EP1309789A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1309789A1
EP1309789A1 EP01955273A EP01955273A EP1309789A1 EP 1309789 A1 EP1309789 A1 EP 1309789A1 EP 01955273 A EP01955273 A EP 01955273A EP 01955273 A EP01955273 A EP 01955273A EP 1309789 A1 EP1309789 A1 EP 1309789A1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
valve needle
injection valve
flange
valve
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
EP01955273A
Other languages
German (de)
French (fr)
Other versions
EP1309789B1 (en
Inventor
Klaus Noller
Uwe Liskow
Martin Buehner
Guido Pilgram
Juergen Maier
Hartmut Albrodt
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 EP1309789A1 publication Critical patent/EP1309789A1/en
Application granted granted Critical
Publication of EP1309789B1 publication Critical patent/EP1309789B1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M51/0671—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 having an elongated valve body attached thereto
    • 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
    • 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 is based on a fuel injection valve according to the preamble of the main claim.
  • a fuel injector is provided with a solenoid which interacts with an armature which is non-positively connected to the valve needle.
  • An additional mass is provided in a cylindrical shape around the armature and the valve needle, which is connected to the armature via an elastomer layer.
  • a disadvantage here is the complex design with an additional component.
  • the large-area elastomer ring is also unfavorable for the course of the magnetic field and makes it difficult to close the field lines and thus to achieve high tightening forces during the opening movement of the fuel injector.
  • a further cylindrical mass is provided for damping and debouncing around the armature and the valve needle, which is movably clamped and held in position by two elastomer rings. When the valve needle strikes the sealing seat, this second mass can move relative to the armature and valve needle and prevent the valve needle from bouncing.
  • a disadvantage of the described embodiment is the additional effort and space requirement.
  • the armature itself is not decoupled, so its impulse increases the tendency for the valve needle to bounce.
  • the anchor is held between two stops, with an elasto ring between the anchor and the lower stop.
  • the problem arises that a bore through the armature is necessary to supply the fuel to the valve seat surface.
  • the armature is drilled near the valve needle.
  • Damping element enclosed internal volume and a central recess of the fuel injector allows. Liquid compensation creates additional damping based on the shock absorber principle.
  • the damping element is also supported by the intermediate rings, whereby vibrations of the elastomer are avoided.
  • the drainage holes in the flange are easy to manufacture and drain the fuel between the damping element and valve needle quickly and without turbulence.
  • the intermediate rings advantageously have grooves which extend radially from the inside out, for. B. in the form of an embossed structure, whereby the fuel can also be derived on the bottom and top of the damping element. This on the one hand prevents overpressure and the lateral slipping of the damping element, and on the other hand achieves a positive effect on the bouncing behavior of the armature and valve needle, since the viscosity of the fuel increases the damping and thus counteracts bouncing.
  • the drainage of the gap between the valve needle and armature can be achieved particularly easily by segment welding, in that the valve needle is not connected to the flange by a continuous weld seam, but by spot welding, which alternates fastening sections with passages through which fuel can flow.
  • the combination of the individual drainage devices is particularly advantageous in that, for example, the flange is connected to the valve needle by segment welding and the damping element has an intermediate ring on the inlet and outlet sides.
  • FIG. 1 shows a schematic section through an exemplary embodiment of a fuel injector according to the prior art
  • FIG. 2A shows a schematic longitudinal section through a fuel injector according to the invention in the area IIA in FIG. 1
  • Fig. 2B is a schematic section along the line IIB-IIB in Fig. 2A
  • FIG. 3 shows a schematic longitudinal section " through a further exemplary embodiment of a fuel injection valve according to the invention in the area IIA in FIG. 1.
  • the fuel injection valve 1 is in the form of a fuel injection valve for fuel injection systems of mixture-compressing, spark-ignited
  • Fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
  • the fuel injector 1 consists of a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is operatively connected to the valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • fuel injector 1 is a fuel injector 1 that opens inward and has a spray opening 7.
  • the nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a solenoid 10.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10.
  • the Inner pole 13 and outer pole 9 are separated from one another by a constriction 26 and connected to one another by a non-ferromagnetic connecting component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • the valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disc 15 is used for stroke adjustment.
  • the armature 20 is located on the other side of the adjusting disc 15. This armature is non-positively connected via a first flange 21 to the valve needle 3, which is connected to the first flange 21 by a weld seam 22.
  • a restoring spring 23 is supported on the first flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24.
  • Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and on the valve seat body 5, which channels the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the spray-discharge opening 7.
  • the fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
  • An annular damping element 32 which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It is' on to a second flange 31, which is frictionally connected by a weld 33 to the valve needle.
  • the first flange 21 is welded to the valve needle 3
  • the armature 20 and the damping element 32 are plugged on, and then the second flange 31 is pressed under pressure on the damping element 32 and also welded to the valve needle 3.
  • the armature 20 has only a slight, highly damped play between the first flange 21 and the damping element 32.
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat 6.
  • the magnetic coil 10 When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20.
  • the armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction.
  • the valve closing body 4, which is connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel which is conducted via the fuel channels 30a to 30c is sprayed off through the spray opening 7.
  • the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the first flange 21, which is connected to the valve needle 3, moves counter to the stroke direction.
  • the valve needle 3 is thereby moved in the same direction, as a result of which the valve-closure member 4 is seated on the valve seat surface 6 and the fuel injection valve 1 is closed.
  • FIG. 2A shows an enlarged sectional view of an enlarged view of the area IIA in FIG. 1.
  • valve needle 3 A part of the valve needle 3 is shown, the second flange 31 welded to it and the lower part of the armature 20 with the fuel channel 30a running therein.
  • the damping element 32 rests on the second flange 31.
  • the exemplary embodiment shown in FIG. 2A has a first intermediate ring 34, which is arranged between an outlet-side anchor surface 35 and the damping element 32.
  • the first intermediate ring 34 has a two-fold task: on the one hand, the first intermediate ring 34 represents a protection of the damping element 32 against the armature 20 impinging on it, since in particular the edges of the fuel channel 30a can damage the damping element 32 during continuous operation of the fuel injection valve 1 and thus damage the damping element 32 correct functioning of the fuel injector 1 is no longer guaranteed.
  • the first intermediate ring 34 provides for the drainage of an inner volume 36 between the damping element 32 and the valve needle 3, into which fuel penetrates during the operation of the fuel injection valve 1, through a specifically applied surface structure.
  • the surface structure of the first intermediate ring 34 thus creates a connection between the inner volume 36 and a central recess 42 of the fuel injector 1.
  • the fuel compressed in the inner volume 36 can also not be drained radially but axially in the outflow direction.
  • the second flange 31 is attached to the valve needle 3 by means of segment welding.
  • the second flange 31 is not connected to the valve needle 3 via a weld seam 33 that runs around the circumference without gaps, but via individual welding segments 37, which, as shown in FIG. 2B, have, for example, a radial angular extent of approximately 90 ° and two drainage gaps 38, which likewise have an angular extent of approximately 90 °.
  • the fuel compressed in the inner volume 36 can thus flow away via the drainage gaps 38 between the valve needle 3 and the second flange 31.
  • the ' segment welding ' method has the particular advantage that the compressed fuel can easily be discharged into the inner volume 36 without additional components.
  • welding segments 37 for connecting the second flange 31 to the valve needle 3, but, for example, four welding segments 37 lying opposite one another in a cross shape, with correspondingly four intermediate drainage gaps 38.
  • the number of welding segments 37 and the drainage gaps 38 can correspond to the requirements be adjusted.
  • FIG. 3 shows an excerpted sectional illustration of a further exemplary embodiment of the fuel injector 1 according to the invention.
  • a second intermediate ring 39 is inserted between the second flange 31 and the damping element 32.
  • radial grooves are expediently provided on a drain-side side 40 of the first intermediate ring 34 and an inlet-soap side 41 of the second intermediate ring 39, through which the fuel from the inner volume 36 between the first intermediate ring 34 and the second intermediate ring 39 can run on the surface of the damping element 32.
  • the structure of the drain-side side 40 of the first intermediate ring 34 and the inlet-side 41 of the second intermediate ring 39 can be generated, for example, by embossing or milling.
  • Another possibility of removing the fuel stowed in the inner volume 36 is to make radial bores 43 in the second flange 31, which, for example, produce a connection between the inner volume 36 and the central recess 42 of the fuel injection valve 1 just below the damping element 32.
  • the ' number of holes' can be limited to one, but several, e.g. B. holes 43 arranged at equal angular intervals.
  • valve needle bouncer is reduced by these measures, since the valve needle 3, after the valve closing body 4 has been put on, has resistance due to the viscosity of the fuel in the inner volume 36 and therefore no longer has any possibility of moving again in the stroke direction.
  • the invention is not limited to the illustrated embodiments and z. B. also suitable for outward opening fuel injection valves 1 or other anchor shapes, for example flat anchors.

Abstract

The invention relates to a fuel injection valve (1), especially a fuel injection valve for fuel inspection systems of internal combustion engines. Said fuel injection valve comprises a valve needle (3) that co-operates with a valve seat (6) to provide a sealing seat. An anchor (20) acts upon the valve needle (3) and can be axially displaced on the valve needle (3) and is dampened by a dampener (32) that consists of an elastomer. Between the anchor (20) and the dampener (32) a first intermediate ring (34) is disposed. The dampener (32) rests on a flange (32) that is linked with the valve needle (3) in a positive fit. The intermediate ring (34) and/or the flange (31) are provided with radial and/or axial channels that interlink an inner volume (36) present between the valve needle (3) and the dampener (32) with a central recess (42) of the fuel injection valve (1).

Description

Brennstoffeinspritsventil Brennstoffeinspritsventil
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspr-itzventil nach der Gattung des Hauptanspruchs .The invention is based on a fuel injection valve according to the preamble of the main claim.
Es ist bereits aus der US 4,766,405 ein Brennstoffeinspritzventil bekannt, das einen mit einer Ventilnadel verbundenen Ventilschließkδrper, der "mit einer an einem Ven ilsitzkörper ausgebildeten Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, aufweist. Zur elektromagnetischen Betätigung desIt is already known from US Pat. No. 4,766,405 which has a valve closing body which is connected to a valve needle and which "interacts with a valve seat surface formed on a valve seat body to form a sealing seat. For electromagnetic actuation of the
Brennstoffeinspritzventils ist eine Magnetspule vorgesehen, die mit einem Anker zusammenwirkt, der mit der Ventilnadel kraftschlüssig verbunden ist. Um den Anker und die Ventilnadel ist eine zusätzliche Masse zylinderförmig vorgesehen, die über eine Elastomerschicht mit dem Anker verbunden ist.A fuel injector is provided with a solenoid which interacts with an armature which is non-positively connected to the valve needle. An additional mass is provided in a cylindrical shape around the armature and the valve needle, which is connected to the armature via an elastomer layer.
Nachteilig ist dabei insbesondere die aufwendige Bauform mit einem zusätzlichen Bauteil. Auch ist der großflächige Elastomerring ungünstig für den Verlauf des Magnetfelds und erschwert das Schließen der Feldlinien und somit das Erreichen hoher Anzugskräfte bei der Öffnungsbewegung des Brennstoffeinspritzventils . Aus der US 4,766,405 ist eine weitere Ausführungsform eines Brennstoffeinspritzventils bekannt, bei dem zur Dämpfung und Entprellung um den Anker und die Ventilnadel eine weitere zylinderförmige Masse vorgesehen ist, die durch zwei Elastomerringe in ihrer Position beweglich eingespannt und gehalten wird. Beim Auftreffen der Ventilnadel auf dem Dichtsitz kann sich diese zweite Masse relativ zu Anker und Ventilnadel bewegen und ein Prellen der Ventilnadel verhindern.A disadvantage here is the complex design with an additional component. The large-area elastomer ring is also unfavorable for the course of the magnetic field and makes it difficult to close the field lines and thus to achieve high tightening forces during the opening movement of the fuel injector. From US 4,766,405 a further embodiment of a fuel injector is known, in which a further cylindrical mass is provided for damping and debouncing around the armature and the valve needle, which is movably clamped and held in position by two elastomer rings. When the valve needle strikes the sealing seat, this second mass can move relative to the armature and valve needle and prevent the valve needle from bouncing.
Nachteilig an der beschriebenen Ausführungsform ist der zusätzliche Aufwand und Platzbedarf. Auch ist der Anker selbst nicht entkoppelt, sein Impuls vergrößert somit bei der Ventilnadel die Neigung, zu prellen.A disadvantage of the described embodiment is the additional effort and space requirement. The armature itself is not decoupled, so its impulse increases the tendency for the valve needle to bounce.
Aus der US 5,299,776 ist ein Brennstoffeinspritzventil mit einer Ventilnadel und einem Anker bekannt, der auf der Ventilnadel beweglich geführt ist und dessen Bewegung in der Hubrichtung der Ventilnadel durch einen ersten Anschlag und entgegen der Hubrichtung der Ventilnadel durch einen zweiten Anschlag begrenzt wird. Das durch die beiden Anschläge festgelegte axiale Bewegungsspiel des Ankers führt in gewissen Grenzen zu einer Entkoppelung der trägen Masse der Ventilnadel einerseits und der trägen Masse des Ankers andererseits. Dadurch wird einem Zurückprallen der Ventilnadel von der Ventilsitzfläche beim Schließen des Brennstoffeinspritzventils in gewissen Grenzen entgegengewirkt. 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 bei der aus der US 5,299,776 bekannten Bauweise des Brennstoffeinspritzventils nicht vermieden, daß der Anker bei der Schließbewegung des Brennstoffeinspritzventils auf den dem Ventilschließkörper zugewandten Anschlag auftrifft und seinen Impuls dadurch schlagartig auf die Ventilnadel überträgt . Diese schlagartige Impulsübertragung kann zusätzliche Preller des Ventilschließkörpers verursachen. Es ist weiter aus der Praxis bekannt, den auf der Ventilnadel axial beweglich angeordneten Anker durch einen Elastomerring in seiner Position beweglich eingespannt zu befestigen. Hierzu wird der Anker zwischen zwei Anschlägen gehalten, wobei zwischen Anker und unterem Anschlag ein Elasto erring liegt. Dabei tritt jedoch das Problem auf, daß zur Zuführung des Brennstoffs zur Ventilsitzfläche eine Bohrung durch den Anker notwendig ist. Die Bohrung durch den Anker ist nahe der Ventilnadel ausgeführt.From US 5,299,776 a fuel injector with a valve needle and an armature is known which is movably guided on the valve needle and whose movement in the stroke direction of the valve needle is limited by a first stop and counter to the stroke direction of the valve needle by a second stop. 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 on the one hand and the inertial mass of the armature on the other. This counteracts a rebounding of the valve needle from the valve seat surface when the fuel injector is closed within certain limits. 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, in the construction of the fuel injector known from US Pat. No. 5,299,776, it is not avoided that the armature strikes the stop facing the valve closing body during the closing movement of the fuel injector and thereby suddenly transfers its impulse to the valve needle. This sudden impulse transmission can cause additional bouncing of the valve closing body. It is also known from practice to fix the position of the armature axially movably arranged on the valve needle by means of an elastomer ring. For this purpose, the anchor is held between two stops, with an elasto ring between the anchor and the lower stop. However, the problem arises that a bore through the armature is necessary to supply the fuel to the valve seat surface. The armature is drilled near the valve needle.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die zwischen dem Anker und demThe fuel injector according to the invention with the characterizing features of the main claim has the advantage that the between the armature and the
Dämpfungselement bzw. zwischen dem Dämpfungselement und demDamping element or between the damping element and the
Flansch angeordneten Zwischenringe durch ihre Position undIntermediate rings arranged by their position and flange
Struktur für ausgeglichene Druckverhältnisse sorgen, so daß das Dämpfungseiement ortsfest bleibt und nicht durchStructure ensure balanced pressure conditions so that the damping element remains stationary and not through
Verrutschen zerstört werden kann. Durch die radialen und/oder axialen Kanäle wird ein Flüssigkeitsausgleich zwischen einem von der Ventilnadel, dem Anker und demSlipping can be destroyed. Due to the radial and / or axial channels, a liquid balance between one of the valve needle, the armature and the
Dämpfungseiement eingeschlossenen Innenvolumen und einer zentralen Ausnehmung des Brennstoffeinspritzventils ermöglicht. Durch Flüssigkeitsausgleich entsteht eine zusätzliche Dämpfung nach dem Stoßdämpferprinzip.Damping element enclosed internal volume and a central recess of the fuel injector allows. Liquid compensation creates additional damping based on the shock absorber principle.
Das Dämpfungselement wird außerdem durch die Zwischenringe gestützt, wodurch Schwingungen des Elastomers vermieden werden .The damping element is also supported by the intermediate rings, whereby vibrations of the elastomer are avoided.
,Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims allow advantageous further developments of the fuel injector specified in the main claim.
Die Drainagebohrungen im Flansch sind einfach herstellbar und leiten den Brennstoff zwischen Dämpfungselement und Ventilnadel schnell und ohne Verwirbelungen ab. Die Zwischenringe weisen vorteilhafterweise Nuten, welche sich radial von innen nach außen erstrecken, z. B. in Form einer eingeprägten Struktur auf, wodurch der Brennstoff auch an der Unter- und Oberseite des Dämpfungseiements abgeleitet werden kann. Dadurch wird einerseits ein Überdruck und dadurch das seitliche Verrutschen des Dämpfungselements verhindert, andererseits ein positiver Effekt auf das Prellverhalten von Anker und Ventilnadel erreicht , da die Viskosität des Brennstoffs die Dämpfung erhöht und -so Prellern entgegenwirkt.The drainage holes in the flange are easy to manufacture and drain the fuel between the damping element and valve needle quickly and without turbulence. The intermediate rings advantageously have grooves which extend radially from the inside out, for. B. in the form of an embossed structure, whereby the fuel can also be derived on the bottom and top of the damping element. This on the one hand prevents overpressure and the lateral slipping of the damping element, and on the other hand achieves a positive effect on the bouncing behavior of the armature and valve needle, since the viscosity of the fuel increases the damping and thus counteracts bouncing.
Die Drainage des Spalts zwischen Ventilnadel und Anker kann besonders einfach durch Segmentschweißen erreicht werden, indem die Ventilnadel nicht durch eine durchgehende Schweißnaht mit dem Flansch verbunden wird, sondern durch punktuelles Schweißen, wodurch Befestigungsabschnitte mit Passagen abwechseln, durch die Brennstoff abfließen kann.The drainage of the gap between the valve needle and armature can be achieved particularly easily by segment welding, in that the valve needle is not connected to the flange by a continuous weld seam, but by spot welding, which alternates fastening sections with passages through which fuel can flow.
Besonders vorteilhaft ist die Kombination der einzelnen Drainagevorrichtungen, indem beispielsweise der Flansch durch Segmentschweißen mit der Ventilnadel verbunden wird und das Dämpfungseiement Zulauf- und ablaufseitig einen Zwischenring aufweist.The combination of the individual drainage devices is particularly advantageous in that, for example, the flange is connected to the valve needle by segment welding and the damping element has an intermediate ring on the inlet and outlet sides.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1 einen schematischen Schnitt durch ein Aus-führungsbeispiel eines Brennstoffeinspritzventils gemäß dem Stand der Technik,1 shows a schematic section through an exemplary embodiment of a fuel injector according to the prior art,
Fig. 2A einen schematischen Längsschnitt dmrch ein erfindungsgemäßes Brennstoffeinspritzventil im Bereich IIA in Fig. 1, Fig. 2B einen schematischen Schnitt entlang der Linie IIB- IIB in Fig. 2A, und2A shows a schematic longitudinal section through a fuel injector according to the invention in the area IIA in FIG. 1, Fig. 2B is a schematic section along the line IIB-IIB in Fig. 2A, and
Fig. 3 einen schematisehen Längsschnitt" durch ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich IIA in Fig. 1.3 shows a schematic longitudinal section " through a further exemplary embodiment of a fuel injection valve according to the invention in the area IIA in FIG. 1.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Bevor anhand der Figuren 2A, 2B und 3 Ausführungsbeispiele eines erfindungsgemäßen Brennstoffeinspritzventils 1 näher beschrieben werden, soll zum besseren Verständnis der Erfindung zunächst anhand von Fig. 1 ein abgesehen von den erfindungsgemäßen Maßnahmen baugleiches Brennstoffeinspritz- ventil gemäß dem Stand der Technik bezüglich seiner wesentlichen Bauteile kurz erläutert werden.Before exemplary embodiments of a fuel injector 1 according to the invention are described in more detail with reference to FIGS. 2A, 2B and 3, a fuel injector according to the prior art, which is identical in construction aside from the measures according to the prior art with regard to its essential components, should first be briefly understood with reference to FIG are explained.
Das Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündetenThe fuel injection valve 1 is in the form of a fuel injection valve for fuel injection systems of mixture-compressing, spark-ignited
Brennkraftmaschinen ausgeführt. DasRunning internal combustion engines. The
Brennstoffeinspritzventil 1 eignet sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine.Fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
Das Brennstoffeinspritzventil 1 besteht aus einem Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht in Wirkverbindung mit dem Ventilschließkörper 4, der mit einer auf einem Ventilsitzkörper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Bei dem Brennstoffeinspritzventil 1 handelt es sich im Ausführungsbeispiel um ein nach innen öffnendes Brennstoffeinspritzventil 1, welches über eine Abspritzöffnung 7 verfügt. Der Düsenkörper 2 ist durch eine Dichtung 8 gegen den Außenpol 9 einer Magnetspule 10 abgedichtet. Die Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt., welcher an einem Innenpol 13 der Magnetspule 10 anliegt. Der Innenpol 13 und der Außenpol 9 sind durch eine Verengung 26 voneinander getrennt und miteinander durch ein nicht ferromagnetisches Verbindungsbauteil 29 verbunden. Die Magnetspule 10 wird über eine Leitung 19 von einem über einen elektrischen Steckkontakt 17 zuführbaren elektrischen Strom erregt. Der Steckkontakt 17 ist von einer Kunststoffummantelung 18 umgeben, die am Innenpol 13 angespritzt sein kann.The fuel injector 1 consists of a nozzle body 2, in which a valve needle 3 is arranged. The valve needle 3 is operatively connected to the valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat. In the exemplary embodiment, fuel injector 1 is a fuel injector 1 that opens inward and has a spray opening 7. The nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a solenoid 10. The magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10. The Inner pole 13 and outer pole 9 are separated from one another by a constriction 26 and connected to one another by a non-ferromagnetic connecting component 29. The magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17. The plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
Die Ventilnadel 3 ist in einer Ventilnadelführung 14 geführt, welche scheibenförmig ausgeführt ist. Zur Hubeinstellung dient eine zugepaarte Einstellscheibe 15. An der anderen Seite der Einstellscheibe 15 befindet sich der Anker 20. Dieser steht über einen ersten Flansch 21 kraftschlüssig mit der Ventilnadel 3 in Verbindung, welche durch eine Schweißnaht 22 mit dem ersten Flansch 21 verbunden ist. Auf dem ersten Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine Hülse 24 auf Vorspannung gebracht wird. In der Ventilnadelführung 14, im Anker 20 und am Ventilsitzkörper 5 verlaufen Brennstoffkanäle 30a bis 30c, die den Brennstoff, welcher über eine zentrale Brennstoffzufuhr 16 zugeführt und durch ein Filterelement 25 gefiltert wird, zur AbspritzÖffnung 7 leiten. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht weiter dargestellte Brennstoffleitung abgedichtet .The valve needle 3 is guided in a valve needle guide 14, which is disc-shaped. A paired adjusting disc 15 is used for stroke adjustment. The armature 20 is located on the other side of the adjusting disc 15. This armature is non-positively connected via a first flange 21 to the valve needle 3, which is connected to the first flange 21 by a weld seam 22. A restoring spring 23 is supported on the first flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24. Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and on the valve seat body 5, which channels the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the spray-discharge opening 7. The fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
An der abspritzseitigen Seite des Ankers 20 ist ein ringförmiges Dämpfungselement 32, welches aus einem Elastomerwerkstoff besteht, angeordnet. Es liegt' auf einem zweiten Flansch 31 auf, welcher über eine Schweißnaht 33 kraftschlüssig mit der Ventilnadel 3 verbunden ist .An annular damping element 32, which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It is' on to a second flange 31, which is frictionally connected by a weld 33 to the valve needle. 3
Bei der Fertigung des aus Anker 20 und Ventilnadel 3 bestehenden Bauteils wird der erste Flansch 21 mit der Ventilnadel 3 verschweißt, der Anker 20 und das Dämpfungseiement 32 aufgesteckt und anschließend der zweite Flansch 31 unter Druck auf das Dämpfungselement 32 gepreßt und ebenfalls mit der Ventilnadel 3 verschweißt. Auf diese Weise verfügt der Anker 20 nur über ein geringfügiges, stark gedämpftes Spiel zwischen dem ersten Flansch 21 und dem Dämpfungseiement 32.In the manufacture of the component consisting of armature 20 and valve needle 3, the first flange 21 is welded to the valve needle 3, the armature 20 and the damping element 32 are plugged on, and then the second flange 31 is pressed under pressure on the damping element 32 and also welded to the valve needle 3. In this way, the armature 20 has only a slight, highly damped play between the first flange 21 and the damping element 32.
Im Ruhezustand des Brennstoffeinspritzventils 1 wird der Anker 20 von der Rückstellfeder 23 entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkörper 4 am Ventilsitz 6 in dichtender Anlage gehalten wird. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt, wobei der Hub durch einen in der Ruhestellung zwischen dem Innenpol 12 und dem Anker 20 befindlichen Arbeitsspalt 27 vorgegeben ist. Der Anker 20 nimmt den ersten Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Verbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab und der über die Brennstoffkanäle 30a bis 30c geführte Brennstoff wird durch die Abspritzöffnung 7 abgespritzt.In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat 6. When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20. The armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction. The valve closing body 4, which is connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel which is conducted via the fuel channels 30a to 30c is sprayed off through the spray opening 7.
Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder 23 vom Innenpol 13 ab, wodurch sich der mit der Ventilnadel 3 in Verbindung stehende erste Flansch 21 entgegen der Hubrichtung bewegt. Die Ventilnadel 3 wird dadurch in die gleiche Richtung bewegt, wodurch der Ventilschließkörper 4 auf der Ventilsitzfläche 6 aufsetzt und das Brennstoffeinspritzventil 1 geschlossen wird.If the coil current is switched off, the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the first flange 21, which is connected to the valve needle 3, moves counter to the stroke direction. The valve needle 3 is thereby moved in the same direction, as a result of which the valve-closure member 4 is seated on the valve seat surface 6 and the fuel injection valve 1 is closed.
Fig. 2A zeigt in einer auszugsweisen Schnittdarstellung eine vergrößerte Ansicht des Bereichs IIA in Fig. 1.2A shows an enlarged sectional view of an enlarged view of the area IIA in FIG. 1.
Dargestellt ist ein Teil der Ventilnadel 3, der daran verschweißte zweite Flansch 31 sowie der untere Teil des Ankers 20 mit dem darin verlaufenden Brennstoffkanal 30a. Auf dem zweiten Flansch 31 liegt das Dämpfungselement 32 auf. Erfindungsgemäß weist das in Fig. 2A dargestellte Ausführungsbeispiel einen ersten Zwischenring 34 auf, welcher zwischen einer ablaufseitigen Ankerfläche 35 und dem Dämpfungselement 32 angeordnet ist.A part of the valve needle 3 is shown, the second flange 31 welded to it and the lower part of the armature 20 with the fuel channel 30a running therein. The damping element 32 rests on the second flange 31. According to the invention, the exemplary embodiment shown in FIG. 2A has a first intermediate ring 34, which is arranged between an outlet-side anchor surface 35 and the damping element 32.
Dem ersten Zwischenring 34 kommt dabei eine zweifache Aufgabe zu: einerseits stellt der erste Zwischenring 34 einen Schutz des Dämpfungselements 32 gegen den darauf aufprallenden Anker 20 dar, da insbesondere die Kanten des Brennstoffkanals 30a im Dauerbetrieb des Brennstoffeinspritzventils 1 das Dämpfungselement 32 beschädigen können und damit die korrekte Funktionsweise des Brennstoffeinspritzventils 1 nicht mehr gewährleistet ist.The first intermediate ring 34 has a two-fold task: on the one hand, the first intermediate ring 34 represents a protection of the damping element 32 against the armature 20 impinging on it, since in particular the edges of the fuel channel 30a can damage the damping element 32 during continuous operation of the fuel injection valve 1 and thus damage the damping element 32 correct functioning of the fuel injector 1 is no longer guaranteed.
Andererseits sorgt der erste Zwischenring 34 durch eine gezielt aufgebrachte Oberflächenstruktur für die Drainage eines Innenvolumens 36 zwischen dem Dämpfungselement 32 und der Ventilnadel 3, in welches während des Betriebs des Brennstoffeinspritzventils 1 Brennstoff eindringt. Die Oberflächenstruktur des ersten Zwischenrings 34 stellt somit eine Verbindung zwischen dem Innenvolumen 36 und einer zentralen Ausnehmung 42 des Brennstoffeinspritzventils 1 her.On the other hand, the first intermediate ring 34 provides for the drainage of an inner volume 36 between the damping element 32 and the valve needle 3, into which fuel penetrates during the operation of the fuel injection valve 1, through a specifically applied surface structure. The surface structure of the first intermediate ring 34 thus creates a connection between the inner volume 36 and a central recess 42 of the fuel injector 1.
Kann der in dem Innenvolumen 36 während des Betriebs des Brennstoffeinspritzventils 1 einfließende und aufgrund der Relativbewegung zwischen Ventilnadel 3 und Anker 20 komprimierte Brennstoff nicht aus dem Innenvolumen 36 abfließen, kann dies beispielsweise zu seitlichen Versätzen des Dämpfungselements 32 führen, was wiederum Beschädigungen des Dämpfungselements 32 aufgrund unerwünschter Dehnung und Kerbwirkung oder Störungen im Brennstofffluß zur Folge hat.If the fuel flowing into the inner volume 36 during operation of the fuel injection valve 1 and compressed due to the relative movement between the valve needle 3 and the armature 20 cannot flow out of the inner volume 36, this can lead, for example, to lateral displacements of the damping element 32, which in turn causes damage to the damping element 32 undesirable expansion and notch effect or disturbances in the fuel flow.
Die Drainage des in dem Innenvolumen 36 komprimierten Brennstoffs kann aber auch, wie in Fig. 2B in einer radialen Schnittansicht entlang der Linie IIB-IIB in Fig. 2A dargestellt, nicht radial, sondern axial in Abströmrichtung erfolgen. Zu diesem Zweck wird der zweite Flansch 31 mittels SegmentSchweißens an der Ventilnadel 3 befestigt. Dabei wird der zweite Flansch 31 nicht über eine lückenlos umfJangsmäßig umlaufende Schweißnaht 33 mit der Ventilnadel 3 verbunden, sondern über einzelne Schweißsegmente 37, welche, wie in Fig. 2B dargestellt, beispielsweise eine radiale Winkelausdehnung von ca. 90° aufweisen und zwei Drainagelücken 38, welche ebenfalls eine Winkelausdehnung von ca. 90° aufweisen, einschließen. Der in dem Innenvolumen 36 komprimierte Brennstoff kann somit über die Drainagelücken 38 zwischen der Ventilnadel 3 und dem zweiten Flansch 31 abfließen.However, as shown in FIG. 2B in a radial sectional view along the line IIB-IIB in FIG. 2A, the fuel compressed in the inner volume 36 can also not be drained radially but axially in the outflow direction. For this purpose, the second flange 31 is attached to the valve needle 3 by means of segment welding. In this case, the second flange 31 is not connected to the valve needle 3 via a weld seam 33 that runs around the circumference without gaps, but via individual welding segments 37, which, as shown in FIG. 2B, have, for example, a radial angular extent of approximately 90 ° and two drainage gaps 38, which likewise have an angular extent of approximately 90 °. The fuel compressed in the inner volume 36 can thus flow away via the drainage gaps 38 between the valve needle 3 and the second flange 31.
Die 'Methode des SegmentSchweißens hat insbesondere den Vorteil, daß die Ableitung des komprimierten Brennstoffs in dem Innenvolumen 36 ohne zusätzliche Bauteile einfach möglich ist.The ' segment welding ' method has the particular advantage that the compressed fuel can easily be discharged into the inner volume 36 without additional components.
Es ist ebenfalls möglich, nicht nur zwei Schweißsegmente 37 zur Verbindung des zweiten Flansches 31 mit der Ventilnadel 3 anzubringen, sondern beispielsweise vier einander kreuzförmig gegenüberliegende Schweißsegmente 37 mit entsprechend vier dazwischenliegenden Drainagelücken 38. Die Zahl der Schweißsegmente 37 und der Drainagelücken 38 kann den Erfordernissen entsprechend angepaßt werden.It is also possible not only to attach two welding segments 37 for connecting the second flange 31 to the valve needle 3, but, for example, four welding segments 37 lying opposite one another in a cross shape, with correspondingly four intermediate drainage gaps 38. The number of welding segments 37 and the drainage gaps 38 can correspond to the requirements be adjusted.
Fig. 3 zeigt in einer auszugsweisen Schnittdarstellung ein weiteres Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils 1. Dabei ist zwischen dem zweiten Flansch 31 und dem Dämpfungselement 32 ein zweiter Zwischenring 39 eingelegt.FIG. 3 shows an excerpted sectional illustration of a further exemplary embodiment of the fuel injector 1 according to the invention. A second intermediate ring 39 is inserted between the second flange 31 and the damping element 32.
Zur Ableitung des in dem Innenvolumen 36 komprimierten Brennstoffs sind zweckmäßigerweise auf einer ablaufseifigen Seite 40 des ersten Zwischenrings 34 und einer zulaufseifigen Seite 41 des zweiten Zwischenrings 39 radiale Nuten angebracht, durch welche der Brennstoff aus dem Innenvolumen 36 zwischen dem ersten Zwischenring 34 und dem zweiten Zwischenring 39 an der Oberfläche des Dämpfungselements 32 ablaufen kann. Die Struktur der ablaufseifigen Seite 40 des ersten Zwischenrings 34 und der zulaufseitigen Seite 41 des zweiten Zwischenrings 39 kann dabei beispielsweise durch Einprägen oder Einfräsen erzeugt werden.In order to discharge the fuel compressed in the inner volume 36, radial grooves are expediently provided on a drain-side side 40 of the first intermediate ring 34 and an inlet-soap side 41 of the second intermediate ring 39, through which the fuel from the inner volume 36 between the first intermediate ring 34 and the second intermediate ring 39 can run on the surface of the damping element 32. The structure of the drain-side side 40 of the first intermediate ring 34 and the inlet-side 41 of the second intermediate ring 39 can can be generated, for example, by embossing or milling.
Eine andere Möglichkeit, den in dem Innenvolumen 36 gestauten Brennstoff abzuführen, besteht darin, in dem zweiten Flansch 31 radiale Bohrungen 43 einzubringen, welche beispielsweise knapp unterhalb des Dämpfungselements 32 eine Verbindung zwischen dem Innenvolumen 36 und der zentralen Ausnehmung 42 des Brennstoffeinspritzventils 1 herstellen. Die 'Anzahl der Bohrungen kann' sich auf eine beschränken, es können aber auch mehrere, z. B. in gleichen Winkelabständen angeordnete Bohrungen 43 vorhanden sein.Another possibility of removing the fuel stowed in the inner volume 36 is to make radial bores 43 in the second flange 31, which, for example, produce a connection between the inner volume 36 and the central recess 42 of the fuel injection valve 1 just below the damping element 32. The ' number of holes' can be limited to one, but several, e.g. B. holes 43 arranged at equal angular intervals.
Allen oben beschriebenen Ausführungsbeispielen des erfindungsgemäßen Brennstoffeinspritzventils 1 ist gemeinsam, daß bei geeigneter Wahl der Durchmesser der Bohrungen 43, der Drainagelücken 38 oder der Nutenstruktur das Verhältnis der abströmenden Menge des Brennstoffs zu der einströmenden Menge aus dem bzw. in das Innenvolumen 36 geregelt werden kann. Die dadurch entstehende Dämpfung kann zur Prellervermeidung genutzt werden kann.All of the above-described exemplary embodiments of the fuel injection valve 1 according to the invention have in common that with a suitable choice of the diameter of the bores 43, the drainage gaps 38 or the groove structure, the ratio of the outflowing amount of fuel to the inflowing amount from or into the inner volume 36 can be regulated. The resulting damping can be used to avoid bouncing.
Insbesondere werden durch diese Maßnahmen die Ventilnadelpreller vermindert, da die Ventilnadel 3 nach dem Aufsetzen des Ventilschließkörpers 4 aufgrund der Viskosität des Brennstoffs in dem Innenvolumen 36 einen Widerstand vorfindet und deshalb keine Möglichkeit mehr hat, sich erneut in Hubrichtung zu bewegen.In particular, the valve needle bouncer is reduced by these measures, since the valve needle 3, after the valve closing body 4 has been put on, has resistance due to the viscosity of the fuel in the inner volume 36 and therefore no longer has any possibility of moving again in the stroke direction.
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und z. B. auch für nach außen öffnende Brennstoffeinspritzventile 1 oder andere Ankerformen, beispielsweise Flachanker, geeignet. The invention is not limited to the illustrated embodiments and z. B. also suitable for outward opening fuel injection valves 1 or other anchor shapes, for example flat anchors.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1), insbesondere Einspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen, mit einer Ventilnadel (3), die mit einer Ventilsitzfläche (6) zu einem Dichtsitz zusammenwirkt, und mit einem an der Ventilnadel (3) angreifenden Anker (20), wobei der Anker (20) an der Ventilnadel (3) axial beweglich ist und von einem aus einem Elastomer bestehenden Dämpfungseiement (32) gedämpft wird, wobei zwischen dem Anker (20) und dem Dämpfungseiement (32) ein erster Zwischenring (34) angeordnet ist und das Dämpfungseiement (32) auf einem mit der Ventilnadel (3) kraftschlüssig verbundenen Flansch (31) aufliegt, dadurch gekennzeichnet, daß der Zwischenring (34) und/oder der Flansch (31) zumindest einen radialen und/oder axialen Kanal aufweist, welcher ein zwischen der Ventilnadel (3) und dem Dämpfungselement (32) befindliches Innenvolumen (36) mit einer zentralen Ausnehmung (42) des Brennstoffeinspritzventils (1) verbindet.1. Fuel injection valve (1), in particular injection valve for fuel injection systems of internal combustion engines, with a valve needle (3) which cooperates with a valve seat surface (6) to form a sealing seat, and with an armature (20) engaging on the valve needle (3), the Armature (20) on the valve needle (3) is axially movable and is damped by a damping element (32) consisting of an elastomer, a first intermediate ring (34) being arranged between the armature (20) and the damping element (32), and that Damping element (32) rests on a flange (31) which is non-positively connected to the valve needle (3), characterized in that the intermediate ring (34) and / or the flange (31) has at least one radial and / or axial channel which has a between the valve needle (3) and the damping element (32) connects the inner volume (36) with a central recess (42) of the fuel injector (1).
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß ein zweiter Zwischenring (39) zwischen dem Dämpfungselement (32) und dem Flansch (31) angeordnet ist. 2. Fuel injection valve according to claim 1, characterized in that a second intermediate ring (39) between the damping element (32) and the flange (31) is arranged.
3. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der zweite Zwischenring (39) ebenfalls zumindest einen Kanal zur Verbindung des Innenvolumens (36) mit der zentralen Ausnehmung (42) des Brennstoffeinspritzventils (1) aufweist.3. Fuel injection valve according to claim 2, characterized in that the second intermediate ring (39) also has at least one channel for connecting the inner volume (36) with the central recess (42) of the fuel injection valve (1).
4. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der zumindest eine Kanal als radiale Bohrung (43) in dem Flansch (31) ausgeführt ist.4. Fuel injection valve according to one of claims 1 to 3, characterized in that the at least one channel is designed as a radial bore (43) in the flange (31).
5. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der zumindest eine Kanal als radiale Nut an einer ablaufseitigen Seite (40) des ersten Zwischenrings (34) ausgeführt ist.5. Fuel injection valve according to one of claims 1 to 3, characterized in that the at least one channel is designed as a radial groove on an outlet side (40) of the first intermediate ring (34).
5. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis5. Fuel injection valve according to one of claims 1 to
3, dadurch gekennzeichnet, daß der zumindest eine Kanal als radiale Nut an einer zulaufseifigen Seite (41) des zweiten Zwischenrings (39) ausgeführt ist.3, characterized in that the at least one channel is designed as a radial groove on an inlet side (41) of the second intermediate ring (39).
7. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Flansch (31) mittels Segmentschweißens an der Ventilnadel (3) befestigt ist.7. Fuel injection valve according to one of claims 1 to 6, characterized in that the flange (31) is fixed by means of segment welding to the valve needle (3).
8. Brennstoffeinspritzventil nach Anspruch 7, dadurch gekennzeichnet, daß der Flansch (31) über mindestens zwei Schweißsegmente (37) mit der Ventilnadel (3) verbunden ist und daß die Schweißsegmente (37) eine radiale Winkelausdehnung von ca. 90° aufweisen. 8. Fuel injection valve according to claim 7, characterized in that the flange (31) via at least two welding segments (37) with the valve needle (3) is connected and that the welding segments (37) have a radial angular extent of approximately 90 °.
9. Brennstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, daß zwischen den SchweißSegmenten (.37) Drainagelücken (38] ausgebildet sind. 9. Fuel injection valve according to claim 8, characterized in that drainage gaps (38) are formed between the welding segments (.37).
EP01955273A 2000-08-10 2001-07-20 Fuel injection valve Expired - Lifetime EP1309789B1 (en)

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DE10039078A DE10039078A1 (en) 2000-08-10 2000-08-10 Fuel injector
PCT/DE2001/002765 WO2002012709A1 (en) 2000-08-10 2001-07-20 Fuel injection valve

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US6808134B2 (en) 2004-10-26
KR20020037067A (en) 2002-05-17
DE50108625D1 (en) 2006-03-30
WO2002012709A1 (en) 2002-02-14
DE10039078A1 (en) 2002-02-21
CZ20021250A3 (en) 2003-10-15
US20030047160A1 (en) 2003-03-13
JP4646180B2 (en) 2011-03-09
EP1309789B1 (en) 2006-01-04
CN1253656C (en) 2006-04-26
JP2004506127A (en) 2004-02-26
CN1388861A (en) 2003-01-01

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