper 12 verschraubt ist. Ferner ist in der Fig. 1 erkennbar, dass der Anker 32 durch eine Ankerfeder 46 kraftbeaufschlagt ist, die den Anker 32 in den Ventilsitz 28 drückt. Bei einer Bestromung der in dem Magnetkern 38 aufgenommenen Magnetspule 42 erfolgt durch Anziehen des Ankers 32 ein Öffnen des Ventilsitzes 28 und damit ein Abströmen aus Kraftstoff aus dem Steuerraum 20 über die Ablaufbohrung 24 in den erwähnten Niederdruckbereich des Kraftstoffinjektors 10 bzw. in den Kraftstoffrücklauf.The armature 32 has a flat end face 34, which is arranged opposite a likewise flat end face 40 of a magnetic core 38. The magnetic core 38 comprises a magnetic coil 42 radially. The magnet assembly, which comprises the magnet core 38, the magnet coil 42 and the armature 32, is radially encompassed by a magnet sleeve 44, which is screwed by means of a clamping nut 48 on the holding body 12. Furthermore, in the Fig. 1 recognizable that the armature 32 is acted upon by an armature spring 46 which presses the armature 32 in the valve seat 28. Upon energization of the magnetic coil 42 accommodated in the magnetic core 38, the valve seat 28 is opened by tightening the armature 32 and thus an outflow of fuel from the control chamber 20 via the drainage bore 24 into the mentioned low-pressure region of the fuel injector 10 or into the fuel return.

Das Ventilstück 16 weist auf der der Halteschulter 13 zugewandten Seite an seinem Umfang eine schräg verlaufende Fase 15 auf. Weiterhin bildet das Ventilstück 16 auf der der Ventilspannschraube 50 zugewandten Stirnseite eine zumindest im Bereich der Ventilspannschraube 50 ebene Stirnfläche 51 aus.The valve piece 16 has on the side facing the retaining shoulder 13 on its periphery an inclined chamfer 15. Furthermore, the valve piece 16 forms on the valve clamping screw 50 facing end side at least in the region of the valve clamping screw 50 flat end face 51.

Der Diffusor 25 bzw. die Ablaufdrossel 26 sind, in axialer Richtung betrachtet, in etwa in Höhe oder etwas unterhalb der Stirnfläche 51 des Ventilstücks 16 angeordnet. Beim axialen Verspannen des Ventilstücks 16 gegen die Halteschulter 13 des Haltekörpers 12 mittels der Ventilspannschraube 50 werden im Bereich des Diffusors 25 sowie der Ablaufdrossel 26 Zugspannungen erzeugt, welche durch die nunmehr beschriebene, erfindungsgemäße Ausbildung des Kraftstoffinjektors 10 zumindest teilweise reduziert bzw. egalisiert werden können.The diffuser 25 and the outlet throttle 26 are, viewed in the axial direction, arranged approximately at the level or slightly below the end face 51 of the valve piece 16. During axial clamping of the valve member 16 against the retaining shoulder 13 of the holding body 12 by means of the valve clamping screw 26 tensile stresses are generated in the region of the diffuser 25 and the outlet throttle 26, which can be at least partially reduced or equalized by the now described, inventive design of the fuel injector 10.

Erfindungsgemäß ist es vorgesehen, dass das Ventilstück 16 zumindest bereichsweise, im dargestellten Ausführungsbeispiel in etwa zwischen dem Bereich der Stirnfläche 51 des Ventilstücks 16 und der Fase 15 von einem Spannelement 55 umgeben ist, das eine radial wirkende Druckkraft auf das Ventilstück 16 erzeugt, welche die im Bereich der Ablaufdrossel 26 und des Diffusors 25 herrschenden Zugspannungen reduziert. Hierzu ist zwischen dem Außendurchmesser des Ventilstücks 16 und dem Innendurchmesser des Spannelements 55 eine Presspassung ausgebildet. Das Spannelement 55 ist hülsenförmig mit vorzugsweise konstanter Wanddicke ausgebildet. Weiterhin ist es im Einbauzustand des Spannelements 55 vorgesehen, dass zwischen dem Spannelement 55 und dem Haltkörper 12 ein radial umlaufender Freiraum 57 ausgebildet ist.According to the invention it is provided that the valve member 16 at least partially, in the illustrated embodiment, approximately between the region of the end face 51 of the valve member 16 and the chamfer 15 is surrounded by a clamping element 55 which generates a radially acting pressure force on the valve member 16, which In the area of the outlet throttle 26 and the diffuser 25 prevailing tensile stresses reduced. For this purpose, a press fit is formed between the outer diameter of the valve piece 16 and the inner diameter of the clamping element 55. The clamping element 55 is sleeve-shaped with preferably constant wall thickness. Furthermore, it is provided in the installed state of the clamping element 55, that between the clamping element 55 and the holding body 12, a radially encircling space 57 is formed.

Entsprechend der Darstellung der Fig. 2 ist es während der Fertigung des Kraftstoffinjektors 10 in einem zeitlich ersten Schritt 61 vorgesehen, dass vor dem Fügen des Spannelements 55 mit dem Ventilstück 16 das Ventilstück 16 herabgekühlt und/oder das Spannelement 55 erwärmt werden/wird. Das Erwärmen bzw. Herabkühlen der angesprochenen Bauteile dient dazu, die Durchmesserunterschiede zwischen dem Außendurchmesser des Ventilstücks 16 und dem Innendurchmesser des Spannelements 55 im Fügebereich zu reduzieren, um beim nachfolgenden axialen Fügen der Bauteile eine mechanische Beschädigung der Bauteile zu vermeiden. Anschließend ist es nach dem Fügen der Bauteile bevorzugt vorgesehen, in einem zweiten Schritt 62 durch eine Wartezeit eine Angleichung der Temperaturen des Ventilstücks 16 und des Spannelements 55 zu erzielen, wodurch das Spannelement 55 schrumpft bzw. sich das Ventilstück 16 im Fügebereich ausdehnt. Dadurch werden die erwünschten Druckspannungen im Fügebereich zwischen dem Ventilstück 16 und dem Spannelement 55 erzeugt. Zuletzt ist es in einem dritten Schritt 63 vorgesehen, die aus dem Ventilstück 16 und dem Spannelement 55 ausgebildete Baugruppe, ggf. zusammen mit anderen Bauteilen, in den Haltekörper 12 einzusetzen und mittels der Ventilspannschraube 50 axial gegen die Halteschulter 13 des Haltekörpers 12 zu verspannen, um die gewünschte Dichtheit des Injektorgehäuses 11 zu gewährleisten.According to the presentation of the Fig. 2 it is provided during the production of the fuel injector 10 in a temporally first step 61, that before joining the clamping member 55 with the valve member 16, the valve member 16 is cooled down and / or the clamping member 55 is heated / is. The heating or cooling down of the addressed components serves to reduce the differences in diameter between the outer diameter of the valve piece 16 and the inner diameter of the clamping element 55 in the joining region, to a subsequent axial joining of the components avoid mechanical damage to the components. Subsequently, it is preferably provided after joining the components, in a second step 62 by a waiting time to achieve an approximation of the temperatures of the valve member 16 and the clamping member 55, whereby the clamping member 55 shrinks or expands the valve member 16 in the joint area. As a result, the desired compressive stresses in the joining region between the valve piece 16 and the clamping element 55 are generated. Finally, in a third step 63, it is provided to insert the assembly formed from the valve piece 16 and the clamping element 55, possibly together with other components, into the holding body 12 and to clamp it axially against the holding shoulder 13 of the holding body 12 by means of the valve clamping screw 50, to ensure the desired tightness of the injector 11.

Claims (10)

  1. Fuel injector (10), in particular common-rail injector for auto-ignition internal combustion engines, having a a valve piece (16) in which an outflow bore (24) with an outflow throttle (26) is formed via which a control chamber (20) can be relieved of pressure to a low-pressure region, wherein the valve piece (16) can be clamped axially against a holding body (12) by means of a valve clamping screw (50),
    characterized
    in that the valve piece (16) is at least regionally radially encompassed by a clamping element (55) which is designed to generate a radially acting pressure force on the valve piece (16).
  2. Fuel injector according to Claim 1,
    characterized
    in that, for the generation of the pressure force between the valve piece (16) and the clamping element (55), in the unloaded state the outer diameter of the valve piece (16) in the joining region with the clamping element (55) is greater than the inner diameter of the clamping element (55), such that, in the joined state, an interference fit is formed between the valve piece (16) and the clamping element (55).
  3. Fuel injector according to Claim 1 or 2,
    characterized
    in that the clamping element (55) is of sleeve-like form with a preferably constant wall thickness.
  4. Fuel injector according to one of Claims 1 to 3,
    characterized
    in that the clamping element (55) is, in the installed state, arranged axially spaced apart from the valve clamping screw (50) and from the holding body (12).
  5. Fuel injector according to one of Claims 1 to 4,
    characterized
    in that the clamping element (55) is received with a radial clearance within the holding body (12).
  6. Fuel injector according to one of Claims 1 to 5,
    characterized
    in that the valve clamping screw (50) is arranged radially spaced apart from the outflow bore (24) in the valve piece (16) and bears against a face surface (51) of the valve piece (16).
  7. Fuel injector according to one of Claims 1 to 6,
    characterized
    in that the outflow throttle (26) is, as viewed in the axial direction, arranged approximately at the level of the face surface (51) of the valve piece (16).
  8. Fuel injector according to one of Claims 1 to 7,
    characterized
    in that the coefficient of thermal expansion of the valve piece (16) is equal to or greater than the coefficient of thermal expansion of the clamping element (55).
  9. Method for producing a fuel injector (10) according to one of Claims 1 to 8,
    characterized
    in that, before the joining, the valve piece (16) is cooled and/or the clamping element (55) is heated.
  10. Method according to Claim 9,
    characterized
    in that, after the joining of the valve piece (16) and of the clamping element (55), and preferably after a waiting time for the equalization of the temperatures of the valve piece (16) and of the clamping element (55), the valve piece (16) is clamped axially in the holding body (12) by means of the valve clamping screw (50).
EP15190117.0A 2014-11-07 2015-10-16 Fuel injector and method for producing a fuel injector Active EP3018335B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014222815.8A DE102014222815A1 (en) 2014-11-07 2014-11-07 Fuel injector and method of manufacturing a fuel injector

Publications (2)

Publication Number Publication Date
EP3018335A1 EP3018335A1 (en) 2016-05-11
EP3018335B1 true EP3018335B1 (en) 2017-08-16

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Country Link
EP (1) EP3018335B1 (en)
DE (1) DE102014222815A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108223222A (en) * 2018-03-28 2018-06-29 南岳电控（衡阳）工业技术股份有限公司 A kind of fuel oil injector for reducing metering servovalve deformation

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5304861B2 (en) * 2010-12-17 2013-10-02 株式会社デンソー Fuel injection device
AT512297B1 (en) * 2012-02-07 2013-07-15 Bosch Gmbh Robert THREAD CONNECTION OF HIGH-PRESSURE MEDIUM LEADING COMPONENTS OF AN INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
DE102012224226A1 (en) 2012-12-21 2014-06-26 Robert Bosch Gmbh Fuel injector, particularly common rail injector for compression-ignition internal combustion engines, has closing element coupled with magnet armature through intermediate element, which has spherical bearing surface for closing element
DE102013226569A1 (en) 2013-12-19 2015-06-25 Robert Bosch Gmbh Fuel injector and method of manufacturing a fuel injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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EP3018335A1 (en) 2016-05-11

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