EP1105639A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1105639A1
EP1105639A1 EP99962123A EP99962123A EP1105639A1 EP 1105639 A1 EP1105639 A1 EP 1105639A1 EP 99962123 A EP99962123 A EP 99962123A EP 99962123 A EP99962123 A EP 99962123A EP 1105639 A1 EP1105639 A1 EP 1105639A1
Authority
EP
European Patent Office
Prior art keywords
armature
fuel injection
spring
valve needle
spring element
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.)
Granted
Application number
EP99962123A
Other languages
German (de)
French (fr)
Other versions
EP1105639B1 (en
Inventor
Ferdinand Reiter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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
Publication of EP1105639A1 publication Critical patent/EP1105639A1/en
Application granted granted Critical
Publication of EP1105639B1 publication Critical patent/EP1105639B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0685—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • the fuel injector has a valve closing body connected to a valve needle, which cooperates with a valve seat surface formed on a valve seat body to form a sealing seat.
  • a magnet coil is provided which interacts with a magnet armature which is movable on the valve needle between a first stop limiting the movement of the armature in the stroke direction of the valve needle and a second stop limiting the movement of the armature against the stroke direction.
  • the axial movement play of the armature defined by the two stops leads within certain limits to a decoupling of the inertial mass of the valve needle and the valve closing body on the one hand and the inertial mass of the armature on the other hand.
  • Valve seat body moved back against the spray direction. Valve bumpers can therefore occur even more frequently with this type of fuel injector.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that possible bouncing of the valve needle can be avoided even more effectively. This results in high long-term stability, since the spring element has a long service life compared to an elastomer material and, in particular, cannot be destroyed by the fuel. A targeted adjustment of the damping properties is possible to the extent that certain materials, shapes and preloads are used for the spring element.
  • the spring element serves firstly as a lower second stop for the armature, secondly as a damping element that continuously brakes the movement of the armature and in this way prevents or severely restricts the valve needle from bouncing on the valve seat surface, and thirdly as a sliding spring that pushes the armature into it Presses the rest position to the system at the first stop.
  • a very high level of functional integration is advantageously achieved with one component of the spring element.
  • the spring element according to the invention is advantageously simple and inexpensive to manufacture, in
  • Fuel injector can be mounted and adjusted on the valve needle.
  • the spring element It is advantageous to design the spring element with a shaft and a plurality of spring arms extending from the shaft. It is advisable to use a spring steel sheet, which is brought into a desired mushroom shape by deep drawing and punching.
  • FIG. 1 shows an embodiment of a fuel injector according to the invention in a sectional view
  • FIG. 2 shows a detail from FIG. 1 around the armature in an enlarged view
  • FIG. 3 shows a section along the line III-III in FIG. 2
  • FIG. 4 shows an alternative embodiment of the as a damping spring serving spring element in an analogous representation to Figure 3 and Figure 5 is a plan view of a spring element.
  • FIG. 1 shows a fuel injection valve 1 according to the invention in a partially sectioned illustration.
  • the fuel injection valve 1 is used to inject Fuel in a mixture-compressing, spark-ignited internal combustion engine.
  • the exemplary embodiment shown can be used as a high-pressure injection valve for the direct injection of fuel, in particular gasoline, into the combustion chamber of an internal combustion engine.
  • the fuel injector 1 has, in the exemplary embodiment, a valve closing body 3 which is integrally connected to a valve needle 2 and which cooperates with a valve seat surface formed on a valve seat body 4 to form a sealing seat.
  • the valve seat body 4 is fastened in a tubular valve seat support 5, which can be inserted into a receiving bore of a cylinder head of the internal combustion engine and is sealed by means of a seal 6.
  • the valve seat support 5 is inserted at its inlet end 7 into a longitudinal bore 8 of a housing body 9 and sealed against the housing body 9 by means of a sealing ring 10.
  • the end 7 of the valve seat carrier 5 is prestressed by means of a threaded ring 11, a stroke adjusting disk 14 being clamped between a step 12 of the housing body 9 and an upper end face 13 of the valve seat carrier 5.
  • an armature 17 is drawn against a stop surface 18 of the housing body 9, the housing body 9 being formed upstream of the stop surface 18 as a magnetic inner pole, to which the
  • Stop surface 18 starting in the downstream direction connects a thin-walled magnetic throttle point 19.
  • the armature 17 due to the abutment of its upstream end face 35 against a stop body 20 which forms a first stop, takes on the Stop body 20 firmly connected valve needle 2 and the valve closing body 3 with.
  • the valve needle 2 is connected to the stop body 20 by a weld 22, for example.
  • the movement of the valve needle 2 takes place against a return spring 23 which is arranged between an adjusting sleeve 24 and the stop body 20.
  • the fuel flows through an axial bore 30 of the housing body 9 and at least one axial bore 31 provided in the armature 17 and via axial bores 33 provided in a guide disk 32 into a longitudinal opening 34 of the valve seat carrier 5 up to the sealing seat of the fuel injection valve 1.
  • the armature 17 is arranged movably on the valve needle 2 between the stop body 20 and a spring element 25 designed as a sliding spring and damping spring and serving as a second stop. Due to the spring force effect of the spring element 25, the armature 17 is in the non-excited rest position on the
  • Stop body 20 held in contact.
  • the spring element 25 is firmly connected to the valve needle 2.
  • Decoupling of the inert masses of the armature 17 on the one hand and the valve needle 2 and the valve closing body 3 on the other hand is achieved by the movement play of the armature 17 created between the stop body 20 and the spring element 25.
  • the armature 17 is not abruptly decelerated when the valve closing body 3 strikes the valve seat surface 26, but moves against the spring element 25, by means of which the armature 17 is braked in its movement.
  • the spring element 25 causes damping the stop of the armature 17 on the second armature stop opposite the stop body 20, which here is the spring element 25 itself according to the invention.
  • FIG. 2 shows the detail according to the invention around the armature 17 on a changed scale.
  • the arrangement of the axially movable armature 17 between its two stops is particularly clear, the stop body 20 being shown in a simplified construction compared to FIG. 1.
  • the spring element 25 serves firstly as a lower stop for the armature 17, secondly as a damping element which continuously brakes the movement of the armature 17 and in this way prevents or severely restricts the valve needle 2 from bouncing on the valve seat surface 26, and thirdly as a sliding spring which the
  • Anchor 17 presses into its rest position to rest against the stop body 20.
  • a very high level of functional integration is advantageously achieved with one component.
  • the spring element 25 is advantageously designed with a tubular shaft 38 and with a plurality of spring arms 39 extending therefrom.
  • the shaft 38 of the spring element 25 directly engages around the valve needle 2 and lies against it.
  • Two different embodiments of the shaft 38 are conceivable, as shown in FIGS. 3 and 4, which represent sections along the line III-III in FIG.
  • the shaft 38 lies directly against the circumference of the valve needle 2, which has a circular cross section, in the form of a sleeve.
  • the shaft 38 according to FIG. 4 is designed with, for example, three axially extending ribs 41 which protrude from the valve needle 2 and are arranged at a respective distance of 120 °.
  • These axial ribs 41 increase the radial elasticity of the spring element 25 and allow greater tolerances for the Establishing a firm connection on the valve needle 2 necessary press fit. In addition, a large contact surface is created in this way in order to be able to move the spring element 25 axially on the valve needle 2, which is necessary for the assembly and adjustment of the spring element 25.
  • Anchor 17 can be excluded.
  • the radial end of the spring arms 39 form spring arm ends 44 behind the outer regions 42 serving as armature supports, which are again bent away from the armature 17, so that no sharp edges lie against the armature 17.
  • FIG. 5 shows a plan view of a spring element 25 with six spring arms 39 distributed over the circumference.
  • the spring arms 39 have, for example, accordingly of the course of the bending moment radially outwards to a smaller width than towards the shaft 38.

Abstract

A fuel injection valve (1) for fuel injection systems of internal combustion engines, comprising a magnetic coil (15), an armature (17) which can be impinged upon by the magnetic coil (15) in the direction of lift counter to the action of a return spring (23), in addition to a valve needle (2) which is connected to a valve closing body (3). The armature (17) can move between a first stop (20) which is connected to the valve needle (2) and limits the movement of said armature (17) in the direction of lift, and a second stop (25) which is connected to the valve needle (2) and which limits the movement of the armature (17) counter to the direction of lift. The second stop is configured as a spring element (25).

Description

BrennstoffeinspritzventilFuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs .The invention relates to a fuel injector according to the preamble of the main claim.
Aus der US-PS 5,299,776 ist bereits einFrom US-PS 5,299,776 is already a
Brennstoffeinspritzventil nach dem Oberbegriff des AnspruchsFuel injection valve according to the preamble of the claim
1 bekannt. Das Brennstoffeinspritzventil hat einen mit einer Ventilnadel verbundenen Ventilschließkörper, der mit einer an einem Ventilsitzkörper ausgebildeten Ventilsitzfläche zu einem Dichtsitz zusammenwirkt. Zur elektromagnetischen Betätigung des Brennstoffeinspritzventils ist eine Magnetspule vorgesehen, die mit einem Magnetanker zusammenwirkt, der an der Ventilnadel zwischen einem die Bewegung des Ankers in der Hubrichtung der Ventilnadel begrenzenden ersten Anschlag und einem die Bewegung des Ankers entgegen der Hubrichtung begrenzenden zweiten Anschlag beweglich ist. Das durch die beiden Anschläge festgelegte axiale Bewegungsspiel des Ankers führt in gewissen Grenzen zu einer Entkopplung der trägen Masse der Ventilnadel und des Ventilschließkörpers einerseits und der trägen Masse des Ankers andererseits. Dadurch wird einem Zurückprallen des Ventilschließkörpers von der Ventilsitzfläche beim Schließen des Brennstoffeinspritzventils in gewissen Grenzen entgegengewirkt. Preller der Ventilnadel bzw. des Ventilschließkörpers führen zu einem unkontrollierten, kurzzeitigen Öffnen des Brennstoffeinspritzventils und somit zu einer nicht reproduzierbaren Zumessmenge des Brennstoffs und zu einem unkontrollierten Einspritzverhalten. Da jedoch die axiale Lage des Ankers bezüglich der Ventilnadel durch die freie Beweglichkeit des Ankers gegenüber der Ventilnadel vollkommen Undefiniert ist, werden Preller nur in beschränktem Maße vermieden. Insbesondere wird nicht vermieden, dass der Anker bei der Schließbewegung des Brennstoffeinspritzventils auf den dem Ventilschließkörper zugewandten Anschlag auftrifft und seinen Impuls schlagartig auf die Ventilnadel und somit auf den Ventilschließkörper überträgt.1 known. The fuel injector has a valve closing body connected to a valve needle, which cooperates with a valve seat surface formed on a valve seat body to form a sealing seat. For the electromagnetic actuation of the fuel injector, a magnet coil is provided which interacts with a magnet armature which is movable on the valve needle between a first stop limiting the movement of the armature in the stroke direction of the valve needle and a second stop limiting the movement of the armature against the stroke direction. The axial movement play of the armature defined by the two stops leads within certain limits to a decoupling of the inertial mass of the valve needle and the valve closing body on the one hand and the inertial mass of the armature on the other hand. This prevents the valve closing body from rebounding from the valve seat surface when the valve is closed Counteracted fuel injector within certain limits. Bumpers of the valve needle or the valve closing body lead to an uncontrolled, brief opening of the fuel injection valve and thus to a non-reproducible metering quantity of the fuel and to an uncontrolled injection behavior. However, since the axial position of the armature with respect to the valve needle is completely undefined due to the free movement of the armature relative to the valve needle, bouncers are only avoided to a limited extent. In particular, it is not avoided that the armature strikes the stop facing the valve closing body during the closing movement of the fuel injection valve and suddenly transmits its impulse to the valve needle and thus to the valve closing body.
Um das Aufprallen des Ankers auf dem dem Ventilschließkörper zugewandten Anschlag zu dämpfen, ist es aus der US-PS 4,766,405 bekannt, zwischen dem Anker und dem Anschlag einen Dämpfungskörper aus einem Elastomerwerkstoff, wie Gummi, anzuordnen. Solche Werkstoffe haben den Nachteil, dass diese in ihrem Dämpfungsverhalten stark temperaturabhängig sind und die DämpfungsWirkung mit einem Ansteigen der Temperatur abnimmt. Außerdem ist die Langzeitstabilität von Elastomeren begrenzt, insbesondere wenn diese mit dem abzuspritzenden Brennstoff in Berührung kommen. Die Montage einer Dämpfungsscheibe aus einem Elastomerwerkstoff ist zudem aufwendig. Eine gezielte Einstellung der Dämpfungseigenschaften ist ebenfalls nicht möglich.In order to dampen the impact of the armature on the stop facing the valve closing body, it is known from US Pat. No. 4,766,405 to arrange a damping body made of an elastomer material, such as rubber, between the armature and the stop. Such materials have the disadvantage that their damping behavior is strongly temperature-dependent and that the damping effect decreases as the temperature rises. In addition, the long-term stability of elastomers is limited, especially if they come into contact with the fuel to be sprayed. The assembly of a damping disc made of an elastomer material is also complex. A targeted adjustment of the damping properties is also not possible.
Aus der US-PS 5,236,173 ist es bekannt, zwischen dem Ventilsitzkörper und einem Ventilsitzträger, an welchem der Ventilsitzkörper montiert ist, eine Dämpfungsfeder in Form einer Tellerfeder vorzusehen, um zu erreichen, dass der Ventilschließkörper an der an dem Ventilsitzkörper ausgebildeten Ventilsitzfläche weich anschlägt. Diese Art der Dämpfung hat jedoch den Nachteil, dass der Ventilsitzkörper nach dem Anschlagen des Ventilschließkörpers in Abspritzrichtung durchschwingt, während der Ventilschließkörper entweder stehen bleibt oder aufgrund der Impulsumkehr sich sogar von demFrom US Pat. No. 5,236,173 it is known to provide a damping spring in the form of a plate spring between the valve seat body and a valve seat support on which the valve seat body is mounted, in order to achieve that the valve closing body on the valve seat body trained valve seat surface strikes softly. However, this type of damping has the disadvantage that the valve seat body swings through in the spray direction after the valve closing body has struck, while the valve closing body either stops or even moves away from it due to the reversal of the pulse
Ventilsitzkörper entgegen der Abspritzrichtung zurückbewegt. Ventilpreller können deshalb bei dieser Bauform des Brennstoffeinspritzventils sogar noch in verstärktem Maße auftreten.Valve seat body moved back against the spray direction. Valve bumpers can therefore occur even more frequently with this type of fuel injector.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat den Vorteil, dass eventuelle Preller der Ventilnadel noch wirkungsvoller vermieden werden können. Es ergibt sich eine hohe Langzeitstabilität, da das Federelement gegenüber einem Elastomerwerkstoff eine hohe Lebensdauer hat und insbesondere vom Brennstoff nicht zerstörbar ist. Eine gezielte Einstellung der Dämpfungseigenschaften ist insofern möglich, dass bestimmte Materialien, Formen und Vorspannungen für das Federelement genutzt werden.The fuel injector according to the invention with the characterizing features of the main claim has the advantage that possible bouncing of the valve needle can be avoided even more effectively. This results in high long-term stability, since the spring element has a long service life compared to an elastomer material and, in particular, cannot be destroyed by the fuel. A targeted adjustment of the damping properties is possible to the extent that certain materials, shapes and preloads are used for the spring element.
Das Federelement dient erstens als unterer zweiter Anschlag für den Anker, zweitens als Dämpfungselement , das die Bewegung des Ankers kontinuierlich abbremst und auf diese Weise ein Prellen der Ventilnadel an der Ventilsitzfläche vermeidet bzw. stark einschränkt, und drittens als Schiebefeder, die den Anker in seine Ruhestellung zur Anlage am ersten Anschlag drückt. In vorteilhafter Weise wird mit dem einen Bauteil des Federelements eine sehr hohe Funktionsintegration erreicht. Das erfindungsgemäße Federelement ist in vorteilhafter Weise einfach und kostengünstig herstellbar, imThe spring element serves firstly as a lower second stop for the armature, secondly as a damping element that continuously brakes the movement of the armature and in this way prevents or severely restricts the valve needle from bouncing on the valve seat surface, and thirdly as a sliding spring that pushes the armature into it Presses the rest position to the system at the first stop. A very high level of functional integration is advantageously achieved with one component of the spring element. The spring element according to the invention is advantageously simple and inexpensive to manufacture, in
Brennstoffeinspritzventil auf der Ventilnadel montierbar und einstellbar.Fuel injector can be mounted and adjusted on the valve needle.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims allow advantageous developments and improvements of the fuel injector specified in the main claim.
Von Vorteil ist es, das Federelement mit einem Schaft und mehreren von dem Schaft ausgehenden Federarmen auszubilden. Dabei bietet es sich an, ein Federstahlblech zu verwenden, welches durch Tiefziehen und Stanzen in eine gewünschte Pilzform gebracht wird.It is advantageous to design the spring element with a shaft and a plurality of spring arms extending from the shaft. It is advisable to use a spring steel sheet, which is brought into a desired mushroom shape by deep drawing and punching.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgendenEmbodiments of the invention are shown in simplified form in the drawing and in the following
Beschreibung näher erläutert. Es zeigen Figur 1 ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils in einer geschnittenen Darstellung, Figur 2 einen Ausschnitt aus Figur 1 rund um den Anker in einer vergrößerten Darstellung, Figur 3 einen Schnitt entlang der Linie III-III in Figur 2, Figur 4 eine alternative Ausführung des als Dämpfungsfeder dienenden Federelements in einer analogen Darstellung zu Figur 3 und Figur 5 eine Draufsicht auf ein Federelement.Description explained in more detail. 1 shows an embodiment of a fuel injector according to the invention in a sectional view, FIG. 2 shows a detail from FIG. 1 around the armature in an enlarged view, FIG. 3 shows a section along the line III-III in FIG. 2, and FIG. 4 shows an alternative embodiment of the as a damping spring serving spring element in an analogous representation to Figure 3 and Figure 5 is a plan view of a spring element.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Figur 1 zeigt in einer auszugsweise geschnittenen Darstellung ein erfindungsgemäßes Brennstoffeinspritzventil 1. Das Brennstoffeinspritzventil 1 dient zum Einspritzen von Brennstoff bei einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine. Das dargestellte Ausführungsbeispiel ist dabei als Hochdruck-Einspritzventil zum direkten Einspritzen von Brennstoff, insbesondere von Benzin, in den Brennraum einer Brennkraftmaschine verwendbar.FIG. 1 shows a fuel injection valve 1 according to the invention in a partially sectioned illustration. The fuel injection valve 1 is used to inject Fuel in a mixture-compressing, spark-ignited internal combustion engine. The exemplary embodiment shown can be used as a high-pressure injection valve for the direct injection of fuel, in particular gasoline, into the combustion chamber of an internal combustion engine.
Das Brennstoffeinspritzventil 1 weist einen im Ausführungsbeispiel einstückig mit einer Ventilnadel 2 verbundenen Ventilschließkörper 3 auf, der mit einer an einem Ventilsitzkörper 4 ausgebildeten Ventilsitzfläche zu einem Dichtsitz zusammenwirkt. Der Ventilsitzkörper 4 ist in einem rohrförmigen Ventilsitzträger 5 befestigt, der in eine Aufnahmebohrung eines Zylinderkopfes der Brennkraftmaschine einführbar ist und mittels einer Dichtung 6 abgedichtet ist. Der Ventilsitzträger 5 ist an seinem zulaufseitigen Ende 7 in eine Längsbohrung 8 eines Gehäusekörpers 9 eingesetzt und gegen den Gehäusekörper 9 mittels eines Dichtrings 10 abgedichtet. Das Ende 7 des Ventilsitzträgers 5 ist mittels eines Gewinderings 11 vorgespannt, wobei zwischen einer Stufe 12 des Gehäusekörpers 9 und einer oberen Stirnfläche 13 des Ventilsitzträgers 5 eine Hubeinstellscheibe 14 eingespannt ist .The fuel injector 1 has, in the exemplary embodiment, a valve closing body 3 which is integrally connected to a valve needle 2 and which cooperates with a valve seat surface formed on a valve seat body 4 to form a sealing seat. The valve seat body 4 is fastened in a tubular valve seat support 5, which can be inserted into a receiving bore of a cylinder head of the internal combustion engine and is sealed by means of a seal 6. The valve seat support 5 is inserted at its inlet end 7 into a longitudinal bore 8 of a housing body 9 and sealed against the housing body 9 by means of a sealing ring 10. The end 7 of the valve seat carrier 5 is prestressed by means of a threaded ring 11, a stroke adjusting disk 14 being clamped between a step 12 of the housing body 9 and an upper end face 13 of the valve seat carrier 5.
Zur elektromagnetischen Betätigung des Brennstoffeinspritzventils 1 dient eine Magnetspule 15, die auf einen Spulenträger 16 gewickelt ist. Bei elektrischer Erregung der Magnetspule 15 wird ein Anker 17 gegen eine Anschlagfläche 18 des Gehäusekörpers 9 gezogen, wobei der Gehäusekörper 9 stromaufwärts der Anschlagfläche 18 als magnetischer Innenpol ausgebildet ist, an den sich von derA magnetic coil 15, which is wound on a coil carrier 16, is used for the electromagnetic actuation of the fuel injection valve 1. When the magnetic coil 15 is electrically excited, an armature 17 is drawn against a stop surface 18 of the housing body 9, the housing body 9 being formed upstream of the stop surface 18 as a magnetic inner pole, to which the
Anschlagfläche 18 ausgehend in Stromabwärtiger Richtung eine dünnwandige magnetische Drosselstelle 19 anschließt. Bei seiner Hubbewegung nimmt der Anker 17 aufgrund der Anlage seiner stromaufwärtigen Stirnfläche 35 an einem einen ersten Anschlag bildenden Anschlagkörper 20 die mit dem Anschlagkörper 20 fest verbundene Ventilnadel 2 und den Ventilschließkörper 3 mit. Die Ventilnadel 2 ist z.B. mit dem Anschlagkörper 20 durch eine Schweißnaht 22 verbunden. Die Bewegung der Ventilnadel 2 erfolgt gegen eine Rückstellfeder 23, die zwischen einer Einstellhülse 24 und dem Anschlagkörper 20 angeordnet ist.Stop surface 18 starting in the downstream direction connects a thin-walled magnetic throttle point 19. During its lifting movement, the armature 17, due to the abutment of its upstream end face 35 against a stop body 20 which forms a first stop, takes on the Stop body 20 firmly connected valve needle 2 and the valve closing body 3 with. The valve needle 2 is connected to the stop body 20 by a weld 22, for example. The movement of the valve needle 2 takes place against a return spring 23 which is arranged between an adjusting sleeve 24 and the stop body 20.
Der Brennstoff strömt über eine Axialbohrung 30 des Gehäusekörpers 9 und wenigstens eine im Anker 17 vorgesehene Axialbohrung 31 sowie über in einer Führungsscheibe 32 vorgesehene Axialbohrungen 33 in eine Längsöffnung 34 des Ventilsitzträgers 5 bis hin zum Dichtsitz des Brennstoffeinspritzventils 1.The fuel flows through an axial bore 30 of the housing body 9 and at least one axial bore 31 provided in the armature 17 and via axial bores 33 provided in a guide disk 32 into a longitudinal opening 34 of the valve seat carrier 5 up to the sealing seat of the fuel injection valve 1.
Der Anker 17 ist zwischen dem Anschlagkörper 20 und einem erfindungsgemäß als Schiebefeder und Dämpfungsfeder ausgebildeten sowie als zweiten Anschlag dienenden Federelement 25 auf der Ventilnadel 2 beweglich angeordnet. Durch die Federkraftwirkung des Federelements 25 wird der Anker 17 in der nicht erregten Ruhestellung an demThe armature 17 is arranged movably on the valve needle 2 between the stop body 20 and a spring element 25 designed as a sliding spring and damping spring and serving as a second stop. Due to the spring force effect of the spring element 25, the armature 17 is in the non-excited rest position on the
Anschlagkörper 20 in Anlage gehalten. Das Federelement 25 ist fest mit der Ventilnadel 2 verbunden.Stop body 20 held in contact. The spring element 25 is firmly connected to the valve needle 2.
Durch das zwischen dem Anschlagkörper 20 und dem Federelement 25 geschaffene Bewegungsspiel des Ankers 17 wird eine Entkopplung der trägen Massen des Ankers 17 einerseits und der Ventilnadel 2 und des Ventilschließkörpers 3 andererseits erreicht. Bei der Schließbewegung der Ventilnadel 2 schlägt an einer Ventilsitzfläche 26 des Ventilsitzkörpers 4 deshalb nur die träge Masse der Ventilnadel 2 an. Der Anker 17 wird bei dem Auftreffen des Ventilschließkörpers 3 an der Ventilsitzfläche 26 nicht abrupt verzögert, sondern bewegt sich gegen das Federelement 25, durch das der Anker 17 in seiner Bewegung abgebremst wird. Das Federelement 25 bewirkt eine Dämpfung des Anschlags des Ankers 17 am dem Anschlagkörper 20 gegenüberliegenden zweiten Ankeranschlag, der hier erfindungsgemäß das Federelement 25 selbst ist.Decoupling of the inert masses of the armature 17 on the one hand and the valve needle 2 and the valve closing body 3 on the other hand is achieved by the movement play of the armature 17 created between the stop body 20 and the spring element 25. When the valve needle 2 closes, only the inert mass of the valve needle 2 strikes a valve seat surface 26 of the valve seat body 4. The armature 17 is not abruptly decelerated when the valve closing body 3 strikes the valve seat surface 26, but moves against the spring element 25, by means of which the armature 17 is braked in its movement. The spring element 25 causes damping the stop of the armature 17 on the second armature stop opposite the stop body 20, which here is the spring element 25 itself according to the invention.
In Figur 2 ist der erfindungsgemäße Ausschnitt rund um den Anker 17 in einem geänderten Maßstab dargestellt. Die Anordnung des axial beweglichen Ankers 17 zwischen seinen beiden Anschlägen wird dabei besonders deutlich, wobei der Anschlagkörper 20 in einer gegenüber Figur 1 vereinfachten Bauweise gezeigt ist. Das Federelement 25 dient erstens als unterer Anschlag für den Anker 17, zweitens als Dämpfungselement, das die Bewegung des Ankers 17 kontinuierlich abbremst und auf diese Weise ein Prellen der Ventilnadel 2 an der Ventilsitzfläche 26 vermeidet bzw. stark einschränkt, und drittens als Schiebefeder, die denFIG. 2 shows the detail according to the invention around the armature 17 on a changed scale. The arrangement of the axially movable armature 17 between its two stops is particularly clear, the stop body 20 being shown in a simplified construction compared to FIG. 1. The spring element 25 serves firstly as a lower stop for the armature 17, secondly as a damping element which continuously brakes the movement of the armature 17 and in this way prevents or severely restricts the valve needle 2 from bouncing on the valve seat surface 26, and thirdly as a sliding spring which the
Anker 17 in seine Ruhestellung zur Anlage am Anschlagkörper 20 drückt. In vorteilhafter Weise wird mit einem Bauteil eine sehr hohe Funktionsintegration erreicht.Anchor 17 presses into its rest position to rest against the stop body 20. A very high level of functional integration is advantageously achieved with one component.
Das Federelement 25 ist in vorteilhafter Weise mit einem rohrförmigen Schaft 38 und mit mehreren davon ausgehenden Federarmen 39 ausgebildet. Der Schaft 38 des Federelements 25 umgreift unmittelbar die Ventilnadel 2 und liegt an dieser an. Dabei sind zwei verschiedene Ausführungsformen des Schaftes 38 denkbar, wie die Figuren 3 und 4 verdeutlichen, die Schnitte entlang der Linie III-III in Figur 2 darstellen. Bei dem Beispiel gemäß Figur 3 liegt der Schaft 38 hülsenförmig an der einen kreisförmigen Querschnitt aufweisenden Ventilnadel 2 unmittelbar und in Umfangsrichtung vollständig umlaufend an. Dagegen ist der Schaft 38 gemäß Figur 4 mit z.B. drei axial verlaufenden Rippen 41 ausgebildet, die von der Ventilnadel 2 wegstehen und in einem jeweiligen Abstand von 120° angeordnet sind. Diese axialen Rippen 41 erhöhen die radiale Elastizität des Federelements 25 und erlauben größere Toleranzen für die zur Herstellung einer festen Verbindung auf der Ventilnadel 2 notwendige Presspassung. Außerdem wird auf diese Weise eine große Angriffsfläche geschaffen, um das Federelement 25 axial auf der Ventilnadel 2 verschieben zu können, was bei der Montage und der Einstellung des Federelements 25 erforderlich ist.The spring element 25 is advantageously designed with a tubular shaft 38 and with a plurality of spring arms 39 extending therefrom. The shaft 38 of the spring element 25 directly engages around the valve needle 2 and lies against it. Two different embodiments of the shaft 38 are conceivable, as shown in FIGS. 3 and 4, which represent sections along the line III-III in FIG. In the example according to FIG. 3, the shaft 38 lies directly against the circumference of the valve needle 2, which has a circular cross section, in the form of a sleeve. In contrast, the shaft 38 according to FIG. 4 is designed with, for example, three axially extending ribs 41 which protrude from the valve needle 2 and are arranged at a respective distance of 120 °. These axial ribs 41 increase the radial elasticity of the spring element 25 and allow greater tolerances for the Establishing a firm connection on the valve needle 2 necessary press fit. In addition, a large contact surface is created in this way in order to be able to move the spring element 25 axially on the valve needle 2, which is necessary for the assembly and adjustment of the spring element 25.
Neben der bereits genannten Ausbildung der Paarung Ventilnadel 2/Federelement 25 mit einer Presspassung zur Erzielung einer festen Pressverbindung ist es zudem möglich, zur weiteren Sicherung im Bereich des Schaftes 38 einen oder mehrere Schweißpunkte oder -nähte 40 zu setzen, wie dies in Figur 2 auf der rechten Seite angedeutet ist. Das z.B. aus rostfreiem Federstahlblech ausgeformte Federelement 25 wird beispielsweise durch Tiefziehen und anschließendes Stanzen in seine gewünschte Form gebracht. Die eigentliche Federwirkung wird durch die Federarme 39 erzielt, die aus dem Schaft 38 hervorgehen und sich von der Ventilnadel 2 abspreizen. Die Federarme 39 erstrecken sich dabei fingerartig über den gesamten Umfang vom Schaft 38 weg, wobei jeder einzelne Federarm 39 unter einer Federspannung gewölbt ist. Wie Figur 2 zu entnehmen ist, sind die Federarme 39 derart gewölbt, dass der Anker 17 mit seinem Randbereich nahe des Außenumfangs an Außenbereichen 42 zur Anlage an den Federarmen 39 kommt, so dass ein Verkippen desIn addition to the already mentioned formation of the pairing of valve needle 2 / spring element 25 with a press fit to achieve a firm press connection, it is also possible to set one or more welding points or seams 40 in the area of the shaft 38, as shown in FIG. 2 the right side is indicated. That e.g. Spring element 25 formed from stainless spring steel sheet is brought into its desired shape, for example, by deep drawing and subsequent punching. The actual spring action is achieved by the spring arms 39, which emerge from the shaft 38 and spread apart from the valve needle 2. The spring arms 39 extend finger-like over the entire circumference away from the shaft 38, each spring arm 39 being arched under spring tension. As can be seen in FIG. 2, the spring arms 39 are curved in such a way that the armature 17 comes into contact with the spring arms 39 with its edge region near the outer circumference at outer regions 42, so that the spring arm 39 tilts
Ankers 17 ausgeschlossen werden kann. Das radiale Ende der Federarme 39 bilden hinter den zur Ankeraufläge dienenden Außenbereichen 42 Federarmenden 44, die wieder vom Anker 17 weggebogen sind, so dass keine scharfen Kanten am Anker 17 anliegen.Anchor 17 can be excluded. The radial end of the spring arms 39 form spring arm ends 44 behind the outer regions 42 serving as armature supports, which are again bent away from the armature 17, so that no sharp edges lie against the armature 17.
Figur 5 zeigt eine Draufsicht auf ein Federelement 25 mit sechs über den Umfang verteilten Federarmen 39. Eine andere Anzahl an Federarmen 39 des Federelements 25 ist jedoch ebenso denkbar. Die Federarme 39 weisen z.B. entsprechend des Biegemomentenverlaufs radial nach außen hin eine geringere Breite auf als zum Schaft 38 hin. FIG. 5 shows a plan view of a spring element 25 with six spring arms 39 distributed over the circumference. However, a different number of spring arms 39 of the spring element 25 is also conceivable. The spring arms 39 have, for example, accordingly of the course of the bending moment radially outwards to a smaller width than towards the shaft 38.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1) für1. Fuel injector (1) for
Brennstoffeinspritzanlagen von Brennkraftmaschinen, mit einer Magnetspule (15), mit einem durch die Magnetspule (15) in eine Hubrichtung beaufschlagbaren Anker (17) und mit einer mit einem Ventilschließkörper (3) in Verbindung stehenden Ventilnadel (2), wobei der Anker (17) zwischen einem mit der Ventilnadel (2) verbundenen, die Bewegung des Ankers (17) in der Hubrichtung begrenzenden ersten Anschlag (20) und einem mit der Ventilnadel (2) verbundenen, die Bewegung des Ankers (17) entgegen der Hubrichtung begrenzenden zweiten Anschlag (25) beweglich ist, dadurch gekennzeichnet, dass der zweite Anschlag durch ein Federelement (25) gebildet ist.Fuel injection systems of internal combustion engines, with a magnet coil (15), with an armature (17) which can be acted upon in one stroke direction by the magnet coil (15) and with a valve needle (2) connected to a valve closing body (3), the armature (17) between a first stop (20) connected to the valve needle (2) and limiting the movement of the armature (17) in the stroke direction and a second stop (20) connected to the valve needle (2) and limiting the movement of the armature (17) in the opposite direction to the stroke direction 25) is movable, characterized in that the second stop is formed by a spring element (25).
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass das Federelement (25) eine Schiebefeder bzw. eine Dämpfungsfeder ist, die fest auf der Ventilnadel2. Fuel injection valve according to claim 1, characterized in that the spring element (25) is a sliding spring or a damping spring which is fixed on the valve needle
(2) angebracht ist.(2) is attached.
3. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass das Federelement (25) auf die Ventilnadel (2) aufgepresst ist. 3. Fuel injection valve according to claim 2, characterized in that the spring element (25) is pressed onto the valve needle (2).
4. Brennstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, dass das Federelement (25) zusätzlich durch wenigstens einen Schweißpunkt (40) oder eine Schweißnaht auf der Ventilnadel (2) gesichert ist.4. Fuel injection valve according to claim 3, characterized in that the spring element (25) is additionally secured by at least one weld spot (40) or a weld seam on the valve needle (2).
5. Brennstoffeinspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Federelement5. Fuel injection valve according to one of the preceding claims, characterized in that the spring element
(25) einen die Ventilnadel (2) umhüllenden Schaft (38) und mehrere von dem Schaft (38) ausgehende Federarme (39) aufweist.(25) has a shaft (38) enveloping the valve needle (2) and a plurality of spring arms (39) extending from the shaft (38).
6. Brennstoffeinspritzventil nach Anspruch 5, dadurch gekennzeichnet, dass der Schaft (38) über seinen Umfang mehrere axiale Rippen (41) besitzt, die von der Ventilnadel (2) wegstehen.6. Fuel injection valve according to claim 5, characterized in that the shaft (38) has a plurality of axial ribs (41) over its circumference, which protrude from the valve needle (2).
7. Brennstoffeinspritzventil nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass die Federarme (39) mit einer7. Fuel injection valve according to claim 5 or 6, characterized in that the spring arms (39) with a
FederSpannung gewölbt ausgeführt sind.Spring tension are arched.
8. Brennstoffeinspritzventil nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass der Anker (17) mit seinem Randbereich nahe des Außenumfangs an von der Ventilnadel (2) entfernten Außenbereichen (42) zur Anlage an den Federarmen (39) kommt.8. Fuel injection valve according to one of claims 5 to 7, characterized in that the armature (17) comes with its edge region close to the outer circumference of the valve needle (2) removed outer regions (42) to bear against the spring arms (39).
9. Brennstoffeinspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Federelement9. Fuel injection valve according to one of the preceding claims, characterized in that the spring element
(25) durch Tiefziehen und Stanzen aus einem Federstahlblech herstellbar ist. (25) can be produced from a spring steel sheet by deep drawing and punching.
EP99962123A 1999-06-18 1999-12-02 Fuel injection valve Expired - Lifetime EP1105639B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19927900A DE19927900A1 (en) 1999-06-18 1999-06-18 Fuel injection valve for direct injection IC engine has movement of armature limited by opposing stops attached to valve needle one of which is provided by spring element
DE19927900 1999-06-18
PCT/DE1999/003868 WO2000079120A1 (en) 1999-06-18 1999-12-02 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1105639A1 true EP1105639A1 (en) 2001-06-13
EP1105639B1 EP1105639B1 (en) 2005-01-26

Family

ID=7911710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99962123A Expired - Lifetime EP1105639B1 (en) 1999-06-18 1999-12-02 Fuel injection valve

Country Status (6)

Country Link
US (1) US6520434B1 (en)
EP (1) EP1105639B1 (en)
JP (1) JP2003502573A (en)
KR (1) KR20010072511A (en)
DE (2) DE19927900A1 (en)
WO (1) WO2000079120A1 (en)

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Also Published As

Publication number Publication date
DE19927900A1 (en) 2000-12-21
KR20010072511A (en) 2001-07-31
WO2000079120A1 (en) 2000-12-28
EP1105639B1 (en) 2005-01-26
DE59911528D1 (en) 2005-03-03
US6520434B1 (en) 2003-02-18
JP2003502573A (en) 2003-01-21

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